JP2016114239A - Drive transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a drive transmission device which accurately holds a shaft with a simple and inexpensive structure.SOLUTION: A drive transmission device has a drive shaft support member 8 attached to a drive frame 2 and used to rotatably support a drive shaft 7. The drive shaft support member 8 has: bearing surfaces 8c, 8d which are used to rotatably hold the drive shaft 7 and arranged on the same straight line C; and a boss part 8e which has a center part on the same straight line C to position the drive shaft support member 8 in the drive frame 2.SELECTED DRAWING: Figure 5

Description

  The present invention relates to a drive transmission device for transmitting rotational drive.

  In a drive transmission device for transmitting rotational driving using a shaft and a gear fixed to the shaft, a configuration in which two points of the shaft are rotatably supported using a bearing supported on a support side plate (frame) or the like. Is generally used. It is important for the function for rotation to hold | maintain the axis center of the axis | shaft which transmits rotation with high precision. For example, if the shaft is tilted in the attached state, there is a risk that abnormal wear or abnormal noise may occur due to contact between the gear fixed to the shaft and the gear meshing with the gear.

  As a support method in which the inclination of the shaft is suppressed, for example, Patent Document 1 proposes a configuration in which a gap is set between the bearing and the shaft and the shaft center is automatically aligned by the planetary gear.

JP 2007-212806 A

  In order to suppress the inclination of the rotating member attached to the drive shaft that transmits the rotation, a support structure that suppresses the inclination of the drive shaft is required. On the other hand, in order to use the alignment mechanism proposed in Patent Document 1, at least three planetary gears, two bearings, one cylindrical member, and other components are required. It is desired to suppress the inclination of the drive shaft with fewer components.

  The present invention has been made in view of such a situation, and an object thereof is to provide a drive transmission device that can suppress the inclination of the drive shaft with a small number of components.

  A drive transmission device as means for solving the problems includes a shaft that is rotatably supported, a drive shaft support member that rotatably supports the shaft, and a mounted member to which the drive shaft support member is attached. A rotation member attached to the shaft for transmitting a driving force, and the attached member has a positioning hole for determining the position of the drive shaft support member, and the drive shaft support The member includes a first bearing portion having a first bearing surface that rotatably supports the shaft, a second bearing portion having a second bearing surface that rotatably supports the shaft, and the first A connecting portion that connects the bearing portion and the second bearing portion, and a positioning portion that is fitted in the positioning hole to determine the position of the drive shaft support member with respect to the attached member, The first bearing portion and the second shaft And the first bearing surface and the second bearing surface are spatially separated in the thrust direction of the shaft, and the first bearing surface and the positioning portion are integrally formed. The shaft center of the bearing surface, the shaft center of the second bearing surface, and the center of the positioning portion are on the same straight line.

  A drive shaft support member in which two bearing surfaces, a positioning portion, and a connecting portion are integrally formed, and the shaft center of the two bearing surfaces and the center of the positioning portion are on the same straight line is attached to the member to be attached. Since the drive shaft support member rotatably supports the shaft, the tilt of the shaft can be suppressed by one drive shaft support member.

Overall view of image forming apparatus according to first to third embodiments Explanatory drawing of arrangement | positioning of the drive transmission device of Embodiment 1, and peripheral components The perspective view explaining the shape of the drive frame to which the drive transmission device is attached The figure explaining the shape of the drive-shaft support member of Embodiment 1. The figure explaining the attachment state of the drive shaft support member of Embodiment 1. The figure explaining the advantage of the present invention over the conventional shaft support method The figure explaining the shape of the drive-shaft support member of Embodiment 2. The figure explaining the shape of the drive-shaft support member of Embodiment 3. Sectional drawing explaining the shape of the rotation member of Embodiment 3. The figure explaining the correctness of the attachment direction of the rotation member of Embodiment 3. The figure explaining the shape of the rotation member of Embodiment 3, and a drive shaft support member

  First, an example of a basic configuration of an image forming apparatus including a drive transmission device according to an embodiment of the present invention will be described with reference to FIG.

  A printer 50 that is an image forming apparatus is provided with a paper feed cassette 20 that is a sheet storage device that can store a sheet bundle P so that the sheet bundle P can be pulled out. The sheet bundle P accommodated in the sheet feeding cassette 20 is sent out one by one by the sheet feeding unit 50C toward the image forming unit 50B. The sheet fed by the sheet feeding unit 50 </ b> C is conveyed to the conveyance roller pair 41.

  An alignment roller pair (registration roller pair) 507 is arranged downstream of the conveyance roller pair 41 in the sheet conveyance direction. The sheet sent out by the conveying roller pair 41 is abutted against the nip of the stopped alignment roller pair, thereby forming a loop on the sheet. By forming a loop in the sheet, the entire area of the leading edge of the sheet is abutted along the nip of the alignment roller pair, and the skew of the leading edge of the sheet is corrected. After the skew of the leading edge of the sheet is corrected, the alignment roller 507 starts to rotate, and the sheet is sent to the image forming unit 50B.

  The image forming unit 50B forms an image on a sheet by an electrophotographic method, and transfers the toner image formed on the image carrier to the sheet in the transfer unit. Further, the toner image is fixed on the sheet by the fixing unit 511. In this embodiment, the image forming unit is not limited to the electrophotographic image forming unit, and may be an image forming unit using another image forming method such as an ink jet method.

  The sheet on which the image is formed by the image forming unit 50B is discharged onto the discharge tray 513 by the discharge roller 512.

  The sheet feeding unit 50C includes a separation unit including a pickup roller 4 as a feeding roller, a feed roller 5 as a conveyance roller, and a retard roller 6 as a separation roller. The pickup roller 4 is pressed against the uppermost sheet P1 of the sheet bundle P stacked on the tray of the sheet feeding cassette 20 and rotates to feed the sheet P1. The feed roller 5 and the retard roller 6 separate the sheets fed by the pickup roller 4 one by one, and further feed the separated sheets toward the conveying roller pair 41. The drive motor M inputs a rotational force to the pickup roller 4 via a drive transmission device 1 described later, and rotates the pickup roller 4. The drive transmission device 1 is fixed to the image forming apparatus by attaching the drive frame 2 shown in FIG. 2 to a body frame (not shown).

(Embodiment 1)
Next, the drive transmission device 1 according to the first embodiment will be described with reference to FIGS.

  The drive transmission device 1 according to the present embodiment includes a caulking shaft 3, an idler gear 13, a drive shaft 7, a drive shaft support member 8, drive gears 9a and 9b, and the like. In addition, the drive may be transmitted using a cam or a pulley. As shown in FIG. 3, a caulking hole 2a is formed in the drive frame 2 as a plate-like attached member to which the caulking shaft 3 and the drive shaft support member 8 are attached. The caulking shaft 3 is positioned and fixed perpendicularly to the plane portion of the drive frame 2 by being inserted into the caulking hole 2a and being caulked. The idler gear 13 is rotatably supported by inserting a through hole provided at the center into the caulking shaft 3.

  A drive shaft support member 8 is fixed to the drive frame 2 as a shaft support portion that supports a drive shaft 7 that is a shaft for transmitting drive. As shown in FIG. 3, a screw hole 2 c and a positioning hole 2 b for attaching the drive shaft support member 8 with screws 15 are formed in the plate-like drive frame 2. In addition, the screw hole 2c has a screw machined on the inner peripheral surface of the hole. Further, the drive frame 2 is provided with a mounting surface 2d to which the drive shaft support member 8 is attached in a flat shape.

  In FIG. 2, a pinion gear 12 is fixed to the shaft of the drive motor M, and the idler gear 13 of the drive transmission device 1 meshes with the pinion gear 12. Further, the idler gear 13 is engaged with a drive gear 9 a attached to the drive shaft 7. A drive input gear 14 is fixed to the support shaft of the pickup roller 4, and the drive input gear 14 meshes with the drive gear 9b. As described above, the drive gear 9 a and the drive gear 9 b are attached to the drive shaft 7 on both sides of the drive frame 2. With this configuration, the rotation of the motor M is transmitted to the pickup roller 4 through the gears 12, 13, 9 a, 9 b, 14 and the drive shaft 7.

  As shown in FIG. 4, in the drive shaft support member 8, bearing portions 8a and 8b and a connecting portion 8j are integrally formed (Integrally Forming). Bearing surfaces 8c and 8d for rotatably supporting the drive shaft 7 are formed on the bearing portions 8a and 8b, respectively. The fastening surface 8 g and the fastening hole 8 f are used for fixing the drive shaft support member 8 to the drive frame 2. The bearing surfaces 8c and 8d are formed so that their respective axes are on the same straight line C. The bearing portion 8b is provided with a boss portion 8e as a positioning portion for positioning on the drive frame 2. The boss 8e has a cylindrical shape in which the inner peripheral surface and the outer peripheral surface are formed concentrically (FIG. 4A). The axial center (center) of the outer peripheral surface of the boss 8e is arranged so as to be positioned on the same straight line C as the axial center of the bearing surfaces 8c and 8d. In the present embodiment, the inner surface of the boss portion 8e is a round hole having the same diameter as the bearing surface 8c and having the function of a bearing. However, any shape may be used as long as the insertion hole is larger than the outer diameter of the drive shaft 7. However, the drive frame 2 can directly support the radial load received by the bearing surface 8d by providing the bearing surface 8d on the inner peripheral surface of the boss portion 8e as in the present embodiment. Furthermore, the area of the bearing surface 8d can be increased without increasing the exclusive space of the drive shaft support member 8.

  The diameters of the bearing surfaces 8c and 8d need not be the same. For example, when the drive shaft 7 is a so-called stepped shaft having a different diameter depending on the position in the thrust direction, the diameters of the bearing surfaces 8c and 8d are different depending on each diameter.

A mounting surface 8h is formed on the outer surface of the bearing portion 8b. The attachment surface 8h is in contact with the attachment surface 2d (FIG. 3) of the drive frame 2 and is formed perpendicular to the same straight line C. With this configuration, when the drive shaft support member 8 is fixed to the drive frame 2, the straight line C through which the shaft centers of the bearing surfaces 8c and 8d and the shaft center of the boss portion 8e pass, and the planar portion of the plate-like drive frame 2 Is maintained in a vertical state.
FIG. 5 shows a state in which the drive shaft support member 8 is fixed to the drive frame 2.

  In this figure, the drive shaft support member 8 is positioned with respect to the drive frame 2 by fitting the outer peripheral surface of the boss portion 8 e into the positioning hole 2 b of the drive frame 2. Then, in the positioned state, the screw 15 is inserted into the fastening hole 8f and screwed into the screw hole 2c, whereby the screw fixes the surface to be fastened 8g to the drive frame 2. In this fixed state, the mounting surface 8h of the drive shaft support member 8 is in contact with the flat portion of the drive frame 2 without a gap.

  Thus, in a state where the drive shaft support member 8 is fixed to the drive frame 2, the drive shaft 7 is perpendicular to the plane of the drive frame 2. Further, the caulking shaft 3 that rotatably supports the idler gear 13 is also perpendicular to the plane of the drive frame 2. That is, when the drive shaft support member 8 is attached to the drive frame 2, the drive shaft 7 and the caulking shaft 3 are in a parallel state (see FIG. 2).

  The shape of the positioning portion is not limited to a cylindrical shape such as the boss portion 8e shown in FIG. The shape of the positioning portion may be any shape that partially protrudes from the attachment surface 8h and has a circular arc shape whose center is on the straight line C. For example, a so-called two-sided shape as shown in FIG.

  In the drive shaft support member 8, the bearing portions 8a and 8b including the bearing surfaces 8c and 8d are integrally formed of the same material. Here, since the bearing surfaces 8c and 8d slide with the drive shaft 7, the material of the drive shaft support member 8 is for industrial use such as sintered metal or conductive POM which contains oil in consideration of slidability and conductivity. Plastic is desirable. Concerning the electrical conductivity, the possibility that the drive shaft 7 is charged by sliding between the drive shaft 7 and the bearing surfaces 8a and 8b to affect peripheral electrical components is considered. Further, the surface 8s on which the bearing 8c slides with the drive gear 9a is formed in a stepped shape, which is easy to control the size of the surface 8s in order to accurately form the position of the drive gear 9a in the axial direction. It is to do.

  In the present embodiment, in the drive shaft support member 8, the bearing portions 8a and 8b, the fastening portion 8g, the boss portion 8e, and the connecting portion 8j are integrally formed with the same material (Integrally Forming). However, each part may be formed of a different material. For example, the bearing portions 8a and 8b may be formed using a material having excellent slidability optimum for the bearing, and the connecting portion 8j may be made of a material having excellent rigidity. In addition, as an integral forming method, any method can be used as long as the driving support member is integrally formed, such as integral molding by a mold, cutting, and molding by a 3D printer. Good.

  Further, as shown in FIG. 5, the drive shaft 7 is formed with pin holes in a direction perpendicular to the axial direction. The drive shaft 7 and the drive gear 9b are fixed by engaging the parallel pin 10 inserted into the pin hole with the groove of the drive gear 9b. On the other hand, the drive gear 9a has a known one-way clutch 11 embedded in the gear, and the gear and the one-way clutch 11 rotate together. The one-way clutch 11 is engaged with the drive shaft 7. The drive gear 9a is disposed so as to be sandwiched between the bearing portions 8a and 8b, and movement in the thrust direction shown in FIG. 4A is restricted. The end of the drive shaft 7 on the drive gear 9a side is fitted with a retaining member such as a C-ring so that the movement of the drive shaft 7 in the axial direction is restricted.

  Next, the operation in which the rotation of the motor M is transmitted to the pickup roller 4 will be described (FIG. 2). The pinion gear 12 rotates with the rotation of the motor M, and the idler gear 13 meshing with the pinion gear 12 rotates about the caulking shaft 3. Next, the drive gear 9a meshed with the idler gear 13 rotates. At this time, since the one-way clutch 11 is arranged to rotate in the drive transmission direction, the drive force is transmitted from the drive gear 9a to the drive shaft 7. Thus, the drive shaft 7 is rotated. When the drive shaft 7 rotates, the drive gear 9 b is rotated via the parallel pin 10, and the driving force is transmitted from the drive input gear 14 to the pickup roller 4. When the pickup roller 4 rotates with the sheet while the motor M is stopped, the rotation of the pickup roller 4 is not transmitted to the motor M because the one-way clutch 11 does not transmit rotation. Thus, in this embodiment, the one-way clutch 11 is used for the purpose of not transmitting the rotational force from the pickup roller 4 to the motor M. However, the present invention is not limited to this configuration, and a one-way clutch may be arranged in order to switch the presence or absence of drive transmission according to the rotation direction of the motor M.

  By the way, in order to smoothly transmit the driving force (rotation of the motor M) from the idler gear 13 to the driving gear 9a, it is important to support the shaft center of the driving shaft 7 with respect to the driving frame 2 with high accuracy. . For example, if the drive shaft 7 is tilted with respect to the drive frame 2, the alignment between the caulking shaft 3 and the drive shaft 7 is reduced, and the gears come into contact with each other, causing noise and abnormal wear on the gear tooth surfaces. There is a fear. Here, the alignment between the caulking shaft 3 and the drive shaft 7 is affected by the distance between the two points that support the shaft. When the positional deviations of the bearing and the support side plate are the same, the tilt of the shaft increases as the distance between the two points that support the shaft is shorter.

  In recent years, there has been an increasing demand for downsizing the apparatus, and a relatively short drive shaft may be used in order to save space. At this time, if the drive shaft is short, the distance between the two points that support the shaft is shortened, and the drive shaft is easily inclined accordingly.

  Therefore, the advantages of the present embodiment will be described with reference to FIG. 6 focusing on the inclination of the drive shaft 7 with respect to the drive frame 2. Note that FIG. 6 exaggerates the mounting backlash and the inclination of the shaft of each component for easy understanding.

  FIGS. 6A and 6B are configurations generally used in the prior art. Drive support plates 102 and 103 are disposed at both ends of the drive shaft 107, and the drive support plates 102 and 103 are respectively disposed. The bearings 104 and 104 are attached to the drive shaft 107 to support them.

In FIGS. 6A and 6B, the distance between the support of the drive shaft (between the bearings 104 and 104) is L. Further, the play between the drive shaft 107 and the bearings 104 and 104 is α1 and α2, the play between the bearings 104 and 104 and the drive support plates 102 and 103 is β1 and β2, and the drive support plates 102 and 103 are misaligned. Let the amount be γ1. At this time, the maximum angle θ1 at which the axis can tilt is (Equation 1) θ1 = arctan {(α1 + α2 + β1 + β2 + γ1) / L}
It can be expressed as. Since L cannot be a value larger than the length of the shaft, L becomes smaller as the shaft is shortened. That is, θ1 increases as the axis is shortened. In this configuration, when L is made smaller than before by downsizing the drive transmission device, the axis inclination θ1 increases unless values such as α1, β1, and γ1 are reduced. Here, α1, α2, β1, β2, and γ1 are numerical values that depend on component accuracy and assembly accuracy, and in order to reduce the numerical values, the accuracy must be improved. As means for improving the accuracy of parts and assembling, it is conceivable to select parts and introduce a high-performance processing machine, but these measures lead to an increase in cost.

  As described above, in the conventional configuration, when the drive transmission device is reduced in size, it is necessary to increase the cost for maintaining the position accuracy of the drive shaft.

On the other hand, the support structure of the drive shaft 7 in the present embodiment is shown in FIGS. 6C and 6D, the backlashes of the bearing surfaces 8c and 8d and the drive shaft 7 are α3 and α4, and the backlash between the boss portion 8e of the drive shaft support member 8 and the positioning hole 2b of the drive frame is β3. The amount of positional deviation between the surfaces 8c and 8d is γ2. At this time, the maximum angle θ2 at which the axis can tilt is (Expression 2) θ2 = arctan {(α3 + α4 + γ2) / L}
It can be expressed as.

  Comparing Equation 1 and Equation 2, it can be seen that there is no term corresponding to β1 and β2 in θ2, and the mounting backlash between the drive shaft support member 8 and the drive frame 2 does not affect the inclination of the drive shaft 7. Further, γ2 is a positional deviation amount between two parts in one part, whereas γ1 is a positional deviation quantity between the two parts. Accordingly, γ1 is larger than γ2 because the component accuracy and assembly accuracy have an extra influence.

  From the above, if the conditions such as L that depend on the size of the drive transmission device and α1, α2, etc. that depend on the component accuracy are the same, θ2 is smaller than θ1, and the inclination of the drive shaft is reduced compared to the conventional case It becomes possible to do. This advantage is particularly effective when L must be set shorter than in the past due to space saving of the drive transmission device. That is, the inclination of the shaft that increases when L is reduced can be reduced without costly improving the component accuracy. In addition, the components for holding the drive shaft are one drive frame and one drive shaft support member, and fewer components are required than in the conventional configuration. Also in this respect, the cost can be reduced as compared with the conventional configuration.

  In order to maintain the position of the drive shaft 7 with respect to the drive frame 2 with high accuracy, it is also important to reduce the positional deviation between the center position of the outer peripheral surface of the boss 8e and the shaft centers of the bearing surfaces 8c and 8d as much as possible. . This is because the shaft centers of the bearing surfaces 8c and 8d are positioned on the drive frame via the outer peripheral surface of the boss 8e. Hereinafter, the advantage which arises by arrange | positioning the center position of the outer peripheral surface of the boss | hub 8e on the straight line C like this embodiment is demonstrated.

  Suppose that the center position of the outer peripheral surface of the boss 8e is arranged at a position not on the straight line C as shown in FIG. At this time, Δ is a design deviation between the center position of the outer peripheral surface of the boss 8e and the straight line C. In order to accurately determine the position of the straight line C with respect to the positioning hole 2b, not only the magnitude of Δ but also the direction must be strictly managed. As the number of parts to be strictly controlled increases, the manufacturing cost of parts increases. In addition, when the drive shaft support member is integrally molded with resin (Integrally Molding), the thickness from the outer peripheral surface of the boss to the bearing surface is not uniform. This is because the amount of shrinkage after molding changes in accordance with the thickness of the resin, so that distortion occurs after molding in a portion where the thickness is not uniform. Naturally, when distortion occurs, the magnitude and direction of Δ change, and the bearing surface cannot be accurately positioned. By disposing the center of the outer peripheral surface of the boss 8e on the straight line C as in the present embodiment, these problems can be solved.

  The amount of positional deviation between the center of the outer peripheral surface of the boss 8e and the shaft center of the bearing surfaces 8c and 8d is within a range where the gear 13 and the gear 9a or the gear 9b and the gear 14 mesh smoothly without tooth skipping or tooth bottom contact. There must be. As a specific example, for example, in the case of the gear of module 1.0, it is desirable that the distance between the axes is an error of 0.2 mm or less with respect to the design value. Further, considering that the displacement of the hole position of the drive frame itself is affected, the amount of displacement between the center of the outer peripheral surface of the boss 8e and the shaft center of the bearing surfaces 8c and 8d is within 0.1 to 0.2 mm. It is desirable to suppress. Here, the advantage that the bearing surface and the positioning boss 8e are integrally formed (Integrally Forming) as in the present embodiment will be described. For example, when the positioning boss 8e and the bearing portion 8b are separate parts, these two parts are assembled and used. Here, the positions of the outer peripheral surface of the positioning boss 8e and the bearing surface 8d are shifted according to the accuracy with which the positioning boss 8e and the bearing portion 8b are assembled. Similarly, when the bearing portions 8a and 8b are separate parts, the positions of the axis lines of the bearing surfaces 8c and 8d are shifted according to the assembling accuracy.

  On the other hand, if the bearing portions 8a and 8b and the positioning boss 8e are integrally formed (Integrally Forming), it is possible to remove the positional deviation due to the assembly accuracy. Moreover, it is relatively easy to suppress the dimensional deviation of one component to about 0.1 mm. Therefore, by integrally forming the bearing portions 8a and 8b and the positioning boss 8e (Integrally Forming), the target accuracy can be satisfied while minimizing the cost.

  In this embodiment, the member that is rotated by the drive shaft is a gear. However, the present invention can be similarly applied to any rotatable member such as a cam or roller. In this embodiment, the drive transmission device for transmitting the drive to the pickup roller 4 has been described. However, the present invention is not limited to this, and the conveyance roller for conveying the sheet may be driven. Furthermore, it may be used anywhere as long as it is configured to transmit the rotational drive to the rotating member using the shaft regardless of the conveying roller.

(Embodiment 2)
A second embodiment will be described with reference to FIG. In this embodiment, since only the shape of the drive shaft support member is different from that of the first embodiment, the difference in the shape of each part will be described in detail.

  As shown in FIG. 7, the drive shaft support member 16 in the second embodiment is integrally formed with bearing portions 16a and 16b, a positioning portion 16e and the like, as in the first embodiment. Moreover, it has the fastening part 16g in which the fastening hole 16f was formed. Further, as in the first embodiment, the center of the outer peripheral surface of the boss portion 16e is arranged on the same straight line C as the axis of the bearing surfaces 16c and 16d.

  However, in the first embodiment, the bearing portion 8a of the drive shaft support member 8 is supported in a cantilever shape, whereas in the second embodiment, the bearing portion 16a is supported from both sides (supported on both sides). By supporting the bearing portion 16a from both sides in this way, the rigidity in the direction in which the drive shaft 7 falls can be increased.

  When the rigidity is increased, the deformation of the driving support member can be reduced even when the transmitted driving torque is high, but the occupied space is slightly larger than that of the first embodiment. Therefore, the connection shape of the bearing portions 8a and 8b may be determined according to the torque transmitted by the drive shaft 7 and the space that can be occupied.

  In addition, since the effect of this embodiment arises by arrange | positioning the shaft center of several bearings on the same straight line in one component, the shape of a drive shaft support member is limited to the shape described in Embodiment 1 and Embodiment 2. Is not to be done. For example, three or more bearing surfaces may be arranged. However, it is necessary to arrange the axis of each bearing surface on the same straight line. Further, it is desirable that the fastening portion by the screw 15 is increased or decreased depending on the shape and size of the drive shaft support member, and the drive shaft support member is securely fixed to the drive frame 2. For example, in the second embodiment, in consideration of the fact that the drive shaft support member is larger than that in the first embodiment, the number of fastening points is increased to two to achieve secure fixing.

(Embodiment 3)
A third embodiment will be described. In the first embodiment, the configuration in which the gear 9a that rotates integrally with the one-way clutch is disposed between the two bearing portions 8a and 8b has been described (FIG. 5). Here, when the mounting direction of the one-way clutch with respect to the shaft is reversed, the direction in which the drive can be transmitted is also reversed. Therefore, if the mounting direction is wrong, the drive cannot be transmitted normally. This embodiment pays attention to this problem, and adds a configuration for preventing an error in the attachment direction of the one-way clutch to the first embodiment. Since the configuration is the same as that of the first embodiment except for the configuration for preventing an error in the attachment direction of the one-way clutch, the description thereof is omitted.

  First, the shape of the drive shaft support member 17 in Embodiment 3 will be described with reference to FIG. The coordinate axes are the XY axes shown in FIG. Here, the X direction coincides with the direction of the straight line C (thrust direction).

  Although the bearing portion 17a is spatially separated from the bearing portion 17b in the direction of the straight line C, it is integrated with the bearing portion 17b by being supported by the connecting portion 17j. The bearing portion 17a is provided with a contact surface 17s that contacts the gear 9a.

  The connecting portion 17j is provided with a protrusion 17i as a second portion. As shown in FIG. 8B, the shortest distance Y1 from the straight line C to the first portion 17k is larger than the shortest distance Y2 from the straight line C to the protrusion 17i.

  On the other hand, the one-way clutch 11 is embedded in the gear 9a disposed between the bearing portions 17a and 17b, and the gear 9a and the one-way clutch 11 rotate together (FIG. 9). When the shaft 7 is inserted with the gear 9a placed between the bearing portions 17a and 17b, if the mounting direction is wrong, the mounting direction of the one-way clutch 11 is also wrong. Therefore, in order to prevent an error in the attachment direction of the one-way clutch 11, it is only necessary to prevent the gear 9a from being attached to the shaft 7 in the wrong direction. A configuration for this will be described below.

  As shown in FIG. 9, the gear 9a has a first rotating portion 91 and a second rotating portion 92 having different radii, and the radii are R1 and R2. The overall width of the gear 9a is X1.

  FIG. 10 is a diagram illustrating a state in which the gear 9a is correctly mounted on the drive shaft 7 (FIG. 10A) and a state in which the mounting direction of the gear 9a is incorrect (FIG. 10B). FIG. 10B is a virtual diagram for explaining the effect of the present embodiment. In practice, the gear 9a and the projection 17i interfere with each other as described below. I can't do it.

  In FIG. 10A, since the dimensional relationship between the gear 9a and the drive shaft support member is expressed by the following mathematical formula 3, the drive shaft support member 17 and the gear 9a can be assembled without interference.

(Expression 3) R1 <Y1 and R2 <Y2
In FIG. 10B, since the larger radius R1 of the gear 9a is larger than the dimension Y2 of the drive shaft support member 17, the gear 9a and the protrusion 17i interfere with each other. Here, when the dimension X1 of the gear 9a is smaller than the dimension X2 of the drive shaft support member, the gear 9a and the protrusion 17i do not interfere even when the gear 9a is attached in the wrong direction as shown in FIG. .

  Therefore, in the present embodiment, X1 is set to a size larger than X2, so that when the gear 9a is attached in the wrong direction, it is set to reliably interfere with the protrusion 17i.

  From the above, the condition for preventing an error in the mounting direction of the gear 9a is the following Expression 4.

(Equation 4) R1> Y2 and X1> X2
In the present embodiment, the gear 9a is configured so that the gear 9a cannot be attached in the wrong direction by setting the radius of the gear 9a in two stages and providing a protrusion on the drive shaft support member 17. Is not limited to this embodiment.

  For example, as shown in FIG. 11 (a), the drive shaft support member may be provided with a recess 18a, and the protrusion 19a of the rotating member may enter the recess 18a. In this case, if the mounting direction of the rotating member is wrong, the convex portion 19a cannot enter the concave portion 18a and cannot be assembled, so that it is possible to prevent the mounting direction from being wrong. Similarly, as shown in FIG. 11 (b), it is possible to prevent the mounting direction from being mistaken even when the concave portion 18b is provided in the rotating member and the convex portion 19b of the drive shaft support member enters the concave portion 18b.

  In the first to third embodiments, the drive transmission device for transmitting the drive to the pickup roller 4 has been described. However, the present invention is not limited to this, and the conveyance roller for conveying the sheet is driven. Also good. Furthermore, regardless of the transport roller, any configuration may be used as long as the drive is transmitted to the rotating member using the shaft. Further, the configuration for preventing the assembly error described in the third embodiment may be applied to the shape of the drive shaft support member described in the second embodiment.

2 Drive frame (attached member)
2b Positioning hole 2c Screw hole 8 Drive shaft support member (shaft support part)
8a, 8b Bearing part 8c, 8d Bearing 8e Boss part (protrusion part)
8g Fastening portion 8h Mounting surface 16 Drive shaft support member (shaft support portion)
16a, 16b Bearing part 16c, 16d Bearing 16e Boss part (protrusion part)
16g fastening part

Claims (16)

A pivotally supported shaft;
A drive shaft support member for rotatably supporting the shaft;
A mounted member to which the drive shaft support member is mounted;
A rotating member attached to the shaft for transmitting a driving force;
Have
The attached member has a positioning hole for determining the position of the drive shaft support member;
The drive shaft support member is
A first bearing portion having a first bearing surface that rotatably supports the shaft;
A second bearing portion having a second bearing surface that rotatably supports the shaft;
A connecting portion for connecting the first bearing portion and the second bearing portion;
In order to determine the position of the drive shaft support member with respect to the attached member, the positioning portion fitted in the positioning hole,
The first bearing part, the second bearing part, the connecting part and the positioning part are integrally formed,
The first bearing surface and the second bearing surface are spatially separated in the thrust direction of the shaft,
The drive transmission device according to claim 1, wherein an axis of the first bearing surface, an axis of the second bearing surface, and a center of the positioning portion are on the same straight line. The shape of the positioning portion is an arc shape,
The drive transmission device according to claim 1. The drive shaft support member is made of a conductive material,
The drive transmission device according to claim 1 or 2. The positioning part has an insertion hole inside,
The shaft passes through the insertion hole,
The drive transmission apparatus of any one of Claim 1 or 3. The insertion hole is a round hole formed with the same diameter as the first bearing surface,
The drive transmission device according to claim 4. The attached member is a plate-shaped frame,
The rotating member and other rotating members are attached to both sides of the shaft across the frame,
The drive transmission device according to any one of claims 4 and 5. The connecting portion has a fastening hole into which a screw is inserted and a fastening surface,
The attached member has a screw hole,
7. The drive shaft support member is fixed to the attached member by inserting the screw through the fastening hole and screwing into the screw hole. 7. Drive transmission device. The second bearing part is cantilevered by the connecting part,
The drive transmission device according to any one of claims 1 to 7. A caulking shaft fixed to the attached portion;
And another gear that rotates around the caulking shaft,
The rotating member includes a gear;
The drive transmission device according to any one of claims 1 to 8, wherein the gear is engaged with the other gear. The rotating member is disposed between the first bearing portion and the second bearing portion,
The drive transmission device according to any one of claims 1 to 9. The rotating member includes a one-way clutch,
The rotating member is disposed between the first bearing portion and the second bearing portion,
The drive transmission device according to any one of claims 1 to 10. The first bearing portion has a mounting surface perpendicular to the straight line;
The attached member has an attached surface to which the drive shaft support member is attached;
The positioning hole is provided in the mounting surface;
The mounting surface is in contact with the mounted surface,
The drive transmission device according to any one of claims 1 to 11. The rotating member has a first rotating part having a radius R1 and a second rotating part having a radius R2 smaller than R1,
The first rotating part and the second rotating part are arranged at different positions in the thrust direction,
The connecting portion has a first portion whose shortest distance from the straight line is larger than Y1 and a second portion whose shortest distance from the straight line is Y2 smaller than Y1,
The first part and the second part are arranged at different positions in the thrust direction;
When the width of the rotating member in the thrust direction is X1, and the length of the first portion in the thrust direction is X2,
R1 <Y1, R2 <Y2, R1> Y2, X1> X2
It is characterized by
The drive transmission device according to claim 10 or 11. The rotating member has a convex portion,
The drive shaft support member has a recess,
The convex portion has penetrated into the concave portion,
The drive transmission device according to claim 10 or 11. The rotating member has a recess;
The drive shaft support member has a convex portion,
The convex portion has penetrated into the concave portion,
The drive transmission device according to claim 10 or 11. The drive transmission device according to claim 1, wherein the drive shaft support member is integrally molded.

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