JP5705344B2 - Image forming apparatus - Google Patents

Description

  The present invention relates to an image forming apparatus that drives a photosensitive drum or a belt unit with a motor, and more particularly, to crowning of a gear that transmits a driving force of the motor to a photosensitive member or a belt unit.

  A tandem type image forming apparatus in which photosensitive drums having different development colors are arranged along a belt unit of an intermediate transfer member or a recording material transport member has been put into practical use. The image forming apparatus is not limited to the tandem type, and when the speed unevenness occurs on the photosensitive drum, the unevenness of the pitch of the scanning line developed on the photosensitive drum occurs and the image quality deteriorates. In the tandem type image forming apparatus, uneven rotation speed of the photosensitive drum and the belt unit enlarges the alignment error of each color toner image and causes color misregistration (Patent Document 1).

  A tandem type image forming apparatus is provided in which a motor is provided for each of the plurality of photosensitive drums, and the photosensitive drum is driven by decelerating one step between a gear provided on the motor shaft and a gear provided on the rotating shaft of the photosensitive drum. (Patent Document 1). This is because, by reducing the number of gear meshing steps, the rotational speed unevenness of the photosensitive drum caused by cumulative addition of errors of a plurality of gears is suppressed.

  In recent years, in order to achieve higher image quality, it is desired that the photosensitive drum of the image forming apparatus further suppresses microscopic rotational speed fluctuations. It is desired to improve the reproducibility of meshing for each gear and suppress the noise-like speed fluctuation generated at the meshing frequency. This is because minute speed fluctuations generated at the meshing frequency cause rotation unevenness of the photosensitive drum and appear as slight scanning line pitch unevenness on the image.

  Patent Document 1 discloses a configuration in which a single gear reduction mechanism is attached to each of four photosensitive drums of a full-color image forming apparatus and driven by individual motors. Here, the tooth surface of the driven gear is crowned to gradually reduce the tooth thickness toward both ends in the gear thickness direction. As a result, rotation unevenness of the photosensitive drum is reduced by avoiding the one-side contact where the driving gear and the driven gear transmit power at the edge in the thickness direction of the driven gear (see FIG. 6).

JP 2004-258353 A

  In recent years, as the image forming apparatus has been reduced in size and weight, even if the photosensitive drum drive system is configured as in Patent Document 1, the speed fluctuation of the photosensitive drum tends to increase. In order to reduce the speed fluctuation, there are methods for increasing the mechanical rigidity of the entire mechanism, such as thickening the shaft of the gear reduction mechanism, increasing the thickness of the support housing, and supporting the both ends by increasing the gear thickness. However, in this case, downsizing and weight reduction of the image forming apparatus are hindered, resulting in an increase in component costs.

  The present invention provides an image forming apparatus capable of realizing high image quality of an output image by suppressing minute speed fluctuations of a photosensitive drum without hindering reduction in size and weight in a gear reduction mechanism between a motor and the photosensitive drum. It is intended to provide.

An image forming apparatus according to an aspect of the invention includes a rotating body that is rotatably supported, a pair of bearing portions that pivotally support the rotating body at both ends of the rotating body, and for driving the rotating body. A motor, a drive gear disposed on the drive shaft of the motor, and a driven gear that is provided outside the pair of bearing portions with respect to the rotation axis direction of the rotary body and meshes with the drive gear and rotates integrally with the rotary body. And at least one of the driven gear and the drive gear is convex with respect to both ends of the tooth surface on the side where the driven gear and the drive gear mesh with each other with respect to the rotational axis direction of the rotating body. It has a crown shape. Then, with respect to the rotational axis of the rotating body, the crown amount formed in the driven gear or said driving gear is maximum position, with respect to the rotation axis direction of the rotating body, the maximum pressure in the tooth surfaces of the drive gear The position where the crown is received is offset to the side that moves as the drive gear is driven, and the position where the crown amount is offset is offset relative to the rotational axis direction of the rotating body. The crown shape is formed so that the change rate of the tooth thickness is larger than that on the side opposite to the side .

  According to the image forming apparatus of the present invention, by applying asymmetric crowning (see FIG. 10) in the thickness direction of the gear, it is possible to avoid hitting to a larger tilt angle than when applying symmetrical crowning (see FIG. 6). . For this reason, even if a light weight driving mechanism with low rigidity is used, it is possible to reduce the rotational speed unevenness of the photosensitive member due to the contact of each gear transmission.

  Therefore, in the gear reduction mechanism between the motor and the photosensitive drum, it is possible to realize a high output image quality by suppressing minute speed fluctuations of the photosensitive drum without hindering downsizing and weight reduction.

1 is an explanatory diagram of a configuration of an image forming apparatus. It is explanatory drawing of the drive system of a photosensitive drum. It is a perspective view of the drive system of a photosensitive drum. It is explanatory drawing of the gear transmission which does not give crowning. It is a perspective view of the driven gear which gave symmetrical crowning. It is explanatory drawing per piece of the driven gear which gave symmetrical crowning. It is a measurement result of the alignment error range which does not generate | occur | produce per piece. FIG. 3 is a partial enlarged view of a photosensitive drum drive system. It is a perspective view of the driven gear which gave asymmetric crowning. It is explanatory drawing per piece of the driven gear which gave the asymmetrical crowning. It is a diagram of the measurement result of the rotational speed fluctuation reduction effect by Example 1. It is explanatory drawing of the measurement result of the load torque of a drum motor. It is explanatory drawing of the deformation amount of a drum gear. 3 is an explanatory diagram of a configuration of an intermediate transfer unit. FIG.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the present invention, as long as a non-target crowning process is applied to the gear of the rotation transmission system of the photosensitive drum and the motor in the gear thickness direction, a part or all of the configuration of the embodiment is an alternative configuration. Other alternative embodiments can also be implemented.

  Therefore, an image forming apparatus using a photosensitive drum can be implemented without distinction between a tandem type / 1 drum type, an intermediate transfer type, a recording material conveyance type, and a direct transfer type. In the present embodiment, only main parts related to toner image formation / transfer will be described. However, the present invention includes a printer, various printing machines, a copier, a fax machine, a composite machine, in addition to necessary equipment, equipment, and a housing structure. It can be implemented in various applications such as a machine.

  In addition, about the general matter of the image forming apparatus shown by patent document 1, illustration is abbreviate | omitted and the overlapping description is abbreviate | omitted.

<Image forming apparatus>
FIG. 1 is an explanatory diagram of the configuration of the image forming apparatus. As shown in FIG. 1, the image forming apparatus 100 is a tandem intermediate transfer type full-color printer in which yellow, magenta, cyan, and black image forming portions PY, PM, PC, and PK are arranged along an intermediate transfer unit 50. is there.

  In the image forming unit PY, a yellow toner image is formed on the photosensitive drum 1Y and is primarily transferred to the intermediate transfer belt 55. In the image forming unit PM, a magenta toner image is formed on the photosensitive drum 1 </ b> M, and is primarily transferred onto the yellow toner image on the intermediate transfer belt 55. In the image forming units PC and PK, a cyan toner image and a black toner image are formed on the photosensitive drums 1C and 1K, respectively, and are sequentially transferred onto the intermediate transfer belt 55 in order to be primarily transferred.

  The four-color toner images carried on the intermediate transfer belt 55 are conveyed to the secondary transfer portion T2 and are collectively secondary transferred to the recording material P. The recording material P on which the four-color full-color toner images are secondarily transferred is separated from the intermediate transfer belt 55 by the curvature and sent to the fixing device 40. The fixing device 40 heats and presses the recording material P to fix the toner image on the surface, and then the recording material P is discharged outside the machine body.

  The image forming units PY, PM, PC, and PK are configured substantially the same except that the color of toner used in the developing devices 4Y, 4M, 4C, and 4K is different from yellow, magenta, cyan, and black. Hereinafter, the yellow image forming unit PY will be described, and the other image forming units PM, PC, and PK will be described by replacing Y at the end of the reference numerals attached to the constituent members being described as M, C, and K. Shall be.

  In the image forming unit PY, a corona charger 2Y, an exposure device 3Y, a developing device 4Y, a primary transfer roller 5Y, and a drum cleaning device 6Y are arranged around the photosensitive drum 1Y.

  The photosensitive drum 1Y is formed by forming a negatively charged photosensitive layer on the base of an aluminum cylinder, and rotates in the direction of arrow R1 at a predetermined process speed. The corona charger 2Y uniformly charges the surface of the photosensitive drum 1Y to the negative dark portion potential VD. The exposure device 3Y scans the laser beam with a rotating mirror and writes an electrostatic image of the image on the surface of the photosensitive drum 1Y.

  The developing device 4Y forms a toner image by reversing and developing the electrostatic image formed on the photosensitive drum 1Y. The primary transfer roller 5 </ b> Y presses the inner surface of the intermediate transfer belt 55 to form a primary transfer portion TY between the photosensitive drum 1 </ b> Y and the intermediate transfer belt 55. By applying a positive voltage to the primary transfer roller 5Y, the toner image carried on the photosensitive drum 1Y is primarily transferred to the intermediate transfer belt 55. The drum cleaning device 6Y slides a cleaning blade on the photosensitive drum 1Y to collect the transfer residual toner remaining on the photosensitive drum 1Y by escaping from the primary transfer to the intermediate transfer belt 55.

  The intermediate transfer belt 55 is supported around a tension roller 52, a drive roller 54, and a counter roller 51, and is driven by the drive roller 54 to rotate in the direction of arrow R2 at a predetermined process speed.

  The secondary transfer roller 33 abuts on the intermediate transfer belt 55 whose inner surface is supported by the opposing roller 51 to form a secondary transfer portion T2. The recording material P drawn from the recording material cassette 30 is separated one by one by the separation roller 31 and sent to the registration roller 32. The registration roller 32 receives and waits for the recording material P in a stopped state, and sends the recording material P to the secondary transfer portion T2 in synchronization with the toner image on the intermediate transfer belt 55.

  In the process in which the recording material P is transported through the secondary transfer portion T2, a positive DC voltage is applied to the secondary transfer roller 33, whereby the full color toner image is transferred from the intermediate transfer belt 55 to the recording material P. Is done.

<Gear transmission mechanism>
FIG. 2 is an explanatory diagram of a photosensitive drum drive system. FIG. 3 is a perspective view of the drive system of the photosensitive drum.

  As shown in FIG. 2, the photosensitive drums 1Y, 1M, 1C, and 1K of the image forming units PY, PM, PC, and PK are individually driven to rotate by the drum driving units 9Y, 9M, 9C, and 9K. Since the drum drive units 9Y, 9M, 9C, and 9K are configured in common and the crowning in the gear transmission mechanism is similarly performed, the motor drive mechanism 9Y will be described below.

  The drum gear shaft 10 of the photosensitive drum 1 </ b> Y, which is an example of a photosensitive member, is rotatably supported by the support housing 16 using a bearing 18. The motor 13 is fixed to the support housing 16, and the motor gear 14, which is an example of a drive gear, is directly formed on the drive shaft 14 of the motor. The drum gear 12, which is an example of a driven gear, meshes with the motor gear 14 and rotates integrally with the photosensitive drum 1Y. A flywheel 15 is connected to the tip end of the drum gear shaft 10 of the photosensitive drum 1Y that is cantilevered to reduce fluctuations in rotational speed due to inertia.

  As shown in FIG. 3, when the drum motor 13 operates, the motor gear 14 rotates in the direction of arrow R13. The motor gear 14 and the drum gear 12 mesh with each other, and the rotation of the motor gear 14 is transmitted to the drum gear 12. Due to the rotational driving force transmitted from the motor gear 14, the drum shaft 10, the photosensitive drum 1Y, the drum gear 12, and the flywheel 15 are integrally rotated in the direction of the arrow R12.

  The motor gear 14 is formed by directly cutting the output shaft of the motor 13. The gear specifications are an outer diameter of 9 mm, a module of 0.6, a pressure angle of 20 °, a number of teeth of 12, and a helical gear twist angle of 20 °.

  The drum gear 12 has a resin gear portion formed by injection molding around a metal bearing portion. The gear specifications are an outer diameter of 124 mm, a thickness of 18 mm, a module 0.6, a pressure angle of 20 °, a number of teeth of 192, and a helical gear twist angle of 20 °. The inclination of the tooth surface of the helical gear is inclined in the direction of the solid line 12L in the figure. The disk portion of the drum gear 12 is lightened by reducing the thickness to 6 mm.

  By the way, as a factor that hinders high image quality in the image forming apparatus 100, the rotational speed unevenness occurs in the photosensitive drum 1Y due to the meshing transmission error generated by the meshing of the motor gear 14 that drives the photosensitive drum 1Y and the drum gear 12. Further, there is a problem that the rotational speed unevenness appears as pitch unevenness of the scanning line on the output image.

  Therefore, in the gear transmission mechanism between the motor 13 and the rotating shaft of the photosensitive drum 1Y, a helical gear is employed in order to continuously transmit torque due to the meshing of the gears and suppress rotational speed unevenness.

  Further, the output torque unevenness is reduced by setting the reduction ratio of the gear transmission system to 10 or more and rotating the motor at a high speed. By increasing the speed reduction ratio, the speed reduction ratio is preferably 10 or more, so that the influence of uneven rotation of the motor on the rotational speed of the photosensitive drum can be reduced.

  In addition, in order to absorb errors in the axial parallelism and the meshing parallelism of the tooth surfaces, which occur regularly or accidentally in the gear transmission system, at least one of the driven gear and the driving gear is crowned. The tooth surface of the drum gear 12 is crowned to gradually decrease the tooth thickness toward both ends in the gear thickness direction. By making the drum gear 12 a crowning gear, the contact of pressure concentrated on the end in the gear thickness direction is avoided, and the meshing transmission error between the motor gear 14 and the drum gear 12 is reduced. The drum gear 12 is a crowning gear having a crown amount of 70 μm.

<Crowning gear>
FIG. 4 is an explanatory diagram of gear transmission without crowning. FIG. 5 is a perspective view of a driven gear subjected to symmetrical crowning. FIG. 6 is an explanatory view of a piece of a driven gear subjected to symmetrical crowning. FIG. 7 shows the measurement result of the alignment error range where no contact occurs.

  4, (a) is the gear meshing, (b) is an enlarged view of the portion A, (c) is an explanatory diagram of the meshing state of the BB cross section, (d) is a small inclination in the tooth surface It is explanatory drawing of the state in which the one-sided collision occurred. In FIG. 6, (a) is a symmetrical crowning, (b) is a state where the tooth surface is not inclined, (c) is a state where a small inclination is generated on the tooth surface, and (d) is a state where a large inclination is generated on the tooth surface. It is.

  As shown in FIG. 4A, a case is considered in which the driving gear G1 and the driven gear G2 that are not crowned mesh with each other at the portion A to transmit the driving force.

  As shown in FIG. 4B, the gear teeth draw an involute curve, and if there is no deformation of the gear teeth, they theoretically contact at one point. For this reason, when the cross section BB of the portion A is taken out, the tooth surfaces of the drive gear G1 and the driven gear G2 are in line contact as shown in FIG. However, in actuality, since it deforms under pressure, it contacts within a certain range, which is called the contact area. A view observed in the direction as shown in FIG. 4C is referred to as a tooth streak schematic diagram of meshing gears.

  As shown in FIG. 5, by applying crowning to the driven gear G <b> 2, as shown in Patent Document 1, torque unevenness and rotational speed unevenness due to such piece contact are reduced.

  As shown in FIG. 6 (a), the driven gear G2 to which the crowning is applied is a crowning gear in which the tooth stripes are swollen.

  As shown in FIG. 5 (b), when the drive gear G1 having a straight tooth stripe and the driven gear G2 having a swollen tooth stripe are meshed, a small inclination is generated between the drive gear G1 and the driven gear G2. Even if it occurs, it does not have to be in a single-contact state. For this reason, the crowning gear has an effect of reducing the meshing transmission error.

  That is, in the image forming apparatus, the drive gear G1 and the driven gear G2 may have an alignment error. The alignment error means that the tooth lines of the meshing gears are not parallel due to tilting of the shafts of the meshing driving gear G1 and the driven gear G2, deformation in the thickness direction of the gears, backlash between the shaft and the inner diameter of the gears, and the like. .

  As shown in FIG. 4D, when the crowning is not performed and the tooth streak is a straight line, even if a slight alignment error occurs, the meshing gear is in a single-contact state where the driving torque is transmitted by point contact. . Even if a slight inclination occurs between the drive gear G1 and the driven gear G2 having a straight tooth streak, only the edge of the tooth surface in the gear thickness direction comes into contact. When the one-side contact state occurs, the contact area between the tooth surfaces of the drive gear G1 and the driven gear G2 becomes unstable, and the gear meshing transmission error increases. Torque unevenness and rotational speed unevenness occur in the meshing pitch period of the gear between the transmission torque and the transmission rotational speed.

  As shown in FIG. 6 (c), when the drive gear G1 having a straight tooth streak and the driven gear G2 having a curved tooth streak are engaged with each other, even if an alignment error occurs, You don't have to hit the hit state. As indicated by the arrow, torque transmission is performed at an intermediate position in the thickness direction of the driven gear G2, and the contact area of the surface contact by pressurization is stabilized. Therefore, the meshing transmission error is caused by the tooth streak shown in FIG. Does not increase as in the case of straight gears.

  As shown in FIG. 6 (c), when the alignment error is below a certain level, the crowning gear does not collide and the meshing transmission error does not increase so much. An area of alignment error in which the crowning gear does not come into contact with each other and the meshing transmission error reduction effect can be exhibited is called an alignment error allowable area.

  As shown in FIG. 6D, there is a limit to the transmission error reduction capability of the crowning gear. When a large alignment error that cannot be absorbed by crowning occurs, as shown by an arrow, a piece-of-piece contact occurs. When a large alignment error occurs, one-side contact occurs even in the crowning gear, and the effect of reducing the meshing transmission error due to crowning is not sufficiently exhibited.

  The alignment error allowable region is widened by increasing the bulging amount (crown amount) of the crowning gear. However, on the other hand, when the crown amount is increased, the pressure contact area of the tooth surface is reduced, and the meshing transmission error is increased. In the crowning gear, a range having a spread centering on the contact point is compressed and deformed and is in surface contact. The larger the surface contact area, the smoother the torque transmission and the smaller the torque fluctuation and speed fluctuation. For this reason, when the crowning amount is increased, the spread of the contact centering on the contact point becomes narrow, and the transmission torque fluctuation and the speed fluctuation increase. Therefore, it is desirable to determine the crown amount as small as possible. In FIG. 6, the change in the tooth thickness is exaggerated for easy understanding, but in actuality, it is only a difference in the tooth thickness of about several μm / mm.

  As shown in FIG. 7, an alignment error allowable region was measured by engaging crowning gears having a module of 0.5, the number of teeth of 96, a pressure angle of 20 °, a twist angle of 20 °, a tooth width of 10 mm, and a crown amount of 30 μm. When the inclination of the parallelism of the shaft exceeds ± 20 min, one-sided contact occurs and the meshing transmission error is rapidly reduced. For this reason, it can be seen that the alignment error allowable region of the parallelism of the crowning gear shaft having a crown amount of 30 μm is about ± 20 min.

  As shown in FIG. 3, when a rotational load is applied to the drum gear 12 of the helical gear, a steady alignment error occurs as the photosensitive drum 1Y is driven. The drum gear 12 and the motor gear 14 are helical gears with a twist angle of 20 °. Since the tooth surfaces of the helical gear are meshed obliquely, a thrust force in the direction of the arrow R10 is generated in the torque transmission portion of the drum gear 12 when the rotational torque is transmitted. Due to the steady thrust force, the drum gear 12 having a large diameter and relatively small rigidity is deformed so as to fall, and the tooth surface is inclined. Centering on this state, an alignment error fluctuation during driving occurs.

  Further, when a load is applied to the drum gear 12 and the motor gear 14 that are cantilevered, a steady alignment error occurs between the drum gear shaft 10 and the motor gear 14. Since both the drum gear 12 and the motor gear 14 are cantilevered, the meshing tooth surfaces are inclined in a direction in which the distance between the axes on the free end side increases with torque transmission. Centering on this state, an alignment error fluctuation during driving occurs. Even if the motor gear 14 itself has high rigidity, a steady alignment error occurs in the motor gear 14 due to the bending of the frame to which the motor 13 is attached.

  In the state where these alignment errors exceed the alignment error allowable region, the effect of reducing the meshing transmission error of the crowning gear is not sufficiently exhibited as shown in FIG. In the following embodiments, the alignment error tolerance range of the crowning gear is offset with respect to these steady alignment errors, thereby absorbing the alignment error fluctuation during driving and avoiding the one-sided contact.

<Example 1>
FIG. 8 is a partially enlarged view of the photosensitive drum drive system. FIG. 9 is a perspective view of a driven gear subjected to asymmetric crowning. FIG. 10 is an explanatory view of a piece of driven gear subjected to asymmetric crowning. FIG. 11 is a diagram of measurement results of the rotational speed fluctuation reduction effect according to the first embodiment. In FIG. 9 and FIG. 10, for easy understanding, asymmetric crowning is shown using a spur gear different from an actual helical gear.

  As shown in FIG. 8, the drum gear 12 subjected to the crowning and the motor gear 14 not subjected to the crowning mesh with each other to transmit the torque of the motor 13 to the drum gear shaft 10. In Example 1, as a result of analysis described later, it was found that the side in the gear thickness direction that receives the maximum applied pressure on the tooth surface of the drum gear 12 approaches the photosensitive drum 1Y side as the photosensitive drum 1Y is driven. .

  For this reason, on the photosensitive drum 1Y side of the drum gear 12, asymmetric crowning is applied in the gear thickness direction so as to increase the ratio of reducing the tooth thickness in the gear thickness direction, compared to the flywheel 15 side. The crowning center position (crowning sensor CC) is moved closer to the photosensitive drum 1Y than the center position in the gear thickness direction.

  As shown in FIG. 9, the tooth surface of the drum gear 12 is asymmetrically crowned in the gear thickness direction. By offsetting the alignment error allowable region due to crowning of the drum gear 12 in the direction of the arrow D with respect to the steady alignment error of the drum gear 12, the mesh transmission error reducing ability is exhibited. The minimum crowning position (maximum tooth thickness position) of the drum gear 12 is shifted by 3 mm in the arrow D direction from the center in the gear thickness direction.

  In the case of the crowning symmetrical to the gear thickness direction shown in FIG. 6A, when a large alignment error occurs as shown in FIG. 6D, the contact position becomes the edge in the gear thickness direction as shown by the arrow. Reach the one-sided state. On the other hand, in the case of asymmetric crowning in the gear thickness direction shown in FIG. 10 (a), as shown in FIG. 10 (d), even if a large alignment error occurs, the contact position is in the gear thickness direction. It is in the middle position and a one-sided state is avoided.

  As shown in FIG. 11, the effect of reducing the rotational speed unevenness was confirmed by the image forming apparatus 100 having the drum gear 12 of the crowning gear in which the minimum crowning position (position of the maximum tooth thickness) is shifted by 3 mm in the arrow D direction of FIG. The image forming apparatus 100 outputs a horizontal line image having a width of 2 scan lines at a pitch of 4 scan lines, measures the pitch interval of the horizontal line toner image by measuring laser reflected light on the photosensitive drum 1Y, and performs discrete Fourier transform on the data. This graph is shown in FIG.

  (A) of FIG. 11 is a measurement result of the comparative example using the drum gear 12 in which the minimum crowning position is at the center in the gear thickness direction. FIG. 11B shows measurement results of Example 1 using the drum gear 12 in which the minimum crowning position is shifted by 3 mm in the direction D in FIG.

  In Example 1 of FIG. 11B, it was found that the pitch unevenness of 216 Hz that is the meshing frequency of the drum gear 12 and the motor gear 14 was reduced as compared with the comparative example of FIG. . Since the photosensitive drum 1Y rotates 0.89 per second, the number of teeth of the drum gear 12 is 192 to 216 Hz. The pitch unevenness of the scanning line at the meshing frequency of 216 Hz indicated by a circle is reduced by about 30% from 0.45 μm in the comparative example to 0.3 μm in the first embodiment.

<Examination result of offset amount>
FIG. 12 is an explanatory diagram of the measurement result of the load torque of the drum motor. FIG. 13 is an explanatory diagram of deformation of the drum gear.

  The examination performed in order to determine the offset amount of the minimum crowning position (position of the maximum tooth thickness) is shown. Since the drum gear 12 is a helical gear with a twist angle of 20 °, the torque of the motor gear 14 generates a thrust force (force that urges in the axial direction), and the drum gear 12 is deformed so as to fall toward the flywheel 15 side. Thus, a stationary alignment error of the tooth surface occurs.

  As shown in FIG. 12, as a result of measuring the load torque of the drum motor 13 by operating the image forming apparatus 100 for 40 seconds, a load torque of 0.09 Nm (about 9 kgf · mm) was applied. When this is converted into a thrust force f applied to the drum gear 12, the following expression is obtained.

As a result of calculating the amount of collapse deformation when a thrust force of 8 N (about 8.0 × 10 ⁻¹ kgf) is applied to the drum gear 12 using finite element analysis, as shown in FIG. It was found that a tilt of 4.04 × 10 ⁻² mm occurred in the direction. Therefore, as shown in FIG. 13B, the minimum crowning position (maximum tooth thickness position) of the crowning gear is shifted to one side in the gear thickness direction. The helical gear is shifted from the center in the gear thickness direction in a direction opposite to the thrust load generation direction in which the helical gear acts on the drum gear 12 (the opposite side in which the drum gear 12 is deformed in the axial direction).

  The steady alignment error (tooth surface twist angle) δ caused by the tilting of the drum gear 12 caused by the helical gear is expressed by the following equation.

  Note that the amount of fall of the motor gear 14 is negligibly small with respect to the amount of fall of the drum gear 12, and the details are omitted. This is because the motor gear 14 is made of metal, has a Young's modulus of about 100 times that of resin, and the point of action of the thrust force is close to the center of rotation.

  Next, since both the drum gear 12 and the motor gear 14 are supported in a cantilevered manner, the free end side of the shafts is tilted in the direction in which the distance between the shafts is widened due to the meshing pressure angle between them, and a steady alignment error occurs. The force f applied to each gear shaft is as follows.

Using finite element analysis, the tilt when the tilting force 8N (8.00 × 10 ⁻¹ kgf) in the separating direction was applied to the drum gear shaft 10 and the motor gear 14 was calculated. As a result, it was found that the drum gear shaft 10 was tilted at 1.60 × 10 ⁻³ mm and the motor gear 14 was tilted at 1.46 × 10 ⁻³ mm.

  A steady alignment error (tooth surface twist angle) δ caused by the tilting of both is calculated by the following equation.

  Next, since the weight of the flywheel 15 is applied to the drum gear shaft 10, the drum gear shaft is tilted in a direction in which the gap between the gear shafts is narrowed, and a steady alignment error (tooth surface twist angle) occurs.

Finite element analysis was performed to calculate the tilt when the load of the flywheel 15 was applied to the drum gear shaft 10. As a result, it was found that the drum gear shaft 10 was tilted by 8.48 × 10 ⁻³ mm.

  A steady alignment error (tooth surface twist angle) δ caused by the tilting of the drum gear shaft 10 is expressed by the following equation.

  When the offset amount Σ from the center in the gear thickness direction of the minimum crowning position (maximum tooth thickness position) necessary for canceling the three steady alignment errors is summed, the following formula is obtained with the D direction in FIG.

  From the above results, the minimum crowning position was shifted by 3 mm in the direction D in FIG. 8 as described above. As described with reference to FIG. 11, the effect of reducing the pitch unevenness of the scanning line at the meshing frequency of 216 Hz by about 30% was obtained.

<Example 2>
FIG. 14 is an explanatory diagram of the configuration of the intermediate transfer unit.

  As shown in FIG. 14, a tension roller 52 and a driving roller 54 are rotatably supported on a support housing 56 of the intermediate transfer unit 50, and the driving roller 54 that drives an intermediate transfer belt 55, which is an example of a belt member, It is driven by a motor drive mechanism 57. The motor drive mechanism 57 meshes the motor gear 64 of the motor 63 with the roller gear 62 fixed to the roller shaft 60, and transmits the output torque of the motor 63 to the roller shaft 60 to rotate the drive roller 54.

  The roller shaft 60 is rotatably supported by the support housing 56 using a bearing 68. The motor 63 is fixed to the support housing 56, and the motor gear 64, which is an example of a drive gear, is formed directly on the drive shaft of the motor. A roller gear 62, which is an example of a driven gear, meshes with the motor gear 64 and rotates integrally with the drive roller 54.

  The motor gear 64 formed by cutting out from the output shaft of the motor 63 is not crowned, but the roller gear 62 formed by resin molding is crowned. The minimum crowning position (maximum tooth thickness position) of the roller gear 62 is shifted in the motor 63 direction from the center in the gear thickness direction.

  The gear specifications of the motor gear 64 are an outer diameter of 10 mm, a module 0.6, a pressure angle of 20 °, a number of teeth of 12, and a helical gear twist angle of 30 °.

  The gear specifications of the roller gear 12 are an outer diameter of 43 mm, a thickness of 10 mm, a module 0.6, a pressure angle of 20 °, a number of teeth of 60, and a helical gear twist angle of 30 °.

<Example 3>
In the first embodiment, suppression of the rotational speed fluctuation of the photosensitive drum attached to the housing structure of the image forming apparatus has been described. However, the present invention can also be applied to a photosensitive drum driving unit attached to a housing structure of a process cartridge. In any case, the steady alignment error amount may be estimated using the analysis method described above, and the crowning center shift amount corresponding to the estimation result may be determined.

  Further, in the case of resin molding, it is not necessary to cut out the crowning from the material, so that a gear subjected to asymmetric crowning can be manufactured at low cost. Further, since the gear made of a resin material has a lower Young's modulus than the metal shaft, the contact area due to compression deformation is increased, and the speed variation of torque transmission can be reduced. However, asymmetric crowning may be applied to the gear of the metal shaft. Speed fluctuation noise is suppressed by applying asymmetric crowning to at least one of the meshing gears.

PY, PM, PC, PK Image forming unit 1Y, 1M, 1C, 1K Photosensitive drum 2Y, 2M, 2C, 2K Corona charger 3Y, 3M, 3C, 3K Exposure device 4Y, 4M, 4C, 4K Developing device 5Y, 5M 5C, 5K Primary transfer rollers 9Y, 9M, 9C, 9K Drum drive unit 54 Drive roller, 55 Intermediate transfer belt 10 Drum shaft, 12 Drum gear 13 Motor, 14 Motor gear 15 Flywheel 16 Crowning gear teeth 17 Gear tooth stripe

Claims (4)

A rotating body supported rotatably,
A pair of bearings that pivotally support the rotating body at both ends of the rotating body;
A motor for driving the rotating body;
A drive gear disposed on the drive shaft of the motor;
A driven gear provided on the outer side of the pair of bearing portions in the rotation axis direction of the rotating body, meshed with the drive gear and rotated integrally with the rotating body,
At least one of the driven gear and the drive gear has a crown shape so that the center side of the tooth surface on the side where the driven gear and the drive gear mesh with each other is convex with respect to both ends in the rotational axis direction of the rotating body. In an image forming apparatus having
The position where the crown amount formed on the driven gear or the drive gear is maximized with respect to the rotation axis direction of the rotating body is subjected to the maximum pressure on the tooth surface of the drive gear with respect to the rotation axis direction of the rotating body. The position is offset to the side that moves as the drive gear is driven ,
With respect to the rotational axis direction of the rotating body, the side where the crown amount is offset is offset so that the rate of change in tooth thickness is greater than the side opposite to the offset side. An image forming apparatus, wherein a crown shape is formed . The image forming apparatus according to claim 1 , wherein the rotating body is an image carrier that carries an image. The rotating body, an image forming apparatus according to claim 1 or 2, characterized in that a driving roller that drives the belt member. The image forming apparatus according to any one of claims 1 to 3, characterized in that it has a flywheel provided on a rotary shaft of the rotary member outside than the drive gear with respect to the rotational axis of the rotating body .

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