Photosensitive member unit, cartridge, and electrophotographic image forming apparatus

Abstract

The present disclosure provides a photosensitive member unit, an image forming apparatus including a first main assembly side helical gear portion and a second main assembly side helical gear portion that are coaxially rotatable, the photosensitive member unit including: a photosensitive member rotatable about a rotation axis thereof; a first unit-side helical gear portion; and a second unit-side helical gear portion, the twisting direction of the teeth of the second unit-side helical gear portion being the same as the twisting direction of the teeth of the first unit-side helical gear portion, the helical angle of the teeth of the second unit-side helical gear portion being greater than the helical angle of the teeth of the first unit-side helical gear portion, and wherein the helical angle of the teeth of the second unit-side helical gear portion is greater than the helical angle of the teeth of the first unit The first unit-side helical gear portion and the second unit-side helical gear portion are rotatable in a state where the first unit-side helical gear portion is engaged with the first main assembly-side helical gear portion and the second unit-side helical gear portion is engaged with the second main assembly-side helical gear portion.

Description

[0001] This application is a divisional application of the invention patent application with the application date of August 31, 2021, application number "202180018257.8", and invention name "Photosensitive member unit, box and electronic photographic imaging device". Technical Field

[0002] The present invention relates to a cartridge that can be mounted to and removed from an electrophotographic image forming apparatus, and to an electrophotographic image forming apparatus using the cartridge.

[0003] Electrophotographic image forming apparatuses form images on recording materials by using an electrophotographic image forming method. Examples of electrophotographic image forming apparatuses include, for example, electrophotographic copying apparatuses, electrophotographic printers (LED printers, laser beam printers, etc.), facsimile machines, word processors, and the like. Background Art

[0004] In an electrophotographic image forming apparatus (hereinafter, also simply referred to as an "image forming apparatus"), a toner image is formed on an electrophotographic photosensitive member (photosensitive drum or drum), and the toner image is directly or indirectly transferred onto a recording material, thereby forming an image on the recording material.

[0005] Generally, such an image forming apparatus needs to replenish toner (developer) and maintain various components. Therefore, there is a cartridge-type image forming apparatus in which a cartridge can be mounted to and removed from the image forming apparatus, and toner replenishment and maintenance operations are efficiently performed by replacing the cartridge.

[0006] The cartridge includes at least one of a drum and a processing device, and is detachably mounted to the main assembly of the imaging device (device main assembly). The processing device is a device for forming an image, and the processing devices acting on the drum mainly include a developing device, a charging device, an image transfer device, a charge elimination device, a cleaning device, and the like. Examples of cartridges include a process cartridge, a drum cartridge, a developer cartridge, and the like, wherein the process cartridge includes a drum and at least one processing device and can be integrally mounted to and removed from the device main assembly, the drum cartridge includes a drum, and the developer cartridge includes a developing device. According to this cartridge method, toner replenishment and maintenance operations of the imaging device can be easily performed.

[0007] As a structure for transmitting driving force from the main assembly of the apparatus to the cartridge, a gear as shown in Japanese Patent Application Laid-Open No. S63-4252 is used, and a coupling as shown in Japanese Patent Application Laid-Open No. H8-328449 is used. Summary of the Invention

[0008] [Problem to be solved]

[0009] An object of the present invention (this disclosure) is to provide improvements to a photosensitive member unit, a cartridge, or an electrophotographic image forming apparatus.

[0010] [Solution to the problem]

[0011] The present invention provides at least one photosensitive member unit, which can be detachably mounted to the main component of an imaging device, the imaging device including a first main component side bevel gear portion and a second main component side bevel gear portion that can rotate coaxially, the photosensitive member unit including: a photosensitive member, which can rotate around its rotation axis; a first unit side bevel gear portion, the first unit side bevel gear portion being used to mesh with the first main component side bevel gear portion; and a second unit side bevel gear portion, the second unit side bevel gear portion being used to mesh with the second main component side bevel gear portion, wherein the torsion direction of the teeth of the second unit side bevel gear portion is the same as the torsion direction of the teeth of the first unit side bevel gear portion, wherein the helix angle of the teeth of the second unit side bevel gear portion is greater than the helix angle of the teeth of the first unit side bevel gear portion, and wherein the first unit side bevel gear portion and the second unit side bevel gear portion are able to rotate in a state in which the first unit side bevel gear portion is meshed with the first main component side bevel gear portion and the second unit side bevel gear portion is meshed with the second main component side bevel gear portion.

[0012] [Effects of the Invention]

[0013] According to the present invention (this disclosure), there is provided an improvement in a photosensitive member unit, a cartridge, or an electrophotographic image forming apparatus. BRIEF DESCRIPTION OF THE DRAWINGS

[0014] Figure 1 It is a perspective view of a part which transmits driving force from the main assembly of the apparatus to the drum unit.

[0015] Figure 2 is a schematic cross-sectional view of the main components and box of the device.

[0016] Figure 3 is a cross-sectional view of the box.

[0017] Figure 4 It is an exploded perspective view of the box.

[0018] Figure 5 It is an exploded perspective view of the box.

[0019] Figure 6 It is an exploded perspective view of the cleaning unit.

[0020] Figure 7 It is a cross-sectional view from the main assembly of the device to the driving portion of the box.

[0021] Figure 8 It is a cross-sectional view of the main components of the equipment.

[0022] Figure 9 It is a cross-sectional view of the main components of the equipment.

[0023] Figure 10 It is a cross-sectional view of the main components of the equipment.

[0024] Figure 11 It is an exploded perspective view of the main components of the device.

[0025] Figure 12 It is a perspective view of the drive transmission portion of the main assembly of the device.

[0026] Figure 13 This is a schematic diagram of the drive transmission gears of the main assembly of the equipment.

[0027] Figure 14 This is a schematic diagram of the drive transmission structure from the drive transmission gear to the drive side flange.

[0028] Figure 15 is a diagram showing a drive transmission structure from the driving side flange to the developing roller.

[0029] Figure 16 It is a schematic diagram of the drive transmission gear and the drive side flange, and a cross-sectional view of the drive transmission gear.

[0030] Figure 17 It is a cross-sectional view of the drive transmission gear and the drive side flange.

[0031] Figure 18 It is a cross-sectional view of the drive transmission gear and the drive side flange.

[0032] Figure 19 It is a side view of the drive transmission gear and the drive side flange.

[0033] Figure 20 It is a side view of the drive transmission gear and the drive side flange.

[0034] Figure 21 is an illustration of the drive transmission gear and the drive side flange.

[0035] Figure 22 is an illustration of the drive transmission gear and the drive side flange.

[0036] Figure 23 is a cross-sectional view of the box.

[0037] Figure 24 It is a schematic diagram of the drive transmission structure.

[0038] Figure 25 is a diagram of the drive transmission structure.

[0039] Figure 26 It is a cross-sectional view of the drive transmission part.

[0040] Figure 27 is a graph showing the deformation amount of the coupling driver and the drive transmission gear.

[0041] Figure 28 is a diagram of the retraction mechanism.

[0042] Figure 29 is a schematic diagram illustrating engagement between the driving side flange and the developing roller gear.

[0043] Figure 30 is a perspective view of the box.

[0044] Figure 31 It is a cross-sectional view of the drive transmission gear and the drive side flange.

[0045] Figure 32 is an illustration of the drive side flange.

[0046] Figure 33 2 is a cross-sectional view of the drive-side flange and the drive transmission gear, and a graph showing changes in the number of meshing teeth.

[0047] Figure 34 2 is a cross-sectional view of the drive-side flange and the drive transmission gear, and a graph showing changes in the number of meshing teeth.

[0048] Figure 35 is a perspective view of the drive side flange.

[0049] Figure 36 is a schematic diagram showing engagement between the drive transmission gear and the drive-side flange.

[0050] Figure 37 is a perspective view of an imaging device.

[0051] Figure 38 is a schematic diagram illustrating meshing engagement between the drive transmission gear and the drive-side flange.

[0052] Figure 39 It is a cross-sectional view of the drive transmission gear and the drive side flange.

[0053] Figure 40 It is a cross-sectional view of the drive transmission gear and the drive side flange.

[0054] Figure 41 It is a cross-sectional view of the drive transmission gear and the drive side flange.

[0055] Figure 42 It is a perspective view of the driving side flange and a cross-sectional view of the drive transmission gear and the driving side flange.

[0056] Figure 43 It is a cross-sectional view of the driving side flange and a cross-sectional view of the drive transmission gear and the driving side flange.

[0057] Figure 44 is a partial perspective view of the box.

[0058] Figure 45 It is a partial cross-sectional view near the drum of the cartridge, and is a diagram showing the drum and the developing roller.

[0059] Figure 46 It is a cross-sectional view of the drive transmission gear and the drive side flange.

[0060] Figure 47 This is a schematic diagram of the drive transmission gear and the drive-side flange.

[0061] Figure 48 It is a cross-sectional view of the driving side flange, and a cross-sectional view of the drive transmission gear and the driving side flange.

[0062] Figure 49 is a graph of drive transfer error when misaligned.

[0063] Figure 50 It is a schematic cross-sectional view of the main assembly and box of the device.

[0064] Figure 51 It is an exploded perspective view of the cleaning unit.

[0065] Figure 52 1 and 2 are a perspective view of a drum supporting member, a sectional view of a driving side flange and the drum supporting member, and a partial sectional view of a cartridge.

[0066] Figure 53 It is an exploded perspective view of the main components of the device.

[0067] Figure 54 It is a schematic cross-sectional view of the gear portion of the drive transmission gear, a schematic cross-sectional view of the gear portion of the driving side flange, and a schematic cross-sectional view of the gear portion of the drive transmission gear and the gear portion of the driving side drum flange.

[0068] Figure 55 It is a schematic cross-sectional view of the gear portion of the drive transmission gear and the gear portion of the driving side drum flange.

[0069] Figure 56 It is a perspective view of a transmission system for driving a developing roller, a partial perspective view of a developing unit, and a perspective view of a cartridge.

[0070] Figure 57 It is a partial perspective view of the main components of the device.

[0071] Figure 58It is a cross-sectional view of the cleaning unit and the drive transmission gear.

[0072] Figure 59 is a partial perspective view of the box.

[0073] Figure 60 is a cross-sectional view of the drum unit.

[0074] Figure 61 It is a partial perspective view of the drum unit.

[0075] Figure 62 It is a sectional view of the second gear portion and the second main assembly gear portion.

[0076] Figure 63 It is a partial perspective view of the drum unit.

[0077] Figure 64 is a side view of the cleaning unit.

[0078] Figure 65 It is an exploded perspective view of the cleaning unit.

[0079] Figure 66 It is a partial cross-sectional view of the cleaning unit.

[0080] Figure 67 It is a partial cross-sectional view of the cleaning unit.

[0081] Figure 68 is a sectional view showing an engagement state between the drum unit and the drive transmission gear.

[0082] Figure 69 is a sectional view showing an engagement state between the drum unit and the drive transmission gear.

[0083] Figure 70 It is an exploded perspective view of the cleaning unit.

[0084] Figure 71 is a sectional view showing an engagement state between the drum unit and the drive transmission gear.

[0085] Figure 72 It is a partial perspective view of the drum unit.

[0086] Figure 73 It is an exploded perspective view of the cleaning unit.

[0087] Figure 74 is a diagram of the drum unit meshingly engaged with the drive transmission gear.

[0088] Figure 75 is a sectional view showing an engagement state between the drum unit and the drive transmission gear.

[0089] Figure 76 It is a partial perspective view of the drum unit.

[0090] Figure 77 It is an exploded perspective view of the cleaning unit and drum unit.

[0091] Figure 78 is a cross-sectional view of the cleaning unit.

[0092] Figure 79 is a sectional view showing an engagement state between the drum unit and the drive transmission gear.

[0093] Figure 80 is a sectional view showing an engagement state between the drum unit and the drive transmission gear.

[0094] Figure 81 It is a partial perspective view of the drum unit.

[0095] Figure 82 It is a partial perspective view of the drum unit.

[0096] Figure 83 It is a partial perspective view of the drum unit.

[0097] Figure 84 is a cross-sectional view of the drum unit.

[0098] Figure 85 This diagram shows the drum unit assembled to the cleaning unit.

[0099] Figure 86 It is a cross-sectional view of the drive side flange and the drive transmission gear.

[0100] Figure 87 It is a cross-sectional view of the drive side flange and the drive transmission gear.

[0101] Figure 88 It is a partial perspective view of the drum unit.

[0102] Figure 89 It is a cross-sectional view of the drive side flange.

[0103] Figure 90 This diagram shows the drum unit assembled to the cleaning unit.

[0104] Figure 91 It is a cross-sectional view of the drive side flange and the drive transmission gear.

[0105] Figure 92 is a side view of the cleaning unit.

[0106] Figure 93 It is an exploded perspective view of the cleaning unit and the driving side drum flange.

[0107] Figure 94 is an exploded perspective view of the drum support unit.

[0108] Figure 95 It is a partial cross-sectional view of the cleaning unit.

[0109] Figure 96 is a diagram of the cleaning unit.

[0110] Figure 97 It is a partial cross-sectional view of the cleaning unit.

[0111] Figure 98 is a diagram of the box and the main components of the device.

[0112] Figure 99 is an illustration of the drive side drum flange 2463 engaged with the drive transfer gear.

[0113] Figure 100 is a schematic sectional view of the meshing engagement portion between the driving side drum flange and the drive transmission gear.

[0114] Figure 101 is a diagram of the cleaning unit.

[0115] Figure 102 It is an exploded perspective view of the cleaning unit and drum unit.

[0116] Figure 103 It is a partial cross-sectional view of the cleaning unit.

[0117] Figure 104 is a perspective view showing a cleaning unit and a drive transmission gear.

[0118] Figure 105 It is a schematic cross-sectional view of the meshing engagement portion between the drive gear and the idler gear and the drive transmission gear.

[0119] Figure 106 It is a schematic cross-sectional view of the meshing engagement portion between the drive gear and the idler gear and the drive transmission gear.

[0120] Figure 107 It is a schematic cross-sectional view of the meshing engagement portion between the drive gear and the idler gear and the drive transmission gear.

[0121] Figure 108 It is an exploded perspective view of the cleaning unit and drum unit.

[0122] Figure 109 is a diagram illustrating the engagement state between the cleaning unit and the drive transmission gear.

[0123] Figure 110 This is a view of the box viewed in the direction of the rotation axis of the drum.

[0124] Figure 111 It is a perspective view of the drive transmission mechanism of the cartridge.

[0125] Figure 112It is a perspective view of another structural example of the drive transmission gear.

[0126] Figure 113 It is a diagram of a box.

[0127] Figure 114 It is a diagram of a box. DETAILED DESCRIPTION

[0128] [Example 1]

[0129] <Overall Structure of Imaging Apparatus>

[0130] Figure 2 : is a cross-sectional view of an electrophotographic image forming apparatus (image forming apparatus) 100, and the plane of the cross section is perpendicular to the rotation axis L1 of the photosensitive drum 62 to be described below. The image forming apparatus 100 is a laser beam printer using an electrophotographic process, and a cartridge B including the photosensitive drum 62 is detachably mounted to the apparatus main assembly A. That is, the portion of the image forming apparatus 100 other than the cartridge B is the apparatus main assembly A. When the cartridge B is mounted in the apparatus main assembly A, an image can be formed on a recording material (sheet material) PA such as paper.

[0131] <Structure of the Main Assembly of the Device>

[0132] The apparatus main assembly A includes an exposure device (laser scanner unit) 3 and a sheet tray 4 for accommodating a sheet material PA. Furthermore, the apparatus main assembly A includes a pickup roller 5a, a feed roller pair 5b, a transfer guide 6, a transfer roller 7, a feed guide 8, a fixing device 9, a discharge roller pair 10, and a discharge tray 11, which are arranged in the specified order along the feed direction D of the sheet material PA. The fixing device 9 includes a heating roller 9a and a pressure roller 9b.

[0133] <Box structure>

[0134] Next, refer to Figure 3 、 4 , 5, 6 and 7, the overall structure of box B will be described. Figure 3 1 is a sectional view of the cartridge B taken along a plane perpendicular to a rotation axis L1 of a photosensitive drum 62 to be described later. Figure 4 and Figure 5 1 is an exploded perspective view showing the structure of the cartridge B. Figure 6 Part (a) is an exploded perspective view showing the structure of the drum unit 69. Figure 6 Part (b) is an exploded perspective view showing the structure of the cleaning unit. Figure 7 It is a sectional view of a driving unit that transmits driving force from the image forming apparatus A to the cartridge B. In this embodiment, screws and the like for connecting components will be omitted.

[0135] The cartridge B is a process cartridge and mainly includes an electrophotographic photosensitive member and a processing device that acts on the electrophotographic photosensitive member. The processing device includes a charging device, a developing device, and a cleaning device, which will be described below. The cartridge B has a structure mainly including a cleaning unit (drum unit) 60 and a developing unit 20, and the electrophotographic photosensitive member and the processing device are provided in these cleaning unit 60 or in the developing unit 20.

[0136] The longitudinal direction of the drum 62 is parallel to the direction of the rotation axis L1 of the drum 62 (the direction of the rotation axis). In the drum 62, the side to which the driving force is transmitted from the main assembly A of the device relative to the direction of the rotation axis is referred to as the drive side, and the opposite side of the drive side in the direction of the rotation axis is referred to as the non-drive side. In addition, the direction from the non-drive side toward the drive side (parallel to the rotation axis L1) on the rotation axis L1 of the drum 62 is the J direction, and the direction from the drive side toward the non-drive side is the H direction. When the J direction and the H direction are mentioned in the main assembly A of the device, they are defined as the same as the J direction and the H direction when the box B is installed in the main assembly A of the device.

[0137] <Cleaning Unit (Drum Unit)>

[0138] like Figure 3 As shown, the cleaning unit (drum unit) 60 includes a photosensitive drum 62, a charging roller 66, a cleaning member 77, and a cleaning frame (drum frame) 60a supporting them. The cleaning frame (drum frame) 60a includes a frame member 71 and a drum supporting member 73.

[0139] like Figure 6 As shown in part (a) of , the photosensitive drum (drum) 62, which is a rotatable member, is a cylindrical electrophotographic photosensitive member and is an aluminum cylinder with a photosensitive layer coated on the outer peripheral surface. The driving side flange (driving force receiving member) 63 is fixed to the end of the drum 62 on the driving side (one end side) by clamping, and the non-driving side flange 64 is fixed to the end on the non-driving side (the other end side) by clamping. The unit in which the drum 62, the driving side flange 63, and the non-driving side flange 64 are integrated (that is, a unit that can rotate integrally with the drum 62) is called a drum unit 69.

[0140] Typically, the cleaning unit 60 may be referred to as a drum unit, and in this case, from the viewpoint of the components provided in the cartridge B, the drum 62 is contrasted with the developing components in the developing unit 20, and the entire cleaning unit 60 is identified as a unit including the drum 62. Therefore, the drum unit as the name of the entire cleaning unit 60 is based on a concept different from that of the drum unit 69 in this embodiment (a unit that can rotate integrally with the drum 62). In the following description, the drum unit refers to a unit that can rotate integrally with the drum 62.

[0141] The drum 62, the drive side flange 63, and the non-drive side flange 64 rotate integrally around the drum's rotation axis L1. That is, the rotation axis of the drive side flange 63, the non-drive side flange 64, and the drum unit 69 is coaxial with the rotation axis L1 of the drum 62. Therefore, hereinafter, the rotation axis of the drum 62, the drive side flange 63, the non-drive side flange 64, and the drum unit 69 in the assembled drum unit 69 is referred to as the rotation axis L1.

[0142] In addition, the driving side flange 63 and the non-driving side flange 64 are fixed integrally in the direction of the rotation axis L1. The driving side flange 63 and the non-driving side flange 64 are made of resin material. The driving side flange 63 includes a first gear portion 63c and a second gear portion 63d, which will be described in detail below.

[0143] like Figure 6 As shown in part (b) of , the drum unit 69 is supported by the drum frame 60a (frame member 71 and drum supporting member 73) so as to be able to rotate around the rotation axis L1. Specifically, the driving side flange 63 is provided with a hole 63g coaxial with the rotation axis L1, and the shaft member 86 that is press-fitted into the drum supporting member 73 is inserted into the hole 63g, whereby the driving side flange 63 is rotatably supported by the drum supporting member 73. The non-driving side flange 64 has a hole (not shown) coaxial with the rotation axis L1, and the shaft member 78 that is press-fitted into the hole 71c of the frame member 71 is inserted into the hole, whereby the non-driving side flange is rotatably supported by the frame member 71. As described above, the non-driving side flange 64 and the driving side flange 63 are supported portions that are rotatably supported by the shaft members 86 and 78.

[0144] In addition, if Figure 7 As shown, the second gear portion 63d of the drive-side flange 63 has a protrusion 63d1 protruding in the H direction on its downstream end surface in the H direction, and a protrusion 63f protruding in the J direction on its upstream end surface in the H direction (downstream end in the J direction). Furthermore, the frame member 71 includes a rib 71p and a side wall 71m extending perpendicularly to the rotation axis L1. The protrusion 63d1 can contact the side surface of the rib 71p, and the protrusion 63f can contact the side surface of the side wall 71m. The drive-side flange 63 is slidably mounted between the rib 71p and the side wall 71m with a loose fit. Therefore, it is possible for the protrusion 63d1 to contact the side surface of the rib 71p or the protrusion 63f to contact the side surface of the side wall 71m. However, the assembly clearance (gap) is extremely small (maximum approximately 150 μm), and therefore, it can be said that the positioning is roughly the same in these cases. As described above, it can be said that the drum unit 69 including the driving-side flange 63 is positioned relative to the drum frame 60 a in the direction of the rotation axis L1 by the ribs 71 p and the side walls 71 m .

[0145] In the present embodiment, the longitudinal direction of the cartridge B, the drum frame 60 a and the frame member 71 is a direction parallel to the direction of the rotation axis L1 of the drum 62 .

[0146] In addition, if Figure 3 As shown, in the cleaning unit 60, a charging roller (charging member) 66 as a charging device and a cleaning member 77 as a cleaning device are arranged to contact the outer peripheral surface of the drum 62. The cleaning member 77 includes a rubber scraper 77a, which is a scraper-shaped elastic member made of rubber as an elastic material, and a support member 77b that supports the rubber scraper 77a. The rubber scraper 77a contacts the drum 62 in the opposite direction relative to the rotation direction of the drum 62. In other words, the rubber scraper 77a contacts the drum 62 so that its free end surface faces the upstream side of the rotation direction of the drum 62. The waste toner removed from the surface of the drum 62 by the cleaning member 77 is stored (accumulated) in the waste toner chamber 71b formed by the frame member 71 and the cleaning member 77. A sheet 65 for suppressing leakage of waste toner through the gap between the frame member 71 and the drum 62 is attached to the edge of the frame member 71 that contacts the drum 62.

[0147] The opposite end portions of the charging roller 66 in the direction of the rotation axis are rotatably supported by charging roller supports 67 supported by the frame member 71. The rotation axis of the charging roller 66 is substantially parallel to the rotation axis L1 of the drum 62. The charging roller supports 67 are pressed toward the drum 62 by the urging member 68, thereby pressing the charging roller 66 against the drum 62. The charging roller 66 is driven by the rotation of the drum 62.

[0148] <Developer Unit>

[0149] like Figure 3 As shown, the developing unit 20 includes a developing roller 32, a magnetic roller 34, a developing blade 42, a feeding member 43, a developing frame 20a supporting them, etc. The developing frame 20a includes a developing container 23, a bottom member 22, a supporting member 24 (see Figure 5 ), support member 37 (see Figure 4 ), the developing side cover 26 (see Figure 4 ) and the developing side cover 27 (see Figure 5 In the developing unit 20 , a toner supply chamber 28 and a toner chamber 29 are formed inside by the developing container 23 and the bottom member 22 .

[0150] like Figure 4 and Figure 5As shown, in the toner supply chamber 28, the opposite end portions of the developing roller 32 in the direction of the rotation axis are rotatably supported by the supporting member 24 and the supporting member 37. The supporting member 24 and the supporting member 37 are attached to the developing container 23. The developing roller (developing member) 32, which serves as a developing device, is a cylindrical member, and the magnetic roller 34 is disposed within the cylindrical member. The developing scraper 42 is provided to determine (control) the thickness of the toner (toner layer) carried on the surface of the developing roller 32.

[0151] The spacer members 38 are respectively attached to the end portions of the developing roller 32 in the direction of the rotation axis, and the distance between the surface of the developing roller 32 and the surface of the drum 62 is determined by the spacer members 38 being in contact with the surface of the drum 62. Specifically, the distance is determined so that a small gap is provided between the surface of the developing roller 32 and the surface of the drum 62.

[0152] In addition, if Figure 3 As shown in FIG. 2 , a sheet 33 for preventing toner from leaking through a gap between the developing frame 20 a and the developing roller 32 is attached to an edge portion of the bottom member 22 so as to contact the developing roller 32. Furthermore, a feeding member (stirring member) 43 is rotatably provided in the toner chamber 29. The feeding member 43 rotates to stir the toner contained in the toner chamber 29 and conveys the toner from the toner chamber 29 to the toner supply chamber 28.

[0153] <Connection between Cleaning Unit and Developing Unit>

[0154] The cartridge B is assembled by connecting the cleaning unit 60 and the developing unit 20. Figure 4 and 5 As shown, first, alignment is performed between the center of the first developing protrusion 26a of the developing container 23, the first developing protrusion being used for the first hanging hole 71i on the driving side of the frame member 71, and the center of the second supporting protrusion 27a being used for the second developing hanging hole 71j on the non-driving side. Then, by moving the developing unit 20 in the direction of arrow G, the first developing supporting boss 26a and the second developing supporting boss 27a are assembled into the first hanging hole 71i and the second hanging hole 71j. Thereafter, by assembling the drum supporting member 73 to the cleaning unit 60, the developing unit 20 is restricted from being disengaged from the cleaning unit 60. Thus, the developing unit 20 is movably connected to the cleaning unit 60. Specifically, the developing unit 20 is rotatably (tiltably) connected to the cleaning unit 60 around the first developing supporting boss 26a and the second developing supporting boss 27a.

[0155] In addition, if Figure 4As shown, the first end portion 46Rb of the driving side spring (urging member) 46R is fixed to the surface 26b of the developing side cover 26, and the second end portion 46Ra contacts the surface 71k of the frame member 71 of the cleaning unit 60. Figure 5 As shown, the first end portion 46Lb of the non-driving side spring (urging member) 46L is fixed to the surface 27b of the developing side cover 27, and the second end portion 46La contacts the surface 71L of the frame member 71. The non-driving side spring 46L and the driving side spring 46R are compression springs. The urging force of these springs generates an urging force between the developing frame 20a and the cleaning frame 60a, thereby pressing the developing roller 32 toward the drum 62. As described above, the spacing member 38 is pressed against the surface of the drum 62 and is maintained so that a gap exists between the surface of the developing roller 32 and the surface of the drum 62.

[0156] <Imaging Processing>

[0157] Next, the image forming process will be described. A control unit (not shown) receives a print command signal fed from a host computer or the like, and generates a print start signal based on the print command signal to start the image forming process.

[0158] When the image forming process starts, the drum 62 is first rotated in the direction of arrow R (see FIG. 1 ) at a predetermined peripheral speed (process speed). Figure 2 and 3 ) is rotationally driven. A charging bias is applied to the charging roller 66 to charge the surface (peripheral surface) of the drum 62 substantially uniformly. Figure 2 As shown, the exposure device (exposure means) 3 emits a laser beam L according to the image information to be printed. The laser beam L passes through a laser opening 71h provided in a frame member 71 of the cartridge B, is projected onto the surface of the drum 62 charged by the charging roller 66, and the surface of the drum 62 is scanned with the laser beam L. Thus, an electrostatic latent image corresponding to the image information is formed on the photosensitive layer on the surface of the drum 62.

[0159] On the other hand, Figure 3As shown, in the developing unit 20, the toner (developer) T in the toner chamber 29 is stirred and fed into the toner supply chamber 28 by the rotation of the feeding member 43. The toner T is carried on the surface of the developing roller 32 by the magnetic force of the magnetic roller (fixed magnet) 34. The developing roller 32 is a developer-carrying member that supports the toner T on its surface to visualize (develop) the electrostatic latent image formed on the drum 62 using the toner. The toner T is triboelectrically charged by the developing blade 42, and the developing blade 42 controls the thickness (layer thickness) of the toner T layer on the outer peripheral surface of the developing roller 32 to a desired thickness. The toner T carried on the surface of the developing roller 32 is then supplied and adhered to the area corresponding to the electrostatic latent image on the drum 62. As a result, the electrostatic latent image on the drum 62 is visualized (developed) as a toner image. It can be said that the drum 62 is an image-carrying member that carries the electrostatic latent image or toner image (developer image) on its surface.

[0160] In addition, if Figure 2 As shown, in synchronization with the output timing of the laser beam L, the sheet material PA stored in the sheet tray 4 at the lower portion of the apparatus main assembly A is fed out to the feed path in the main assembly A by the pickup roller 5a and the feed roller pair 5b. Then, the sheet material PA is guided by the transfer guide 6 and fed to the transfer nip provided between the drum 62 and the transfer roller (transfer device) 7. In this transfer nip, the toner image formed on the drum 62 is transferred onto the sheet material PA.

[0161] The sheet material PA onto which the toner image is transferred in the transfer nip is guided by a transfer guide 8 and conveyed to a fixing device (fixing means) 9. The sheet material PA then passes through a fixing nip provided between a heating roller 9a and a pressure roller 9b of the fixing device 9. By applying pressure and heat to the sheet material PA in this fixing nip, the toner image is melted onto the sheet material PA and fixed thereto. The sheet material PA that has passed through the fixing nip is fed to a discharge roller pair 10 and discharged onto a discharge tray 11.

[0162] On the other hand, Figure 3 As shown, after the sheet material passes through the transfer nip, the surface of the drum 62 comes into contact with the cleaning blade 77, and the toner remaining on the surface of the drum 62 is removed, so that the surface of the drum 62 can be used again for the above-mentioned image forming process. The toner removed from the drum 62 by the cleaning blade 77 is stored as waste toner in the waste toner chamber 71b of the cleaning unit 60.

[0163] In the present embodiment, at least the charging roller 66 , the exposure device 3 , the developing roller 32 , the transfer roller 7 , and the cleaning blade 77 are process devices acting on the drum 62 .

[0164] <Installation and Removal of the Cartridge>

[0165] Next, refer to Figure 8 、 Figure 9 and Figure 10 , the installation of box B on the main component A of the device will be described in detail. Figure 8 Part (a) is a sectional view of the driving side of the apparatus main assembly A in a state where the door 13 is open, and Figure 8 Part (b) is a sectional view of the non-driving side of the apparatus main assembly A in a state in which the door 13 is opened. Figure 8 Part (a) and Figure 8 The cross section of portion (b) is perpendicular to the rotation axis L1. Figure 9 It is a view showing the positioning of box B in the longitudinal direction (the direction of the rotation axis L1), and is a sectional view of the assembly part 15j of the device main component A cut along a horizontal plane parallel to the rotation axis L1 (parallel to the mounting surface of the device main component A). Figure 9 Part (a) shows the state immediately before the box B is assembled with the assembly portion 15j, and Figure 9 Part (b) shows the state in which the box B is assembled and engaged at the assembly portion 15j. Figure 10 Part (a) is a sectional view of the driving side of the apparatus main assembly A in a state where the door 13 is closed, and Figure 10 Part (b) is a sectional view of the non-driving side of the apparatus main assembly A in a state where the door 13 is closed. Figure 10 Part (a) and Figure 10 The plane of the cross section of portion (b) is perpendicular to the rotation axis L1.

[0166] First, the installation of box B on the main assembly A of the device will be described. The main assembly A of the device includes a first drive side plate 15 and a non-drive side plate 16, which sandwich the box B installed on the main assembly A of the device in the direction of the rotation axis L1. In addition, the door 13 for opening and closing the insertion opening 17 is rotatably mounted on the main assembly A of the device. The first drive side plate 15 is provided with an upper guide rail 15g and a lower guide rail 15h for guiding box B when installing and removing box B. The non-drive side plate 16 is provided with an upper guide rail 16d and a lower guide rail 16e for guiding box B when installing and removing box B. In addition, the drum supporting member 73 of box B is provided with a guided portion 73g and a rotation stop portion 73c, and the frame member 71 is provided with a positioned portion 71d and a rotation stop portion 71g. Therefore, the guided portion 73g and the rotation stopper portion 73c are arranged on the driving side of the cartridge B, and the guided portion 73g and the rotation stopper portion 73c are arranged on the non-driving side of the cartridge B.

[0167] When the door 13 of the apparatus main assembly A is opened and the insertion opening 17 formed between the first drive side plate 15 and the non-drive side plate 16 is opened, the cartridge B can be inserted into the apparatus main assembly A through the insertion opening 17 and can be removed from the apparatus main assembly A. At this time, the cartridge B can be inserted into and mounted on the apparatus main assembly A and removed from the apparatus main assembly A by moving the cartridge B in a direction substantially perpendicular to the rotation axis L1 of the drum 62. That is, the mounting direction M of the cartridge B to the apparatus main assembly A ( Figure 9 Part (a)) and the disassembly direction of the cartridge from the apparatus main assembly A (the direction opposite to the installation direction M) are directions substantially perpendicular to the rotation axis L1. The rotation axis L1 of the cartridge B installed in the apparatus main assembly A is parallel to the rotation axis L2 of the drive transmission gear 81, and therefore, the installation direction M of the cartridge B to the apparatus main assembly A and the disassembly direction of the cartridge from the apparatus main assembly A are substantially perpendicular to the rotation axis L2. In addition, when the cartridge B is installed to and disassembled from the apparatus main assembly A, the drum unit 69 is moved integrally with the cartridge B to the apparatus main assembly A, and is installed to and disassembled from the apparatus main assembly A. Therefore, the installation direction of the drum unit 69 to the apparatus main assembly A and the disassembly direction of the drum unit from the apparatus main assembly A are the same as the installation direction M of the cartridge B to the apparatus main assembly A and the disassembly direction of the cartridge from the apparatus main assembly A, respectively.

[0168] <Installation and Positioning of the Box>

[0169] When the cartridge B is inserted into the apparatus main assembly A through the cartridge insertion opening 17, the guided portion 73g and the rotation stop portion 73c on the drive side of the cartridge B are guided by the upper guide rail 15g and the lower guide rail 15h, respectively. The positioned portion 71d and the rotation stop portion 71g on the non-drive side of the cartridge B are guided by the upper guide rail 16d and the lower guide rail 16e. By guiding the cartridge B by the guide rails of the apparatus main assembly A and inserting the cartridge B in this manner, the installation of the cartridge B on the apparatus main assembly A is finally completed.

[0170] like Figure 9 As shown in parts (a) and (b) of the drawings, the drum supporting member 73 is provided with a mounted portion 73h serving as a positioned portion (axially positioned portion) to be positioned relative to the main assembly A of the device in the direction of the rotation axis L1. The mounted portion 73h has a concave shape (or a groove shape or a slit shape) that is concave in the mounting direction M (a direction perpendicular to the rotation axis L1). On the other hand, the first drive side plate 15 of the main assembly A of the device is provided with a mounting portion 15j that can be assembled with the mounted portion 73h. The mounting portion 15j has a protruding shape that protrudes in a direction opposite to the mounting direction MD.

[0171] During the process of inserting the cartridge B into the apparatus main assembly A, as shown in FIG. Figure 9As shown in part (b) of the embodiment, the assembled portion 73h is assembled with the assembly portion 15j, thereby determining the position of the cartridge B in the direction of the rotation axis L1 (the longitudinal direction of the cartridge B). The assembly between the assembled portion 73h and the assembly portion 15j is a loose fit, but the assembly play (clearance) is set to be extremely small (maximum 150 μm). Therefore, it can be said that regardless of whether the assembled portion 73h abuts the assembly portion 15j in the H direction or the J direction, the cartridge B is positioned in substantially the same position in the direction of the rotation axis L1.

[0172] In addition, if Figure 8 Part (a), Figure 8 Part (b) Figure 10 Part (a) and Figure 10 As shown in part (b), the first drive side plate 15 is provided with a positioning portion 15a, a positioning portion 15b and a rotation stop portion 15c, and the non-drive side plate 16 is provided with a positioning portion 16a, a positioning portion 16b and a rotation stop portion 16c. The cartridge pressing members 1 and 2 are mounted to opposite ends of the door 13 in the direction of the rotation axis of the door 13 so as to be movable (rotatable) relative to the door 13. In addition, the first drive side plate 15 and the non-drive side plate 16 are respectively provided with pressing springs 19 and 21.

[0173] In addition, if Figure 3 As shown, the drum supporting member 73 of the cartridge B has a pressed portion (urging force receiving portion) 73e, and the frame member 71 has a pressed portion (urging force receiving portion) 71n. The pressed portions 73e and 71n are provided in recessed portions on the driving side and the non-driving side of the cartridge B, respectively.

[0174] like Figure 10 Part (a) and Figure 10 As shown in part (b) of the drawing, by closing the door 13, the cartridge pressing members 1 and 2 are urged toward the cartridge B by the pressing springs 19 and 21. Also, the cartridge pressing members 1 and 2 abut against the pressed portions 73e and 71n, and are pressed by the urging forces of the pressing springs 19 and 21.

[0175] As a result, on the drive side, the positioned portion 73g of cartridge B contacts the positioning portions 15a and 15b of the apparatus main assembly A, and the rotation stop portion 73c contacts the rotation stop portion 15c of the apparatus main assembly A. As a result, the drive side portion of the drum frame 60a of cartridge B is positioned in a direction perpendicular to the rotation axis L1, and rotation around an axis parallel to the rotation axis L1 is restricted. On the non-drive side, the positioned portion 71d of cartridge B abuts the positioning portions 16a and 16b of the apparatus main assembly A, and the rotation stop portion 71g abuts the rotation stop portion 16c of the apparatus main assembly A. As a result, the non-drive side portion of the drum frame 60a of cartridge B is positioned in a direction perpendicular to the rotation axis L1, and rotation around an axis parallel to the rotation axis L1 is restricted.

[0176] By positioning the drum frame 60a of the cartridge B relative to the apparatus main assembly A in this manner, the drum unit 69 positioned relative to the drum frame 60a is also indirectly positioned relative to the apparatus main assembly A.

[0177] <Drive Transmission to Drum Unit>

[0178] Next, the structure for transmitting drive from the apparatus main assembly A to the drum unit 69 and the drum 62 will be described. Figure 1 It is a perspective view of a portion for transmitting drive from the apparatus main assembly A to the drum unit 69. Figure 11 1 is an exploded perspective view showing the supporting structure of the drive transmission gear 81 of the apparatus main assembly A. Figure 12 14. It is a perspective view showing the drive transmission unit of the apparatus main assembly A. Figure 13 Part (a) is a diagram schematically showing the drive transmission gear 81 of the apparatus main component A. Figure 13 Part (b) is a diagram schematically showing the drive side flange 63 of the cartridge B. Figure 13 Part (a) and Figure 13 In part (b), the addendum circle of the gear for the gear teeth is shown. Figure 14 1 and 2 are diagrams schematically showing the drive transmission structure from the drive transmission gear 81 of the apparatus main assembly A to the drive side flange 63 of the cartridge B.

[0179] <Drive Structure on Device Main Assembly Side>

[0180] like Figure 11As shown, the main component A of the device includes a motor (not shown), an idler wheel 80, a drive transmission gear 81, a second drive side plate 83, a main frame 84, a drive shaft 82 and a compression spring 85. The driving force of the motor is transmitted from the idler wheel 80 to the drive transmission gear 81. The idler wheel 80 and the drive transmission gear 81 are supported by the drive shaft 82 so as to be able to rotate coaxially and to move in the direction of the rotation axis. One end 82a of the drive shaft 82 is fixed to the hole 83a of the second drive side plate 83, and the other end 82b of the drive shaft is supported by the hole 84a of the main frame 84. The drive shaft 82 is arranged so that when the box B is installed in the main component A of the device, the rotation axis of the drive transmission gear 81 is parallel to the rotation axis L1 of the drum 62.

[0181] In addition, a compression spring 85 is provided between the other end portion 80b of the idler wheel 80 and the second drive side plate 83 so that the idler wheel 80 is urged in the H direction in the direction of the rotation axis. As described above, the J direction and the H direction in the apparatus main assembly A are defined to coincide with the J direction and the H direction of the cartridge B already mounted on the apparatus main assembly A. As a result, as Figure 11 As shown, the J direction is a direction from the idler gear 80 toward the second driving side plate 83 along the rotation axis of the idler gear 80 , and the H direction is a direction opposite to the J direction.

[0182] One end 80a of the idler gear 80 is provided with a recessed portion 80a1 recessed in the direction of the rotation axis. On the other hand, one end 81a of the drive transmission gear 81 is provided with a protrusion 81a1 protruding in the direction of the rotation axis at a position facing the recessed portion 80a1 of the idler gear 80. Through the engagement of the recessed portion 80a1 of the idler gear 80 with the protrusion 81a of the drive transmission gear 81, the driving force is transmitted from the idler gear 80 to the drive transmission gear 81, and the drive transmission gear 81 rotates integrally. The protrusion-recess relationship between the recessed portion 80a1 and the protrusion 81a1 can be reversed.

[0183] As will be described later, the drive transmission gear 81 is meshedly engaged with the driving side flange 63 of the cartridge B to transmit the driving force. Figure 1 As shown, during the execution of the above-mentioned image forming process operation, the initial operation after the cartridge B is mounted, and the preparatory operation for the image forming process (collectively referred to as "driving"), the drive transmission gear 81 rotates in the I direction to rotate the drive-side flange 63 in the K direction. That is, the driving direction (rotation direction) of the drive transmission gear 81 during driving is the I direction, and the driving direction (rotation direction) of the drive-side flange 63 during driving is the K direction. When the drive transmission gear 81 and the drive-side flange 63 are viewed from the driving side to the non-driving side along the H direction, the I direction is the clockwise direction, and the K direction is the counterclockwise direction.

[0184] <Drive Transmission Gear 81>

[0185] like Figure 1 、 Figure 12 and Figure 13 As shown in part (a), the drive transmission gear 81 includes a first main component gear portion (first main component side gear portion, first main component side helical gear portion) 81c and a second main component gear portion (second main component side gear portion, second main component side helical gear portion) 81d, and the first main component gear portion and the second main component gear portion are coaxially arranged with each other as helical tooth gear portions. The first main component gear portion 81c is located on the downstream side in the H direction (upstream side in the J direction) relative to the second main component gear portion 81d. The first main component gear portion 81c includes a plurality of first main component helical teeth 81ct, and the second main component gear portion 81d includes a plurality of second main component helical teeth 81dt. The first main component helical teeth 81ct and the second main component helical teeth 81dt both have an involute tooth profile. The first main component gear portion 81c and the second main component gear portion 81d are integrally resin molded and can rotate integrally. Furthermore, the twisting directions of the first main assembly gear portion 81c and the second main assembly gear portion 81d are the same, and the tooth surfaces are twisted so as to be displaced in the I direction with advancement in the J direction. Figure 13 As shown in part (a) of the second main assembly gear portion 81d, the helix angle α2 is greater than the helix angle α1 of the first main assembly gear portion 81c (i.e., α1 < α2 is satisfied). In addition, the first main assembly gear portion 81c and the second main assembly gear portion 81d have the same number of teeth.

[0186] <Driving Side Flange 63>

[0187] On the other hand, Figure 1 、 Figure 6 Part (b) and Figure 13As shown in part (b) of the drawing, the drive-side flange 63 is coaxially provided with a first gear portion (first unit-side gear portion, first unit-side helical gear portion) 63c and a second gear portion (second unit-side gear portion, second unit-side helical gear portion, second helical gear portion) 63d, which serve as helical gear portions. The first gear portion 63c is arranged on the downstream side of the second gear portion 63d in the H direction (upstream side in the J direction). That is, the first gear portion 63c is arranged between the second gear portion 63d and the drum 62 in the direction of the rotation axis L1. The first gear portion 63c includes a plurality of first helical teeth (first protrusions) 63ct arranged at different positions in the circumferential direction around the rotation axis L1, and the second gear portion 63d includes a plurality of second helical teeth (second protrusions) 63dt arranged at different positions in the circumferential direction around the rotation axis L1. The first helical teeth 63ct and the second helical teeth 63dt are both involute teeth and are protrusions that protrude in the radial direction centered on the rotation axis L1. The first gear portion 63c and the second gear portion 63d are integrally molded from resin and rotate integrally, and therefore, the first gear portion 63c and the second gear portion 63d can be said to be a first rotating portion and a second rotating portion that can rotate integrally with each other. The first gear portion 63c meshes with the first main assembly gear portion 81c of the drive transmission gear 81, and the second gear portion 63d meshes with the second main assembly gear portion 81d of the drive transmission gear 81.

[0188] like Figure 1 As shown, the torsion direction of the first gear portion 63c and the second gear portion 63d of the driving side flange 63 is the same, and the tooth surface is twisted so as to shift in the K direction as the gear advances in the J direction. The torsion direction of the first gear portion 63c and the second gear portion 63d is opposite to the torsion direction of the first main assembly gear portion 81c and the second main assembly gear portion 81d of the drive transmission gear 81. In addition, as shown in FIG. Figure 13As shown in part (b) of , the helix angle α2 of the second gear portion 63d is greater than the helix angle α1 of the first gear portion 63c (i.e., α1<α2 is satisfied). The helix angle α1 of the first gear portion 63c is the same as the helix angle α1 of the first main component gear portion 81c, and the helix angle α2 of the second gear portion 63d is the same as the helix angle α2 of the second main component gear portion 81d. In addition, the number of teeth of the first gear portion 63c and the second gear portion 63d of the drive side flange 63 is the same. In addition, the width (tooth width) W63c (Wc, Wc1) of the first helical tooth (first protrusion) 63ct measured in the direction of the rotation axis L1 is greater than the width (tooth width) W63d (Wd) of the second helical tooth (second protrusion) 63dt measured in the direction of the rotation axis L1. That is, the first gear portion 63c and the second gear portion 63d are each provided with at least one tooth, so that the tooth width Wc of the first helical tooth (tooth, first protrusion) 63ct measured in the direction of the rotation axis L1 and the tooth width Wd of the second helical tooth (tooth, second protrusion) 63dt measured in the direction of the rotation axis L1 satisfy the following formula A1.

[0189] Wc>Wd (Formula A1).

[0190] In other words, when the width (tooth width) of the first helical tooth 63ct having a maximum width (tooth width) measured in the direction of the rotation axis L1 of the first gear portion 63c is Wc1, the second gear portion 63d has a second helical tooth (second protrusion) 63dt, which has a width (tooth width) smaller than Wc1 measured in the direction of the rotation axis L1.

[0191] As will be described in detail below, when the driving side flange 1763 is driven by the drive transmission gear 1781 in a balanced state, the driving force FD received by the first gear portion 1763c is higher than the limiting force FB received by the second gear portion 1763d, and therefore, this relationship is preferred.

[0192] In addition, the greater the width (meshing width) of the portion where the first gear portion 63c meshes with (contacts with) the first main assembly gear portion 81c in the direction of the rotation axis L1, and the greater the meshing width of the second helical gear portion 63c with the second main assembly gear portion 81d, the better the drive transmission accuracy. However, if the meshing width is set larger than necessary, the widths of the first gear portion 63c and the second gear portion 63d in the direction of the rotation axis L1 become larger, and the dimensions of the drive-side flange 63, the drum unit 69, the cartridge B, and ultimately the main assembly A of the apparatus increase. Therefore, the tooth width Wc1 of the first helical tooth (tooth) 63ct having the largest tooth width in the first gear portion 63c, and the tooth width Wd1 of the second helical tooth (tooth) 63dt having the largest tooth width in the second gear portion 63d preferably satisfy the following formula A2, and more preferably satisfy the following formula A3.

[0193] Wd1≤(4 / 5)×Wc1 (A2)

[0194] Wd1≤(3 / 4)×Wc1 (A3)

[0195] Furthermore, from the viewpoint of the strength of the second helical teeth (teeth) 63dt of the second gear portion 63d, it is preferred that the second helical teeth (teeth) 63dt have a tooth width above a certain level, and preferably the tooth width Wc1 and the tooth width Wd1 satisfy the following formula A4.

[0196] Wd1≥(1 / 10)×Wc1 (Formula A4).

[0197] In addition, if Figure 14 As shown, in the meshing between the drive-side flange 63 and the drive transmission gear 81, the meshing pitch circle diameters D63c and D63d of the first gear portion 63c and the second gear portion 63d are set to be substantially the same. In addition, the tooth tip circle diameters Dt63c and Dt63d of the first gear portion 63c and the second gear portion 63d are also set to be substantially the same. Similarly, the meshing pitch circle diameters D81c and D81d of the first main component gear portion 81c and the second main component gear portion 81d are set to be substantially the same. As a result, the meshing between the first gear portion 63c and the first main component gear portion 81c and the meshing between the second gear portion 63d and the second main component gear portion 81d can be properly engaged without the tooth tips touching each other.

[0198] In order to set the meshing pitch circle diameters D63c and D63d of the first gear portion 63c and the second gear portion 63d to be substantially the same, it is preferable that the shapes of the first gear portion 63c and the second gear portion 63d are as follows.

[0199] Specifically, the tooth tip diameter Dt63c of the first gear portion 63c is preferably greater than the tooth root diameter Db63d of the second gear portion 63d, or is greater than 0.8 times (more preferably 0.9 times) the tooth tip diameter Dt63d of the second gear portion 63d. Furthermore, the tooth tip diameter Dt63c of the first gear portion 63c is preferably less than 1.1 times the tooth tip diameter Dt63d of the second gear portion 63d.

[0200] Furthermore, preferably, the root circle diameter Db63c of the first gear portion 63c is smaller than the root circle diameter Dt63d of the second gear portion 63d. Furthermore, the root circle diameter Db63c of the first gear portion 63c is preferably greater than 0.9 times the root circle diameter Db63d of the second gear portion 63d.

[0201] Furthermore, the tip circle diameter Dt63d of the second gear portion 63d is preferably larger than the root circle diameter Db63c of the first gear portion 63c, or is larger than 0.8 times (more preferably 0.9 times) the tip circle diameter Dt63c of the first gear portion 63c. Furthermore, the tip circle diameter Dt63d of the second gear portion 63d is preferably smaller than 1.1 times the tip circle diameter Dt63c of the first gear portion 63c.

[0202] Furthermore, the root circle diameter Db63d of the second gear portion 63d is preferably smaller than the tip circle diameter Dt63c of the first gear portion 63c. Furthermore, the root circle diameter Db63d of the second gear portion 63d is preferably greater than 0.9 times the root circle diameter Db63c of the first gear portion 63c.

[0203] Here, the relationship between these dimensions is expressed using the diameters of the first gear portion 63c and the second gear portion 63d, but of course, the relationship remains the same even if the diameters are replaced by radii. Furthermore, in the embodiments described below, examples will be shown in which the teeth of the first gear portion 63c and the second gear portion 63d are replaced by a plurality of protrusions having various shapes. In this case, the tip circle is a circle drawn as the rotational trajectory when the free end (point) of the tooth tips of the plurality of protrusions, which is farthest from the rotation axis L1, rotates, and the diameter / radius of this circle is the tip circle diameter / radius.

[0204] In order to make the meshing pitch diameters D63c and D63d the same while making the helix angles of the first gear portion 63c and the second gear portion 63d different as described above, the module and / or the amount of tooth profile shift between the first gear portion 63c and the second gear portion 63d are made different. Similarly, for the drive transmission gear 81, the module and / or the amount of tooth profile shift between the first main assembly gear portion 81c and the second main assembly gear portion 81d are made different.

[0205] In addition, the drive-side flange 63 includes a cylindrical portion (intermediate portion, small diameter portion, shaft portion) 63e located between the first gear portion 63c and the second gear portion 63d in the direction of the rotation axis L1. The maximum diameter D63e of the cylindrical portion 63e, centered about the rotation axis L1, is smaller than the addendum diameter Dt63c of the first gear portion 63c and the addendum diameter Dt63d of the second gear portion 63d. Furthermore, in this embodiment, the maximum diameter D63e of the cylindrical portion 63e, centered about the rotation axis L1, is smaller than the root diameter Db63c of the first gear portion 63c and the root diameter Db63d of the second gear portion 63d. However, the maximum diameter D63e of the cylindrical portion 63e, centered about the rotation axis L1, is not limited to the above, as long as it does not contact the drive transmission gear 81 while the drive-side flange 63 is driven by the drive transmission gear 81. In addition, as will be described below in Examples 22 and 23, the structure can make the distance (radius) R63e from the rotation axis L1 to the outer diameter of the cylindrical portion 63e at least temporarily smaller than the tooth top circle radius Rt63ct of the first gear portion 63c or the tooth top circle radius Rt63d of the second gear portion 63d, so that the driving side flange 63 and the drive transmission gear 81 can engage with each other to transmit driving force.

[0206] Here, the relationship between these dimensions is expressed using the diameters of the first gear portion 63c, the second gear portion 63d, and the cylindrical portion 63e. However, these relationships remain the same even if the diameters are replaced by radii. The shape of the cylindrical portion 63e does not necessarily have to be cylindrical centered on the rotation axis L1. For example, various shapes can be used, such as a polygonal prism and a shape asymmetrical with respect to the rotation axis L1. In this case, when the drive-side flange 63 rotates, the diameter of the circle drawn as the rotation trajectory of the point farthest from the rotation axis L1 in the intermediate portion 63e is the aforementioned maximum diameter D63e, and the radius of this circle is the maximum value of radius R63e.

[0207] By providing the cylindrical portion 63e, the second gear portion 63d can be arranged at a position away from the drum 62 (further downstream in the J direction) so as not to contact the first gear portion 81c. Similarly, the first gear portion 63c can be placed at a position close to the drum 62 (further downstream in the H direction) so as not to contact the second main component gear portion 81d. That is, by providing the cylindrical portion 63e, a gap g is provided between the first gear portion 81c and the second gear portion 63d in the direction of the rotation axis L1. Thus, when the cartridge B is mounted to the main assembly A of the apparatus, the first gear portion 63c is prevented from contacting the second main assembly gear portion 81d, and the second gear portion 63d is prevented from contacting the first main assembly gear portion 81c in the direction of the rotation axis L1. In addition, when the drive transmission gear 81 is driven and the drive transmission gear 81 moves to the equilibrium position, the first main assembly gear portion 81c is prevented from contacting the second gear portion 63d, and the second main assembly gear portion 81d is prevented from contacting the first gear portion 63c. The width of the cylindrical portion 63 e measured in the direction of the rotation axis L1 will be described in detail below.

[0208] <Drive Transmission to the Developing Roller>

[0209] Figure 15 Schematic diagram of the structure for transmitting drive from the drive-side flange 63 to the developing roller 32. The developing roller 32 is fixed to the developing roller shaft 31, and the developing roller gear 30 is provided at one end portion of the driving side of the developing roller shaft 31 so as to be movable in the direction of the rotation axis of the developing roller shaft 31. The developing roller gear 30 is rotatable integrally with the developing roller shaft 31 and the developing roller 32. In other words, the developing roller gear 30 is configured to be able to transmit driving force to the developing roller shaft 31 and the developing roller 32. The developing roller gear 30 is meshedly engaged with the first gear portion 63c of the drive-side flange 63 to transmit the driving force thereto.

[0210] Alternatively, the developing roller gear 30 may be engaged with the second gear portion 63d to transmit the driving force. However, by adopting a structure in which the developing roller gear 30 is engaged with the first gear portion 63c, the length of the developing roller shaft 31 in the direction of the rotation axis can be reduced compared to a structure in which the developing roller gear 30 is engaged with the second gear portion 63d.

[0211] <Drive transfer operation>

[0212] Next, refer to Figure 16 、 Figure 17 、 Figure 19 、 Figure 20 and Figure 21 The meshing operation between the drive transmission gear 81 and the drive side flange 63 will be described in sequence starting from the installation of the box B.

[0213] Figure 16Part (a) is a schematic diagram of the drive transmission gear 81 and the driving side flange 63 as viewed in the rotation axis direction. Figure 16 Part (b) is a cross-sectional view of the drive transmission gear 81 taken along line AF-AF. Figure 16 In the drawings after part (b), the shaded (hatched) portion in the drawing is a cross-section of the tooth portion of the gear, and the portion between adjacent shaded portions corresponds to a portion of the gear including the inter-tooth space portion of the gear. Figure 16 Part (c) is a cross-sectional view of the driving side flange 63 taken along line AF-AF. Figure 16 Part (d) is a sectional view of the drive transmission gear 81 taken along line AF-AF before the cartridge is mounted. Figure 16 Part (e) is a sectional view of the drive transmission gear 81 and the driving side flange 63 taken along line AF-AF after the cartridge B is mounted and before the driving operation starts.

[0214] Figure 17 is a sectional view taken along the line AF-AF in contact with the meshing pitch circle between the drive transmission gear 81 and the driving side flange 63 immediately after the start of driving, wherein Figure 17 Part (a), Figure 17 Part (b) Figure 17 Part (c) and Figure 17 Part (d) shows the state as time passes.

[0215] Figure 19 Part (a), Figure 19 Part (b) and Figure 19 Part (c) is a diagram of the drive transmission gear 81 and the driving side flange 63 as viewed in the H direction.

[0216] Figure 21 Part (a) is a view of the drive transmission gear 81 and the driving side flange 63 as viewed in a direction perpendicular to the rotation axis direction. Figure 21 Part (b) is a sectional view of the first main assembly gear portion 81c taken along line AD-AD during the driving operation. Figure 21 Part (c) is a sectional view of the second main assembly gear portion 81d taken along line AD-AD during the driving operation.

[0217] <Jointing when installing box B>

[0218] like Figure 16As shown in part (d) of the drive transmission gear 81 before the cartridge B is mounted, the other end portion 81e of the drive transmission gear 81 is pressed against the surface 84b of the main frame by the urging force F1 of the compression spring 85, so that the drive transmission gear 81 is thereby held. By causing the drive transmission gear 81d to abut against the abutment surface 84b in this manner and maintaining the abutment, the initial position of the drive transmission gear 81 in the direction of the rotation axis is fixed, so that the meshing with the drive-side flange 63 can be stabilized.

[0219] When the cartridge B is mounted to the apparatus main assembly A in the mounting direction M (M direction), the drive side flange 63 is brought into meshing engagement with the drive transmission gear 81, as shown in FIG. Figure 19 Here, the force required to rotate the drive side flange 63 is greater than the force required to rotate the drive transmission gear 81. Therefore, the drive transmission gear 81 rotates in the I direction (clockwise direction) by the movement of the drive side flange 63 in the M direction. At this time, as shown in FIG. Figure 16 As shown in part (e) of the drive transmission gear 81, the first main assembly gear portion 81c or the second main assembly gear portion 81d of the drive transmission gear 81 comes into contact with the first gear portion 63c or the second gear portion 63d of the driving side flange 63 and is pressed in the M direction. A thrust F3 in the H direction is applied to the drive transmission gear 81. However, since the other end portion 81e of the drive transmission gear 81 abuts against the abutment surface 84b of the main frame 84 and receives a reaction force F4, the drive transmission gear 81 cannot move in the H direction.

[0220] <Operations after driving starts>

[0221] Next, a case where the driving side flange 63 is driven to perform an initial operation, a preparatory operation for image formation, and the like will be described. Figure 19 As shown in part (b) of the drive transmission gear 81, the drive transmission gear 81 is rotated by the motor (not shown) of the main assembly A of the apparatus and rotates in the direction I. As a result, the driving side flange rotates in the direction K. It is presumed that immediately after the drive transmission gear 81 starts to rotate in the direction I, the second main assembly gear portion 81d of the drive transmission gear 81 first meshes with the second gear portion 63d of the driving side flange 63 to transmit the driving force thereto, as shown in FIG. Figure 17 As shown in part (a) of . Then, the second main component gear portion 81d applies a thrust in the H direction to the second gear portion 63d. However, the driving side flange 63 is prevented from moving in the H direction by the rib 71p, and receives a reaction force in the J direction corresponding to the thrust in the H direction. Therefore, due to the action of the reaction force received from the second gear portion 63d, the second main component gear portion 81d receives a thrust F5 in the J direction. The drive transmission gear 81 moves in the J direction by this thrust F5.

[0222] When the drive transmission gear 81 moves in the J direction with further rotation, as shown in FIG. Figure 17 As shown in part (b) of the figure, the first gear portion 63c is also brought into meshing engagement with the first main assembly gear portion 81c, causing the first main assembly gear portion 81c to receive thrust F6. The direction of thrust F6 is the J direction, which is the same as the direction of thrust F7 received by the meshing engagement of the second main assembly gear portion 81d with the second gear portion 63d. As a result, the drive transmission gear 81 further moves in the J direction.

[0223] When the drive transmission gear 81 is further rotated and moved in the J direction, the second main assembly gear portion 81d becomes disengaged from the second gear portion 63d, as shown in FIG. Figure 17 . On the other hand, the meshing engagement between the first gear portion 81c and the first gear portion 63c is maintained, and the thrust F8 is applied to the first gear portion 81c in the J direction. At this time, the drive transmission gear 81 rotates the driving side flange 63 only by the engagement between the first main component gear portion 81c and the first gear portion 63c. That is, the tooth surface 81c1 on the downstream side in the I direction of the first main component gear portion 81c and the tooth surface 63c1 on the upstream side in the I direction of the first gear portion 63c are in contact with each other.

[0224] This is effective because the helical angle α2 of the second main assembly gear portion 81d of the drive transmission gear 81 is larger than the helical angle α1 of the first main assembly gear portion 81c (α2>α1). Figure 21 Part (b) and Figure 21 The details are described in detail in part (c). Assume that the drive transmission gear 81 moves by the amount LL in the J direction due to the thrust through the engagement with the drive side flange 63. Figure 21 In parts (b) and (c), the first main component gear portion 81c and the second main component gear portion 81d are shown by the solid line before the movement and the dotted line after the movement, respectively. The amount of movement of the first main component gear portion 81c and the second main component gear portion 81d in the rotation direction through this movement can be represented by LL / tanα1 and LL / tanα2, respectively. Based on the relationship between the helix angles α1 and α2, the amount of movement LL / tanα2 of the second main component gear portion 81d in the rotation direction is greater than the amount of movement LL / tanα1 of the first main component gear portion 81c in the rotation direction (LL / tanα1<LL / tanα2). It can be understood that the amount of movement in the rotation direction corresponding to the amount of movement LL in the J direction is greater in the second main component gear portion 81d than in the first main component gear portion 81c. Therefore, even if the first main component gear portion 81c and the first gear portion 63c are engaged with each other, the second main component gear portion 81d is separated from the second gear portion 63d.

[0225] When the drive transmission gear 81 further continues to rotate and moves to the driving side J, the tooth surface 81d2 on the upstream side in the I direction of the second main assembly gear portion 81d eventually contacts the tooth surface (contact portion) 63d2 on the downstream side in the I direction of the second gear portion 63d, as shown in FIG. Figure 17 As shown in part (d) of . The surface 81c1 of the first main component gear portion 81c and the surface 63c1 of the first gear portion 63c maintain contact with each other. That is, in this state, the first main component gear portion 81c of the drive transmission gear 81 presses the tooth surface (contact portion) 63c1 through the tooth surface 81c1 to rotate the drive side flange 63, and the tooth surface 81d2 of the second main component gear portion 81d of the drive transmission gear 81 contacts the tooth surface 63d2, so that the drive transmission gear 81 is sandwiched by the drive side flange 63. Then, the movement of the drive transmission gear 81 in the direction of the rotation axis L1 stops. The position in the direction of the rotation axis L1 at this time is the equilibrium position. The state in which the drive transmission gear 81 rotates at the equilibrium position and is driven to achieve drive transmission to the drive side flange 63 will be described.

[0226] In a balanced state, force F9, force F10, and force F1 are applied to the drive transmission gear 81 in the direction of the rotation axis L1. Force F9 is the thrust in the J direction received by the first main assembly gear portion 81c through meshing engagement with the first gear portion 63c, and force F1 is the thrust in the H direction received by the second main assembly gear portion 81d through meshing engagement with the second gear portion 63d, and force F1 is the urging force of the compression spring 85. Furthermore, the driving-side flange 63 receives the force from the drive transmission gear 81 and is positioned in the direction of the rotation axis L1 by the side wall 71m or the rib 71p, and generates a reaction force F11 that is balanced with the force received from the drive transmission gear 81. Figure 17 Part (d) shows the drive transmission gear 81 positioned in contact with the side wall 71m. When friction is ignored in the equilibrium state, the forces F9, F10, F1, and F11 are balanced, and the drive transmission gear 81 and the driving side flange 63 are positioned in the direction of the rotation axis L1.

[0227] Furthermore, the drive-side flange 63 is clamped (in contact with) the first main assembly gear portion 81c and the second main assembly gear portion 81d of the drive transmission gear 81, and receives the following force in the K direction (rotational direction). Specifically, the tooth surface (contact portion) 63c1 of the first gear portion 63c contacts the first main assembly gear portion 81c, which is located upstream in the K direction (first circumferential direction), and receives the driving force FD as a force component for rotating the drive-side flange 63 in the direction K (predetermined direction). Simultaneously, the tooth surface (contact portion) 63d2 of the second gear portion 63d contacts the second main assembly gear portion 81d, which is located downstream in the K direction (first circumferential direction), and receives the restricting force (braking force) FB as a force component in a direction that suppresses (restricts) the rotation of the drive-side flange 63 in the direction K. Therefore, it can be said that the first gear portion 63c is a driving force receiving portion that receives the driving force FD, and the second gear portion 63d is a restricting force receiving portion that receives the restricting force FB. The driving force FD is greater than the limiting force FB.

[0228] Here, since the second gear portion 63d is integrally provided with the first gear portion 63c in the rotational direction, this structure prevents the second gear portion 63d from rotating in the opposite direction K relative to the first gear portion 63c. Strictly speaking, since the driving-side flange 63 is made of resin and deformation of the teeth and components occurs, the second gear portion 63d, subjected to the restricting force FB, rotates slightly relative to the first gear portion 63c in the direction opposite to the K direction, then its rotation stops and its position is fixed. Therefore, the restricting force FB received by the second gear portion 63d acts on (is transmitted to) the first gear portion 63c. By the same principle, the driving force FD received by the first gear portion 63d acts on (is transmitted to) the second gear portion 63d.

[0229] In this manner, the first gear portion 63c receives the driving force FD, and the second gear portion 63d receives the limiting force FB. This results in a state in which there is no play (backlash) in the rotational direction (direction I) between the drive-side flange 63 and the drive transmission gear 81, i.e., a backlash-free state. Thus, the drive-side flange 63 is rotationally driven in the direction K while maintaining the backlash-free state. When drive is transmitted by engaging with each other in the backlash-free state, drive transmission with high rotational accuracy is achieved.

[0230] In addition, the width (tooth width) W63c of the first helical tooth (first protrusion) 63ct measured in the direction of the rotation axis L1 is greater than the width (tooth width) W63d of the second helical tooth (second protrusion) 63dt in the direction of the rotation axis L1. In other words, the second gear portion 63d has a second helical tooth (second protrusion) 63dt that is narrower than the first helical tooth 63ct of the first gear portion 63c having the maximum width (tooth width) in the direction of the rotation axis L1.

[0231] If the second main assembly gear portion 81d and the second gear portion 63d are not in contact with each other at the start of driving, and the first main assembly gear portion 81c and the first gear portion 63c are in contact with each other, the driving from Figure 17 The state shown in part (c) starts without going through Figure 17 Then, according to the same principle as above, the state is achieved. Figure 17 The equilibrium state shown in part (d) is obtained. Figure 17 Starting from the state shown in part (c), the drive transmission gear 81 moves in the J direction by the thrust F8 to Figure 17 Part (d) shows the equilibrium state.

[0232] <Disengagement When Removing Cartridge B>

[0233] Next, refer to Figure 18 、 Figure 19 and Figure 20 , the meshing and disengaging operation between the drive transmission gear 81 and the driving side flange 63 when the cartridge B is detached after the driving operation is finished will be described. Figure 18 is a sectional view taken along the line AF-AF in contact with the meshing pitch circle between the drive transmission gear 81 and the driving side flange 63 when the cartridge B is to be disassembled after the driving operation is finished, and the time is in Figure 18 Part (a) and Figure 18 The sequence of parts (B) passes. Figure 20 Schematic diagram of the drive transmission gear 81 and the driving-side flange 63 as viewed along the H direction.

[0234] like Figure 19 As shown in part (c) of FIG. 1 , the cartridge B is disassembled in the removal direction N (N direction) and removed from the main assembly A of the apparatus. The N direction is opposite to the M direction. As described above, the force required to rotate the drive side flange 63 is greater than the force required to rotate the drive transmission gear 81. Therefore, the drive transmission gear 81 rotates in the K direction (counterclockwise direction) by the movement of the drive side flange 63 in the N direction. At this time, as Figure 18 As shown in part (a), when the driving side flange 63 moves in the N direction, the first gear portion 63c presses the first main assembly gear portion 81c. In addition, Figure 20 The figure shows the positional relationship between the drive-side flange 63 and the drive transmission gear 81 when the drive-side flange 63 moves in the N direction, where the solid line shows the state before the movement in the N direction, and the dotted line shows the state after the movement. When the drive-side flange 63 moves in the N direction, the distance between the rotation center (rotation axis) L1 of the drive-side flange 63 and the rotation center (rotation axis) L2 of the drive transmission gear 81 changes from the distance LA to the distance LB (LA < LB).

[0235] Thus, the meshing position of the teeth of the first gear portion 63c and the first main assembly gear portion 81c gradually moves toward the tooth top. Figure 18 As shown in part (b) of the embodiment, the backlash of the meshing in the rotational direction increases, and the gap AL between the tooth surface 63d2 of the second gear portion 63d and the tooth surface 81d2 of the second main component gear portion 81d increases. When the gap AL is set between the tooth surfaces, the force from the second gear portion 63d does not act on the drive transmission gear 81, and the thrust F16 in the J direction generated by the engagement between the first main component gear portion 81c and the first gear portion 63c acts. As a result, when the box B is disassembled, the drive transmission gear 81 gradually moves in the J direction while rotating in the K direction, and eventually the meshing between the first gear portion 63c and the first main component gear portion 81c disappears. As a result, the engagement between the drive side flange 63 and the drive transmission gear 81 is released.

[0236] <Setting the helix angle>

[0237] Next, refer to Figure 46 , preferred helix angles of the first gear portion 63c and the second gear portion 63d will be described. Figure 46 Part (a) and Figure 46 Part (b) is a sectional view of the second gear portion 63 d and the second main assembly gear portion 81 d taken along the line AF-AF in contact with the meshing pitch circle between the drive transmission gear 81 and the driving side flange 63 .

[0238] The following will describe the setting of the helix angle α1 of the first gear portion 63c and the helix angle α2 of the second gear portion, in the case where the first gear portion 63c is the gear portion that receives the driving force FD and the second gear portion 63d is the gear portion that receives the limiting force FB, as described above. First, as a premise, since the first gear portion 63c is the gear portion that receives the driving force FD and the second gear portion 63d is the gear portion that receives the limiting force FB, the helix angle α2 is greater than the helix angle α1 (α2>α1). If the helix angle α2 is less than the helix angle α1, drive transmission cannot be performed in a backlash-free state. In other words, the thrust applied by the first gear portion 63c to the first main assembly gear portion 81c and the thrust applied by the second gear portion 63d to the second main assembly gear portion 81d are unbalanced, and therefore, the position of the drive transmission gear 81 in the direction of the rotation axis L1 is not determined to be in a balanced position.

[0239] The helix angle α1 of the first gear portion 63c of the drive-side flange 63 is preferably equal to or greater than 10° (α1 ≥ 10°), more preferably equal to or greater than 15° (α1 ≥ 15°), and even more preferably equal to or greater than 20° (α1 ≥ 20°). This is because, generally, if the tooth width (the width of the gear teeth in the direction of the rotation axis L1) is the same, a larger helix angle results in a larger meshing ratio and higher rotational accuracy. The helix angle α1 is preferably equal to or less than 40° (α1 ≤ 40°), and more preferably equal to or less than 35° (α1 ≤ 35°). This is because, generally, larger helix angles deteriorate moldability in a mold.

[0240] On the other hand, the helix angle α2 of the second gear portion 63d of the drum gear 63 is preferably equal to or less than 40° (α2≤40°), and more preferably equal to or less than 35° (α2≤35°). The reason is that, generally, when the helix angle is large, the moldability by the mold deteriorates. In addition, the helix angle α2 of the second gear portion 63d of the drum gear is preferably equal to or greater than 20° (α2≥20°), and more preferably equal to or greater than 25° (α2≥25°). The reason is that, as Figure 46 Part (a) and Figure 46 As shown in part (b) of FIG. 8 , the larger the helix angle α2 is, the larger the width E of the contact surface with the second main assembly gear portion 81d in the rotational direction (K direction) is. In this embodiment, the helix angle α2 is 35°.

[0241] If the width E is small, when the second gear portion 63d receives the thrust F9 (see Figure 17When the force F9 is received by the first gear portion 63c in the portion (d) of the second gear portion 63d, the tooth surface of the second gear portion 63d is deformed, and the second main assembly gear portion 81d enters and moves like a wedge, and the positioning in the direction of the rotation axis L1 becomes unstable. Therefore, it is necessary to ensure a certain width E in order to reliably receive the thrust F9, thereby positioning the drive transmission gear 81 in the direction of the rotation axis L1.

[0242] From the overall perspective of the above analysis, the helix angle α1 is preferably greater than or equal to 10° and less than or equal to 40° (15°≤α1≤40°), more preferably greater than or equal to 15° and less than or equal to 40° (15°≤α1≤40°), and further preferably greater than or equal to 20° and less than or equal to 35° (20°≤α1≤35°). The helix angle α2 is preferably greater than or equal to 20° and less than or equal to 40° (20°≤α2≤40°), and further preferably greater than or equal to 25° and less than or equal to 35° (25°≤α2≤35°). In this embodiment, the helix angle α1 is 20° and the helix angle α2 is 35°, satisfying the above conditions.

[0243] <Width of Cylindrical Portion 63e>

[0244] Next, the width (length) of the cylindrical portion 63 e in the direction of the rotation axis L1 will be described. Figure 47 Part (a) of FIG. 8 is a schematic diagram of the driving side flange 63 and the drive transmission gear 81 when the cartridge B is mounted as viewed from a direction perpendicular to the rotation axis L1. Figure 47 Part (b) of FIG. 8 is a schematic diagram of the driving-side flange 63 and the drive transmission gear 81 during the driving operation as viewed from a direction perpendicular to the rotation axis L1 .

[0245] As described above, by providing the cylindrical portion 63e, the first gear portion 63c is prevented from contacting the second main component gear portion 81d, and the second gear portion 63d is prevented from contacting the first main component gear portion 81c, relative to the direction of the rotation axis L1. In addition, by providing the cylindrical portion 63e, when the drive transmission gear 81 is driven and the drive transmission gear 81 moves to the equilibrium position, the first main component gear portion 81c is prevented from contacting the second gear portion 63d, and the second main component gear portion 81d is prevented from contacting the first gear portion 63c. That is, by providing the cylindrical portion 63e, a gap g is formed between the first gear portion 81c and the second gear portion 63d in the direction of the rotation axis L1. Therefore, in the following description, the width (length) of the cylindrical portion 63e measured in the direction of the rotation axis L1 is synonymous with the width (length) of the gap g measured in the direction of the rotation axis L1.

[0246] The above contact may occur in the following two situations. First, if Figure 47 As shown in part (a) of FIG. 1 , when the cartridge B is mounted on the apparatus main assembly A, the other end portion 81e of the drive transmission gear 81 is held in contact with the abutment surface 84b of the main frame 84. The second condition is a condition in which the drive transmission gear 81 is driven and moves toward the equilibrium position, as shown in FIG. Figure 47 as shown in part (b).

[0247] The positions of the first gear portion 63c and the second gear portion 63d of the drive side flange 63, the positions of the first main component gear portion 81c and the second main component gear portion 81d of the drive transfer gear 81, and the equilibrium position may be different depending on the following factors. Specifically, (1) the tolerances of relevant parts such as the drive side flange 63, the drive transfer gear 81 and the cleaning frame (drum frame) 60a in the direction of the rotation axis L1, (2) the tolerances related to the distance between the rotation axis L1 of the drive side flange 63 and the rotation axis L2 of the drive transfer gear 81, (3) the tolerances of the phases of the teeth of the first gear portion 63c and the second gear portion 63d of the drive side flange 63 in the rotation direction, (4) the tolerances of the phases between the teeth of the first main component gear portion 81c and the second main component gear portion 81d of the drive transfer gear 81 in the rotation direction, and (5) the deformation of the teeth due to the maximum drive load, and the thermal expansion and contraction of the drive side flange 63 and the drive transfer gear 81. The width (length We) of the cylindrical portion 63 e (or the gap g) in the direction of the rotation axis L1 is selected in consideration of these factors.

[0248] Specifically, the width We is selected so as to satisfy the following formula B1, where the width (tooth width, length) of the teeth of the first gear portion 63c measured in the direction of the rotation axis L1 is Wc as a reference,

[0249] We≥Wc / 5(Formula B1)

[0250] In addition, as the width We increases, the width of the cartridge B in the direction of the rotation axis L1 increases, and therefore, the width We is selected to be no larger than a required size in order to reduce the size of the cartridge B and the apparatus main assembly A. From this viewpoint, it is further preferred to satisfy the following formula B2.

[0251] We≤Wc (Formula B2)

[0252] In this embodiment, Wc=8.6 mm and We=2.3 mm, satisfying the above formulas B1 and B2. In the case where the tooth width Wc of the first gear portion 63c is not constant, the tooth width Wc1 of the tooth having the largest tooth width is considered to be the tooth width Wc.

[0253] In addition, from Figure 13 、 Figure 14 and Figure 47It will be understood from part (b) that the width We preferably satisfies the following formula B3, where Wd is the width (tooth width, length) of the teeth of the second gear portion 63c in the direction of the rotation axis L1.

[0254] We≤Wd(Formula B3)

[0255] <Rotation Accuracy>

[0256] Below, refer to Figure 22 and Figure 49 , the reason why the rotation accuracy is improved in the backlash-free state will be described. Figure 22 Part (a) is a view of the drive transmission gear 81 and the driving side flange 63 as viewed in a direction perpendicular to the rotation axis direction. Figure 22 Part (b) is a partial cross-sectional view of the meshing engagement portion of the ordinary helical tooth gears 51 and 53 as a comparative example. Figure 22 Part (c) is a partial cross-sectional view taken along the line AD-AD in contact with the meshing pitch circle of the drive transmission gear 81 and the driving side flange 63 . Figure 22 Part (d) is a partial perspective view of the helical gear 51. Figure 22 Part (e) is a partial perspective view of the drive transmission gear 81. Figure 49 Graphs comparing drive transmission errors when the alignment of the drive-side flange 63 and the helical-tooth gear 53 is misaligned.

[0257] like Figure 22 As shown in part (b), in the gear drive, due to the molding accuracy, clearance and deformation of the shaft portion, the tooth surfaces of the helical gears on the driving side and the driven side may mesh with each other in a state where they are not parallel in the tooth line direction. This state is generally referred to as a misaligned state. When the alignment of the helical gear (driving side) 51 and the helical gear (driven side) 53, which are ordinary helical gears, deviates by β°, the helical gears 51 and 53 mesh only at one end of the tooth surface in the axial direction. As a result, the meshing rate is significantly reduced compared to the state where the alignment is not deviated. As a result, the rotational accuracy during drive transmission is extremely deteriorated. Figure 22 Part (d) shows a region where the tooth surface of the helical-tooth gear 51 meshes with the helical-tooth gear 53 when the alignment is deviated, and the width of this region is defined as a width LP.

[0258] On the other hand, Figure 22As shown in part (c) of the driving side flange 63, the driving side flange 63 rotates, and at the same time, the first gear portion 63c and the second gear portion 63d of the driving side flange 63 clamp the first main component gear portion 81c and the second main component gear portion 81d of the drive transmission gear 81 in the middle. As a result, a clamping force FC (i.e., a rotational drive brake) is generated acting on the second main component gear portion 81d. The reaction force of the clamping force FC is added to the force applied to the tooth surface of the first main component gear portion 81c pressing the first gear portion 63c in the I direction, thereby generating a force FB. On the other hand, when the same load torque is driven in the conventionally used helical gear 51, no such additional force is generated for the force FA applied to the tooth surface of the helical gear 51. Therefore, the force FB applied to the tooth surface of the first main component gear portion 81c of this embodiment is greater than the force FA applied to the tooth surface of the helical gear 51. Figure 22 Part (e) shows the area where the tooth surface of the first main assembly gear portion 81c of the drive transmission gear 81 meshes with the first gear portion 63 of the drive side flange 63 when the alignment is deviated, wherein the width of the area is LQ. Since the force FB is greater than the force FA, when comparing Figure 22 The width LP in part (d) is Figure 22 When the width LQ in the portion (e) is less than the width LQ, the width LQ is greater than the width LP. Therefore, when the alignment is deviated, the reduction in the overlapping meshing ratio between the first main assembly gear portion 81c and the first gear portion 63c is less than the reduction in the overlapping meshing ratio between the helical gears 51 and 53.

[0259] Figure 49 This graph shows the measurement results of the drive transmission error to the driven-side helical gear 53 and the driving-side flange 63 relative to the amount of misalignment when using conventional helical gears 51 and 53 and the drive transmission gear 81 and driving-side flange 63 of this embodiment. The gear specifications for the helical gears 51 and 53 and the drive transmission gear 81 and driving-side flange 63 are identical, such as the number of teeth and the amount of backlash in the interaxial direction of 0.15 mm, as well as conditions such as a load torque of 0.25 Nm and a rotational speed of 270 rpm, are the same, and the shafts and gears are fitted without play. The drive transmission error (%) is the ratio of experimental rotational pitch deviation data to the ideal rotational pitch during gear meshing. For example, if the ideal rotational pitch is 0.7258 mm and the experimental deviation data from the ideal rotational pitch is 0.00036 mm, the result is 0.05% (= (0.00036 / 0.7258) × 100). In addition, when the axes of the meshing gears are parallel to each other, the misalignment amount (°) is 0°, and when the axes of the gears are tilted on the driven side so that the tooth trace direction of the gears is tilted by an angle β, the misalignment amount is the angle between the axes (see Figure 22(b) and (c)). As shown in this graph, when the alignment is misaligned, the reduction in the rotational accuracy of the drive-side flange 63 of this embodiment is suppressed compared to the conventional helical gear 53. Therefore, it can be said that the drive transmission structure using the drive transmission gear 81 and the drive-side flange 63 of this embodiment is more resistant to misalignment than the drive transmission structure using conventional helical gears.

[0260] <Wear of Drive Transmission Gears>

[0261] Next, refer to Figure 24 , the wear of the drive transmission gear 81 and the helical gear 101 will be described below. Figure 24 Part (a) is a schematic diagram of a drive transmission structure using a conventional helical gear. Figure 24 Part (b) is a schematic diagram of the drive transmission structure of this embodiment. Figure 24 As shown in part (a) of FIG, when the helical gear 101 is driven to rotate, the helical gear 101 receives a thrust force (force in the axial direction) FD provided by the meshing engagement force. As a result, the helical gear 101 moves toward the non-driving side along the H direction, and the end surface 101a of the helical gear abuts against the abutment surface 184b of the main frame 84 and slides thereon, so that they are worn. On the other hand, as shown in FIG. Figure 24 As shown in part (b), in the drive transmission gear 81 of the present embodiment, the position of the drive transmission gear in the direction of the rotation axis L1 during driving is determined by the drive side flange 63 and the spring 85 (not shown), and therefore, since a gap AA is formed between the main frame 84 and the second drive side plate 83, the end surface 81e in the H direction and the end surface 81f in the J direction of the drive transmission gear 81 do not slide, and therefore, the wear of the two end surfaces 81e, 81f of the drive transmission gear 81, the main frame 84 and the second drive side plate 83 can be suppressed, and the durability can be improved.

[0262] <Comparison with conventional joint drivers>

[0263] Next, refer to Figure 26 and 27 , a comparison with a structure in which the drum is driven by a conventional coupling will be described. Figure 26 Part (a) is a cross-sectional view of a drive transmitting portion of a conventional coupling driver, and the cross section includes the rotation axis of the coupling. Figure 26 Part (b) is a sectional view of the drive transmission unit of the present embodiment, which includes the rotation axis ( L1 ) of the driving side flange 63 and the rotation axis of the drive transmission gear 81 . Figure 27 is a graph showing the deformation amount of the coupling driver and the drive transmission gear.

[0264] like Figure 26As shown in part (a) of the drawing, in a conventional coupling driver, a driving side flange 263 provided with a protruding coupling piece 263a having a twisted polygonal prism shape is mounted to the end of the drum 62 of the cartridge. The drum flange 263 has a supporting portion 263b which is a cylindrical portion having a diameter smaller than that of the drum 62. The apparatus main assembly has a drive transmission gear 281 having a recessed coupling piece 281a into which the coupling piece 263a is inserted and engaged.

[0265] The coupling 263a is provided at the end portion of the driving side flange 263 in the direction of the rotation axis. Therefore, the amount of twisting of the driving side flange 263 during driving in the coupling driver is greater than Figure 26 The amount of twisting of the driving side flange 63 in the gear driver of this embodiment is shown in part (b). Figure 27 The simulation results for the rotational deformation of the drive member (drum flange 263, drive-side flange 63) are shown. As will be appreciated, the deformation of the gear drive (driven by the drive-side flange 63) is smaller than that of the coupling drive (driven at the drum flange 263). Here, the rotational deformation of the drive member will be described. This deformation is the displacement in the rotational direction relative to the drive transmission point of the drum 62 when the drum 62 side of the drum coupling 263 and the drive-side flange 63 are fixed and the same static load torque of 0.25 N·m is applied to the engagement portion with the drive input member 281 or the meshing engagement portion with the drive transmission gear 81. The drive transmission point is a point fixed on the drum 62. The displacement is converted to the displacement when there is no torsion at a predetermined point on the surface of the drum 62. Due to this difference in the deformation of the drive member, the change in the deformation of the drive member and the fluctuation in the rotational speed of the drum 62 when the load torque of the cartridge B changes are smaller in the gear drive than in the coupling drive. That is, it is possible to suppress unevenness in the density of the image in the rotation direction of the drum 62 (caused by variation in the pitch between scanning lines in the sub-scanning direction (pitch variation) generated when the surface of the drum 62 is scanned with the laser beam L) when fluctuations in the load torque of the cartridge B occur. As described above, with the drive transmission structure of the drive-side flange 63 and the drive transmission gear 81 of the above-described embodiment, it is possible to suppress deterioration in the rotation accuracy of the drum 62 with respect to fluctuations in the load torque, as compared with the conventional coupling drive structure.

[0266] In addition, from another point of view, compared with the conventional connecting drive, in the case of the conventional connecting drive, a retraction mechanism needs to be provided for advancing and retracting the connecting member 263a on the main component side in the direction of the rotation axis to allow installation and removal of box B.

[0267] Next, refer to Figure 28 , the retraction mechanism will be described. Figure 28Part (a) is a sectional view of the drum 62 of the retracting mechanism in a cross section including the rotation axis. Figure 28 Part (b) is a schematic cross-sectional view of the imaging apparatus provided with the retracting mechanism. Figure 28 Parts (c) and (d) are cross-sectional views of the drive transmission gear 281 and the retracting mechanism, and the cross sections thereof include the rotation axis of the drive transmission gear 281 .

[0268] The main assembly of the coupling-driven imaging device is equipped with a retraction mechanism including a connecting rod 210, a cylindrical cam 212, and a compression spring 214. One end of the connecting rod 210 is connected to the opening / closing door 211 of the main assembly A of the device. The other end of the connecting rod 210 is coaxially connected to the cylindrical cam 212 rotatably provided between the driving input member 281 and the side wall 213. In addition, as shown in FIG. Figure 28 As shown in part (a), the cylindrical cam 212 has an inclined surface 212d, a protruding surface 212c, and a concave surface 212e with a height difference in the rotation direction on one end surface in the axial direction. In addition, the side wall 213 has an inclined surface 213e, a protruding surface 213f, and a concave surface 213g at positions facing the inclined surface 212d, the protruding surface 212c, and the concave surface 212e, respectively. In addition, as shown in FIG. Figure 28 As shown in part (d) of FIG. 2 , the drive transmission gear 281 is pushed in the H direction by the compression spring 214 .

[0269] like Figure 28 As shown in part (b) of the drawing, by the operation of opening the door 211, the cylindrical cam 212 rotates in the direction I by means of the connecting rod 210, and the protruding surface 212c of the cylindrical cam 212 and the protruding surface 213f provided on the side wall 213 come into contact with each other, so that the cylindrical cam 212 moves in the direction J. By operating the cylindrical cam 212 in the direction J, as shown in FIG. Figure 28 As shown in part (c) of FIG. 2 , the cylindrical cam 212 overcomes the urging force of the compression spring 214 and moves the drive input member 281 in the J direction. As a result, the drive input member 281 moves away from the drum flange 263 (see FIG. 2 ). Figure 26 ) to disengage the coupling 281a from the coupling 263a (see Figure 26 As a result, box B can be removed.

[0270] In addition, if Figure 28As shown in part (b) of FIG. 2 , as the door 211 is closed, the cylindrical cam 212 rotates in the direction opposite to the direction I by means of the connecting rod 210, and the inclined surface 212d of the cylindrical cam 212 and the inclined surface 213e provided on the side wall 213 come into contact with each other. During this rotation, the cylindrical cam 212, the side wall 213 and the drive input member 281 come out of contact with each other in the direction of the rotation axis, and as shown in FIG. Figure 28 As shown in part (d) of FIG, the drive input member 281 becomes rotatable in the H direction by the urging force of the compression spring 214. As a result, the drive input member 281 moves in a direction close to the drum flange 263 (see FIG. Figure 26 , and the coupling 281a and the coupling 263a become engageable with each other.

[0271] As described above, conventional coupling drive requires retraction mechanism, and there is the possibility that the size or cost of the main assembly of the device increases correspondingly with the number of retraction mechanisms. However, in the case of the gear drive as in the present embodiment, box B can be installed and removed under the situation that there is no such retraction mechanism.

[0272] <Modification Example 1>

[0273] Next, Modification Example 1 will be described. In the above embodiment, the first main assembly gear portion 81c and the second main assembly gear portion 81d of the drive transmission gear 81 have the same number of teeth, but this number of teeth need not necessarily be the same. However, the reduction ratio between the first main assembly gear portion 81c of the drive transmission gear 81 and the first gear portion 63c of the drive-side flange 63 and the reduction ratio between the second main assembly gear portion 81d of the drive transmission gear 81 and the second gear portion 63d of the drive-side flange 63 need to be the same. For example, if the first gear portion 81c of the drive transmission gear has 20 teeth and the first gear portion of the drum gear has 30 teeth, the reduction ratio is 2:3. If the second main assembly gear portion 81d of the drive transmission gear has 40 teeth and the second gear portion 63d of the drive-side flange 63 has 60 teeth, the reduction ratio is also 2:3. In this case as well, the gears of the drive transmission gear 81 can be clamped between the first and second gear portions 63c, 63d of the drive-side flange 63, thus establishing a backlash-free state in the rotational direction.

[0274] <Modification Example 2>

[0275] Next, Modification Example 2 will be described. In this modification, the first gear portion 181c and the second gear portion 181d of the drive transmission gear 181 have different numbers of teeth, and the number of teeth on one side is not an integer multiple of the number of teeth on the other side. The first gear portion 163c and the second gear portion 163d of the drive-side flange 163 also have different numbers of teeth, and the number of teeth on one side is not an integer multiple of the number of teeth on the other side. These points of this modification differ from those of the above-described embodiment, and except for these differences and the associated structures, the structure of this modification is the same as that of the above-described embodiment, so their description will be omitted.

[0276] In this modification, the backlash-free state in the rotational direction can also be established in the same manner as in the above embodiment. However, due to the setting of the number of teeth as described above, in the structure of this modification, the meshing phase of the gear relative to the drive transmission gear 181 of the drive side flange 163 is not unique. Figure 25 , regarding the structure in which the meshing phase is not uniquely determined, the position where the drive transmission gear 181 is positioned (balanced) in the axial direction will be described. Figure 25 Part (a) is a schematic diagram of a drive transmission structure using the drive transmission gear 81 of the present embodiment described above. Figure 25 Part (b) is an illustration of a drive transmission portion using the drive transmission gear 181 and the driving side flange 163 of the modified example. Figure 25 Part (c) and Figure 25 Part (d) shows a state in which the drive transmission gear 181 is in a balanced position after the drive transmission gear is driven.

[0277] Compare Figure 25 Part (c) and Figure 25 In the portion (d), the drive transmission gear 181 and the driving side flange 163 are meshed with each other, but the meshing modes at the meshing engagement portions are different from each other. Specifically, Figure 25 Part (c) shows a state in which the tooth tops of the first gear portion 181c and the tooth tops of the second gear portion 181d of the drive transmission gear 181 are aligned in phase with each other at the meshing engagement portion between the drive side flange 163 and the drive transmission gear 181, and the tooth tops of the first gear portion 163c and the second gear portion 163d of the drive side flange 163 are aligned in phase with each other. Figure 25 Part (d) shows a state in which the tooth tops of the first gear portion 181c and the tooth tops of the second gear portion 181d of the drive transmission gear 181 are aligned in phase with each other at the meshing engagement portion, and the tooth tops of the first gear portion 163c and the tooth spaces between the second gear portion 163d of the drive side flange 163 are aligned in phase with each other.

[0278] When the number of teeth of the first gear portion 181c and the second gear portion 181d of the drive transmission gear 181 is different from each other, the phases of the tooth tops of the first gear portion 181c and the second gear portion 181d are different from each other depending on the phase of the gears in the rotational direction. For example, depending on the phase in the rotational direction of the gears, there is a position Q1 where the tooth top portion 181cs of the teeth of the first gear portion and the tooth top 181ds of the second gear portion are aligned in phase with each other, and a position Q2 where the tooth top portion 181cs of the teeth of the first gear portion and the tooth space 181dv of the second gear portion are aligned in phase with each other. This also applies to the relationship between the first gear portion 163c and the second gear portion 163d of the drum gear 163. As a result, as Figure 25 Part (c) and Figure 25 As shown in part (d), the equilibrium position of the drive transmission gear 181 relative to the drive side flange 163 in the axial direction is different depending on the initial (pre-drive) engagement phase between the drive transmission gear 181 and the drive side flange 163 in the rotational direction. Figure 25 Part (c) shows a case where the equilibrium position of the drive transmission gear 181 is the most downstream side in the H direction, and Figure 25 Part (d) shows a case where the equilibrium position of the drive transmission gear 181 is the most downstream side in the J direction. The amount of change in the equilibrium position can be represented, for example, by the amount of deviation of the boundary between the first gear portion 181c and the second gear portion 181d of the drive transmission gear 181 relative to the midline between the first gear portion 163c and the second gear portion 163d of the drive side flange 163. That is, in Figure 25 In the state of part (c), the deviation in the J direction is LD, and Figure 25 In the state of part (d), the deviation amount in the H direction is LE, and therefore, the sum (LD+LE) of the deviation amount LD and the deviation amount LE is the change amount of the equilibrium position in this modification example.

[0279] Before the drive transmission gear 181 reaches the equilibrium position, in the case where the first gear portion 181c is in contact with the second gear portion 163d, or the second gear portion 181d is in contact with the main assembly frame 184, or the second gear portion 181d is in contact with the first gear portion 163c, a backlash-free state cannot be established even if a driving operation is performed. Therefore, in this modified example, the distance LF between the first gear portion 163c and the second gear portion 163d of the drive-side flange 163 (the width of the cylindrical portion 163e) and / or the gap LG between the drive transmission gear 181 and the main assembly frame 184 are selected in consideration of the amount of change (LD+LE) in the equilibrium position.

[0280] On the other hand, Figure 25In the structure of this embodiment shown in part (a), the number of teeth of the first main component gear portion 81c and the second main component gear portion 81d are the same, and the positional relationship between the tooth top 81cs of the first main component gear portion 81c and the tooth top 81ds of the second main component gear portion 81d is not changed by the phase in the rotation direction. Therefore, the position of the drive transmission gear 81 does not change relative to the equilibrium position determined in the axial direction of the drive side flange 63. That is, there is no need to pay attention to the change in the equilibrium position (LD+LE) that must be considered in the modified example. Therefore, in this embodiment, the gap between the first gear portion 63c and the second gear portion 63d of the drive side flange 63 (the width of the cylindrical portion 63e) can be designed to be smaller than the gap in the modified example, and the box B can be miniaturized. In addition, the device main component A of this embodiment can be designed so that the gap between the drive transmission gear 81 and the main component frame 84 is smaller than the gap in the modified example. Thereby, the box B and / or the device main component A can be miniaturized.

[0281] <Other modification examples>

[0282] Next, a modification example will be described in which the main modification is in a portion other than the drive-side flange 63 or the drive transmission structure itself of the drive transmission gear 81 .

[0283] <Application in cleaner-less structure>

[0284] In the above embodiment, in the process cartridge B, the toner remaining on the drum 62 without being transferred is scraped off by the rubber blade 77a contacting the drum 62 and stored in the waste toner chamber 71b ( Figure 3 ). However, the cartridge B may have a cleaner-less structure. In other words, the drive transmission structure of the drive-side flange 63 and the drive transmission gear 81 of the above-described embodiment may be applied to a cartridge having a cleaner-less structure.

[0285] Figure 23: is a sectional view of a box B with a cleaner-free structure. The box B with a cleaner-free structure is constructed and controlled so that the residual colorant on the drum 62 can be recovered by the developing roller 32. Therefore, the box B does not have a rubber scraper in contact with the drum 62, which is a resistance against the rotation of the drum 62, and for this reason, compared with the structure with a rubber scraper 77a in contact with the drum 62, the torque required for the rotation of the drum 62 in the cleaner-free structure is smaller by an amount corresponding to the absence of the rubber scraper 77a. As a result, due to the influence of the impact when the sheet material PA is fed, the rotation speed of the drum 62 tends to fluctuate. In other words, the rotation accuracy of the drum 62 may deteriorate. By applying the drive transmission structure of the drive side flange 63 and the drive transmission gear 81 of the above-mentioned embodiment, the drum 62 can be driven by the transmission between the drive side flange 63 and the drive transmission gear 81 in a zero-backlash state. Therefore, compared with a structure in which drive is transmitted with backlash and play in the rotational direction between the drive-side flange and the drive member on the main assembly side, deterioration in the rotation accuracy of the drum 62 due to the absence of the rubber blade can be suppressed.

[0286] <Application to a structure without a magnetic roller 34>

[0287] Furthermore, in the above-described embodiment, the developer carrying member in which the magnetic roller 34 is provided in the developing roller 32 has been described, but an elastic roller in which no magnetic roller is provided may be used.

[0288] <Application to the Structure in Which the Developing Roller Gear 30 Engages with the Second Gear Portion 63d>

[0289] Furthermore, in the above embodiment, the structure in which the developing roller gear 30 is meshedly engaged with the first gear portion 63c of the driving side flange 63 has been described. However, the developing roller gear 30 may be configured to be meshedly engaged with the second gear portion 63d. Figure 29 , this situation will be described. Figure 29 is a schematic diagram illustrating the engagement between the drive-side flange 63 and the developer roller gear 30. The developer roller gear 130, fixed to the end of the developer roller shaft 31, meshes with the second gear portion 63d. Because the second gear portion 63d has a larger helix angle than the first gear portion 63c, the meshing ratio increases accordingly. Therefore, the developer roller gear 130 meshing with the second gear portion 63d can have a smaller tooth width than the developer roller gear 30 meshing with the first gear portion 63d.

[0290] <Application to the drive transmission structure from the drive side flange to the developing roller gear>

[0291] In addition, the same structure as the driving force transmission structure from the drive transmission gear 81 to the driving side flange 63 can be further applied to the driving force transmission structure from the driving side flange 63 to the developing roller gear 230. Figure 30 Describe the situation. Figure 30 This is a perspective view of cartridge B. The developing roller gear 230 includes a first developing gear portion 230c and a second developing gear portion 230d that mesh with the first gear portion 63c and the second gear portion 63d of the drive-side flange 63, respectively. When the drive-side flange 63 is driven, the developing roller gear 230 moves in the direction of the rotation axis L1 and reaches a balanced position using the same principle as that used in the above-described embodiment to cause the drive transmission gear 81 to move in the direction of the rotation axis L1 and reach a balanced position. When the developing roller gear 230 is in the balanced position, it is driven with no backlash relative to the drive-side flange 63, thereby suppressing misalignment of the developing roller 32 and degradation of its rotational accuracy when load fluctuations occur.

[0292] <Application in a structure where the developing roller gear is not driven by the driving side flange>

[0293] Furthermore, the driving force may not be transmitted to the developing roller 532 via the driving-side flange 63 . Figure 44 53 is a partial perspective view of the cartridge B showing a drive system to the developing roller 532. For better illustration, a portion of the frame of the cartridge B is not shown.

[0294] like Figure 44 As shown, the developing roller 532 is not configured to receive the driving force from the driving side flange 63, but is configured to receive the driving force through another path. Specifically, the box B is provided with a developing coupling member 89, which can be engaged with the coupling member (not shown) of the main component A of the device for driving the developing roller. In addition, the box B is provided with idler wheels 90 and 91 that mesh with the gear portion 89a of the developing coupling member 89, and is provided with a developing roller gear 530 that meshes with the idler wheel 91 at one end of the shaft of the developing roller 532. With this structure, the developing roller 530 is driven by transmitting the driving force received by the developing coupling member 89 by means of the idler wheels 90 and 91 and the developing roller gear 530. Therefore, the drive of the developing coupling member 89 can be controlled separately from the drive of the driving side flange 63, and for example, the developing coupling member 89 can be driven while the driving side flange 63 is not driven.

[0295] <Application to a Drive Transmission Structure to a Rotatable Member Other than a Drum>

[0296] The driving side flange 63 is attached to the end of the drum 62, but the developing roller gear 30 may be provided with a first gear portion 63c, a second gear portion 63d, and a cylindrical portion 63e, and the driving transmission gear 81 drives the developing roller 30. In addition, the object driven by the driving transmission gear 81 is not limited to the developer carrier (e.g., the drum 62) and the developing roller 30 that carries the toner (developer). For example, the object driven by the driving transmission gear 81 may be a feeding member (or agitator member) 43 for conveying (or stirring) the toner, a charging roller 66, or a supply member for supplying the toner to the developing roller 30. In addition, when the object driven by the driving transmission gear 81 is a member other than the drum 62 included in the cartridge B, the cartridge B may be a cartridge that does not include a photosensitive member such as the drum 62.

[0297] [Example 2]

[0298] Next, refer to Figure 31 , Embodiment 2 will be described below. In this embodiment, the structures of the first gear portion and the second gear portion provided on the driving side flange are different from those in Embodiment 1. Since other points are the same as those in Embodiment 1, their description will be omitted.

[0299] Figure 31 It is a cross-sectional view of the meshing engagement portion between the drive transmission gear 81 and the drive side flange 263, and the cross section is in contact with the meshing pitch circle between them. The drive side flange 263 is provided with a first gear portion (first unit side gear portion) 263c and a second gear portion (second unit side gear portion) 263d. The first gear portion 263c includes a plurality of first flat teeth (first protrusions) 263ct, the tooth width of which is designed to be inserted between the teeth of the first main component gear portion 81c. The second gear portion 263d includes a plurality of second flat teeth (second protrusions) 263dt, the tooth width of which is designed to be inserted between the teeth of the second main component gear portion 81d. In addition, the width (tooth width) of the first flat teeth 263ct measured in the direction of the rotation axis L1 is greater than the width (tooth width) of the second flat teeth 263dt measured in the direction of the rotation axis L1. The plurality of first flat teeth and the plurality of second flat teeth are protrusions that protrude in the radial direction relative to the rotation axis L1 , and are arranged at different positions in the circumferential direction around the rotation axis L1 .

[0300] In addition, when using such a drive-side flange 263, the drive transmission gear 81 is rotated in the I direction, and the drive transmission gear 81 moves to the equilibrium position, and a backlash-free state is established as in Example 1. That is, the first main assembly gear portion 81c meshes with the first gear portion 263c and receives a reaction force of the driving force FD and a thrust force F209 in the J direction from the contact point (contact portion) CP1 of the first gear portion 263c. The second main assembly gear portion 81d meshes with the second gear portion 263d and receives a reaction force of the limiting force FB and a thrust force F210 in the H direction from the contact point (contact portion) CP2 of the second gear portion 263d. Similarly, thereby, the drive transmission gear 81 is sandwiched between the first gear portion 263c and the second gear portion 263d of the drive-side flange 263 in the rotational direction in the axial direction, so that a backlash-free state is provided as in Example 1.

[0301] [Example 3]

[0302] Next, refer to Figure 32 , will describe embodiment 3. In this embodiment, the structures of the first gear portion and the second gear portion provided on the driving side flange are different from those in embodiment 1. Since other points are the same as those in embodiment 1, their description will be omitted.

[0303] Figure 32 363c is an illustration of the driving side flange 363. The driving side flange 363 is provided with a first gear portion 363c and a second gear 363d. The first gear portion (first unit side gear portion) 363c includes a plurality of first helical tooth gears (first protrusions) 363ct provided by being divided into a plurality of parts in the direction of the rotation axis L1. Although the plurality of first helical tooth gears (protrusions) 363ct are provided by being divided in the direction of the rotation axis L1, they basically serve as a helical tooth extending in the direction of the rotation axis L1 relative to the first main component gear portion 81c. In addition, the tooth surfaces of the plurality of first helical tooth gears (protrusions) 363ct are a plurality of force receiving portions that receive force from the first main component gear portion 81c. Therefore, it can be said that the plurality of force receiving portions that receive force from the first main component gear portion 81c are provided on the plurality of first helical tooth gears (first protrusions) 363ct. It can be said that the tooth surfaces of the plurality of first helical-tooth gears (protrusions) 363ct constitute a helical tooth surface provided by being divided into a plurality of parts in the direction of the rotation axis L1, or they constitute a plurality of helical tooth surfaces provided by being divided in the circumferential direction centered on the rotation axis L1 of the driving-side flange 363. As described above, the plurality of helical-tooth-shaped protrusions 363ct constitute one tooth of the helical-tooth gear corresponding to one tooth of the first main assembly gear portion 81c.

[0304] The tooth surfaces of the plurality of second helical-toothed gears (protrusions) 363dt serve as force-receiving portions that receive force from the second main assembly gear portion 81d. Therefore, it can be said that the plurality of force-receiving portions that receive force from the second main assembly gear portion 81d are provided on the plurality of second helical-toothed gears (second protrusions) 363dt. The second gear portion (second unit-side gear portion) 363d includes a plurality of second helical-toothed gears (protrusions) 363dt that are arranged by being divided into a plurality of sections in the direction of the rotation axis L1. Although the plurality of second helical-toothed gears (second protrusions) 363dt are arranged by being divided in the direction of the rotation axis L1, they essentially function as a single helical tooth extending in the direction of the rotation axis L1 relative to the second main assembly gear portion 81d. Alternatively, it can be said that the tooth surfaces of the plurality of second helical-toothed gears (protrusions) 363dt constitute a plurality of helical tooth surfaces that are divided in the direction of the rotation axis L1, or that they constitute a helical tooth surface that is divided in the circumferential direction relative to the rotation axis L1 of the drive-side flange 363. As described above, the plurality of helical tooth-like projections 363dt constitute one helical tooth corresponding to one tooth of the second main assembly gear portion 81d.

[0305] Therefore, also when such a driving side flange 363 is used, by the drive transmission gear 81 rotating in the I direction, the drive transmission gear 81 moves to the equilibrium position and a backlash-free state as in Embodiment 1 is established.

[0306] [Example 4]

[0307] Next, refer to Figure 33 , will describe embodiment 4. In this embodiment, the structures of the first gear portion and the second gear portion provided on the driving side flange are different from those in embodiment 1. Since other points are the same as those in embodiment 1, their description will be omitted.

[0308] The driving side flange 463 has two gear portions (a first unit side gear portion and a second unit side gear portion) like the first gear portion 63c and the second gear portion 63d of the driving side flange 63 of Embodiment 1. At least one of the two gear portions has a toothless portion (apparently, a portion where teeth of a gear are intermittently missing) 463L. Figure 33 Part (a) is a view of the driving side flange 463 and the drive transmission gear 81 meshing with each other in a cross section perpendicular to the rotation axis L1. Figure 33Part (b) is a graph showing the change in the number of teeth of the meshing gears. When the meshing ratio between the gear portion of the drive side flange 463 and the gear portion of the drive transfer gear 81 is N teeth with the decimal point discarded (rounded off), the gear portion of the drive side flange 463 may have a missing tooth portion 463L at a maximum of every N-1 teeth. By satisfying this condition, even if the missing tooth portion 463L is provided, there are one or more teeth (meshing ratio is 1 or greater) that mesh with the drive transfer gear 81. With this structure, by the drive transfer gear 81 rotating in the I direction, the drive transfer gear 81 moves to the equilibrium position to establish a backlash-free state as in Example 1. As Figure 33 As shown in part (b) of , the number of gear teeth of the driving side flange 463 that mesh with each gear portion of the drive transmission gear 81 changes during driving.

[0309] [Example 5]

[0310] Next, refer to Figure 34 , will describe embodiment 5. In this embodiment, the structure of the first gear portion and the second gear portion provided on the driving side flange is different from that in embodiment 1. Since other points are the same as in embodiment 1, their description will be omitted.

[0311] The driving side flange 563 is provided with two gear portions (a first unit side gear portion and a second unit side gear portion) like the first gear portion 63c and the second gear portion 63d of the driving side flange 63 of Embodiment 1. At least one of the two gear portions has a tooth-missing portion 563L. Figure 34 Part (a) is a view of the driving side flange 563 and the drive transmission gear 81 meshing with each other in a cross section perpendicular to the rotation axis L1. Figure 34 Part (b) is a view showing the change in the number of teeth of the meshing gears. Figure 34 As shown in part (a), unlike the drive side flange 463 of Example 4, the teeth of the drive side flange 563 are not arranged at equal intervals in the circumferential direction. That is, it can be said that the size of the multiple toothless portions 563 in the circumferential direction is not constant, or the apparent spacing amounts of all toothless portions 563 are not the same. In other words, it is sufficient as long as they are arranged at intervals LI, LJ in the rotation direction, and LI, LJ are natural number (1, 2, ...) multiples of the minimum spacing LH between adjacent teeth. Even if such a toothless portion 563 is provided, it is sufficient as long as there is at least one meshing tooth (meshing ratio is 1 or greater). With this structure, by driving the transmission gear 81 to rotate in the I direction, the transmission gear 81 is moved to the equilibrium position to establish a backlash-free state as in Example 1. As Figure 34 As shown in part (b) of , the number of gear teeth of the driving side flange 463 that mesh with each gear portion of the drive transmission gear 81 is changed.

[0312] [Example 6]

[0313] Next, refer to Figure 35 , Example 6 will be described below. In this example, the structures of the first and second gear portions provided on the drive-side flange differ from those in Example 1. Specifically, in Example 1, both the first and second gear portions 63c and 63d have helical teeth with an involute profile, but this example differs in that the helical teeth do not have an involute profile. Since the remaining points are the same as those in Example 1, their description will be omitted.

[0314] Figure 35 : This is a perspective view of the drive side flange 763. The drive side flange 763 has a first gear portion (first unit side gear portion) 763c and a second gear portion (second unit side gear portion) 763d. The first gear portion 763c includes a plurality of first protrusions 763ct, and the second gear portion 63d includes a plurality of second protrusions 763dt. The first protrusion 763ct and the second protrusion 763dt are protrusions that protrude in the radial direction relative to the rotation axis L1, and the cross-sectional shape in the cross section perpendicular to the rotation axis L1 is a trapezoidal shape with the width narrowing toward the free end. In addition, the first protrusion 763ct and the second protrusion 763dt are helical teeth twisted around the rotation axis L1. Even with this structure, the first gear portion 763c and the second gear portion 763d also serve as helical gears that mesh with the drive transmission gear 81. Therefore, by rotating the drive transmission gear 81 in the I direction, the drive transmission gear 81 moves to a balanced position to establish a backlash-free state as in Example 1.

[0315] The cross-sectional shape of the first protrusion 763ct and the second protrusion 763dt is not limited to a trapezoidal shape, but may be a protrusion shape such as a rectangular, triangular, or curved shape, or a shape having chamfered corners.

[0316] [Example 7]

[0317] Next, refer to Figure 36 , Example 7 will be described. In this embodiment, the structure of the first and second gear portions provided on the drive-side flange differs from that of Example 1. Specifically, the torsion direction of first gear portion 63c and second gear portion 63d is opposite to that of Example 1. Consistent with this structure, the torsion direction of the first main assembly gear portion and second main assembly gear portion of the drive transmission gear is also opposite to that of Example 1. Since other points are the same as those of Example 1, their description will be omitted.

[0318] Figure 36 8 is a schematic diagram showing the engagement between the drive transmission gear 881 and the drive side flange 863. Figure 36 As shown, the first gear portion (first unit side gear portion) 863c and the second gear portion (second unit side gear portion) 863d of the driving side flange 863 are twisted in such a direction that the tooth surface is offset in the I direction as the gear advances in the J direction. The first gear portion 881c and the second gear portion 881d of the drive transmission gear 881 are twisted in such a direction that the tooth surface is offset in the K direction as the gear advances in the J direction.

[0319] Since the twisting direction is opposite to that of Example 1, the direction of the thrust F21 applied to the drive transmission gear 881 by meshing engagement during driving of the drive transmission gear 881 is also opposite to that of Example 1. Therefore, when moving to the equilibrium position in the axial direction, a space having a width LK for moving the drive transmission gear 881 in the H direction is required. Therefore, a compression spring 185 for urging the drive transmission gear 881 in the J direction is provided so that the drive transmission gear 881 is placed against the positioning portion 83b of the second drive side plate 83 before the cartridge B is installed.

[0320] Also, with this structure, by the drive transmission gear 881 rotating in the I direction, the drive transmission gear 881 moves to the equilibrium position to establish a backlash-free state as in Embodiment 1.

[0321] [Example 8]

[0322] Next, refer to Figure 37 , will describe embodiment 8. This embodiment has a different structure in which the cartridge B is mounted to the main assembly of the apparatus compared to embodiment 1. Since other points are the same as in embodiment 1, description thereof will be omitted.

[0323] Figure 37 is a perspective view of the imaging device 800. In the imaging device 800, the insertion direction for inserting the box B into the main component A of the device is parallel to or substantially parallel to the rotation axis L1 of the drum 62. Even if the box B is fully inserted in the direction parallel to the rotation axis L1, the drive side flange 63 and the drive transmission gear (not shown) of the main component A of the device cannot engage with each other because there is a distance between them in the direction perpendicular to the rotation axis L1. Thereafter, by closing the door 211, the box B is displaced at least in the direction VD perpendicular to the rotation axis L1 by a lifting mechanism (not shown) provided in the main component A of the device and connected to the door 211, and the drive side flange 63 and the drive transmission gear (not shown) of the main component A of the device engage with each other.

[0324] The driving operation after the driving side flange 63 and the drive transmission gear (not shown) are meshedly engaged with each other is the same as in Embodiment 1, and the drive transmission gear moves to the equilibrium position to establish the backlash-free state as in Embodiment 1.

[0325] When the cartridge B is displaced at least in the direction VD perpendicular to the rotation axis L1 by the elevating mechanism, the cartridge B can be displaced not only in the direction perpendicular to the rotation axis L1 but also in the direction of the rotation axis L1. Furthermore, the elevating mechanism can be configured to rotate the cartridge B about an axis perpendicular to the rotation axis L1 and to displace the driving-side flange 63 in the direction VD perpendicular to the rotation axis L1.

[0326] In addition, instead of closing the door 211 to operate the lifting mechanism after inserting the box B into the main assembly A of the device, the box B can be displaced at least in the direction VD perpendicular to the rotation axis L1 during the insertion of the box B into the main assembly A of the device. Specifically, in the initial stage of the insertion stroke of the box B into the main assembly A of the device, the box B is guided by a guide (not shown) so as to move the box B in a direction parallel to the rotation axis L1. Then, in the final stage of the insertion stroke, the box B is guided by a guide (not shown) so as to displace the box B at least along the direction VD perpendicular to the rotation axis L1. In this way, the structure can change the moving direction (installation direction) of the box B during the insertion process.

[0327] [Example 9]

[0328] Next, refer to Figure 38 , Example 9 will be described. In this embodiment, the structure of the first gear portion and the second gear portion provided on the drive-side flange differs from that in Example 1. Specifically, in this embodiment, the arrangement of the first gear portion 963c and the second gear portion 963d in the direction of the rotation axis L1 is opposite to that of the first gear portion 63c and the second gear portion 63d in Example 1. Consistent with this structure, the positions of the first main assembly gear portion and the second main assembly gear portion of the drive transmission gear in the direction of the rotation axis L1 are also opposite to those in Example 1. Since other points are the same as in Example 1, their description will be omitted.

[0329] Figure 38Schematic diagram showing the meshing engagement between the drive transmission gear 981 and the drive side flange 963. The drive side flange 963 is provided with a first gear portion (first unit side gear portion) 963c and a second gear portion (second unit side gear portion) 963d. The helix angle of the second gear portion 963d is greater than the helix angle of the first gear portion 963c. The first gear portion 963c is arranged on the downstream side (drive side) of the second gear portion 963d in the J direction. That is, the second gear portion 963d is arranged between the first gear portion 963c and the drum 62 in the direction of the rotation axis L1. Similarly, the drive transmission gear 981 is provided with a first gear portion 981c meshing with the first gear portion 963c and a second gear portion 981d meshing with the second gear portion 963d. Their positions in the direction of the rotation axis L1 are opposite to those in Example 1.

[0330] Also by this structure, by the drive transmission gear 981 being driven, the drive transmission gear 981 moves to the equilibrium position. During the subsequent driving operation, the first gear portion 963c receives the driving force FD (see Figure 17 and the second gear portion 963d receives the limiting force FB (see Figure 17 Part (d)) of the embodiment establishes a backlash-free state.

[0331] Here, the end portion of the drum unit 969 on the driving side (downstream side in the J direction) where the driving side flange 963 and the drum 62 are integrated is rotatably supported by the shaft member 86 (see also Figure 4 ). In addition, the first gear portion 963c is arranged at a position closer to the root portion of the shaft member 86 than the second gear portion 963d. In addition, in the driving side flange 963, the force applied to the tooth surface of the first gear portion 963c that receives the driving force FD is greater than the force applied to the tooth surface of the second gear portion 963d that receives the limiting force FB. Therefore, the driving force FD may act to tilt the rotation axis L1 of the drum unit 969, and therefore, the drum 62 may tilt relative to the ideal rotation axis L1. However, as in the present embodiment, by arranging the first gear portion 963c that receives the driving force FD at a position closer to the root portion of the shaft member 86 than the second gear portion 963d, the tilting of the rotation axis L1 of the drum unit 969 caused by being subjected to the driving force FD can be suppressed.

[0332] [Example 10]

[0333] Next, refer to Figure 39Next, Example 10 will be described. In this example, the structures of the first and second gear portions provided on the drive-side flange differ from those in Example 1. Specifically, while the first and second gear portions 63c, 63d in Example 1 have the same position and width in the direction of the rotation axis L1, in this example, the positions and widths of the teeth in the direction of the rotation axis L1 differ (unlike Example 1). Since the remaining points are the same as in Example 1, their description will be omitted.

[0334] Figure 39 The figure is a cross-sectional view of the meshing engagement portion between the drive transmission gear 81 and the drive-side flange 1063, and the cross-section is in contact with the meshing pitch circle between the drive transmission gear and the drive-side flange. The drive-side flange 1063 is provided with a first gear portion (first unit-side gear portion) 1063c and a second gear portion (second unit-side gear portion) 1063d. The first gear portion 1063c includes a plurality of first helical teeth (first protrusions) 1063ct having different widths and positions along the direction of the rotation axis L1. The second gear portion 1063d includes a plurality of second helical teeth (second protrusions) 1063dt having different widths and positions along the direction of the rotation axis L1.

[0335] In the case of this structure, the meshing ratio is different from the case of using the drive-side flange 63 of Example 1, but the first gear portion 1063c and the second gear portion 1063d are respectively used as helical gears similar to the first gear portion 63c and the second gear portion 63d. Therefore, when the drive transmission gear 81 rotates in the I direction, the drive transmission gear 81 moves to the equilibrium position, so that the backlash-free state is established as in Example 1.

[0336] [Example 11]

[0337] Next, refer to Figure 40 Next, Example 11 will be described. In this example, the structure of the second gear portion provided on the driving-side flange differs from that in Example 1. Specifically, the second gear portion 63d of Example 1 is a helical gear, but in this example, unlike Example 1, it is a spur gear. Since the other points are the same as in Example 1, their description will be omitted.

[0338] Figure 40The figure is a cross-sectional view of the meshing engagement portion between the drive transmission gear 81 and the drive side flange 1163, and the cross-section is in contact with the meshing pitch circle between the drive transmission gear and the drive side flange. The drive side flange 1163 is provided with a first gear portion (first unit side gear portion) 1163c and a second gear portion (second unit side gear portion) 1163d. The first gear portion 1163c is the same as the first gear portion 63c of Example 1, and the second gear portion 1163d includes a plurality of second flat teeth (teeth, second protrusions) 1163dt. The plurality of second flat teeth 1163dt are flat teeth having a tooth width and tooth thickness, the dimensions of which are designed to be inserted between the teeth (inter-tooth portion) of the second main component gear portion 81d of the drive transmission gear 81. Therefore, the width (tooth width) of the second flat teeth (second protrusions) 1163dt in the direction of the rotation axis L1 is smaller than the width (tooth width) of the first gear portion 1163c in the direction of the rotation axis L1. In other words, the second gear portion 1163d has second flat teeth (second protrusions) 1163dt having a width narrower than that of the first helical teeth of the first gear portion 1163c having the maximum width (tooth width) in the direction of the rotation axis L1.

[0339] The width (length) of the second protrusion 1163dt in the rotational direction (direction I) or the circumferential direction is smaller than the width (length) of one tooth of the first gear portion 1163c in the rotational direction (direction I) or the circumferential direction. In other words, the second gear portion 1163d includes the second protrusion 1163dt that is narrower in the rotational direction (direction I) or the circumferential direction than the first helical tooth of the first gear portion 1163c, which has the largest width (length) in the rotational direction (direction I) or the circumferential direction.

[0340] Furthermore, the second projection 1163dt has a contact portion CP2 which contacts the second main assembly gear portion 81d. Figure 40 As shown, the contact portion CP2 is provided at the corner portion of the second protrusion 1163dt. The corner portion (contact point CP2) is provided so that the corner portion (contact point CP2) contacts one tooth of the second main assembly gear portion 81d only at one point in the direction of the rotation axis L1. The radius of curvature of the corner portion can be set to a desired value, and the corner portion can have a sharper shape by making the radius of curvature smaller, or a less sharp corner can be formed by increasing the radius of curvature, as shown in the second protrusion 1363dt shown in Example 13 to be described below.

[0341] When the drive transmission gear 81 is driven, it receives a thrust force F1109 in the J direction and moves in the J direction in the same manner as in Example 1. Then, the surface 81d2 of the second main assembly gear portion 81d, located on the upstream side in the I direction, contacts the contact portion CP2 of the second flat teeth 1163dt of the second gear portion 1163d, and receives a thrust force F1110 in the H direction. Thus, the drive transmission gear 81 is positioned at a balanced position based on the same principle as in Example 1 to establish a backlash-free state. Furthermore, in the backlash-free state, for drive in the rotational direction, the first gear portion 1163c receives a driving force FD, and the second gear portion 1163d receives a limiting force FB at the contact portion CP2 of the second flat teeth 1163dt.

[0342] [Example 12]

[0343] Next, refer to Figure 41 Next, Example 12 will be described. In this example, the structure of the second gear portion provided on the drive-side flange differs from that of Example 1. Specifically, the helix angle of the second gear portion 63d in Example 1 is greater than the helix angle of the first gear portion 63c, but this is not the case with the helix angle of the second gear portion 1263d in this example. Since the remaining points are the same as those in Example 1, their description will be omitted.

[0344] Figure 41It is a cross-sectional view of the meshing engagement portion between the drive transmission gear 81 and the drive side flange 1263, and the cross section is in contact with the meshing pitch circle between the drive transmission gear and the drive side flange. The drive side flange 1263 is provided with a first gear portion (first unit side gear portion) 1263c and a second gear portion (second unit side gear portion) 1263d. The first gear portion 1263c is the same as the first gear portion 63c of Example 1. The second gear portion 1263d includes a plurality of second helical teeth (teeth, second protrusions) 1263dt. The helical angle of the plurality of second helical teeth 1263dt is the same as the helical angle of the helical teeth of the first gear portion 1263c. In addition, similar to the plurality of second helical teeth 1163dt of Example 11, the plurality of second helical teeth 1263dt have tooth widths and tooth thicknesses that are designed to be inserted between the teeth (inter-tooth portion) of the second main component gear portion 81d of the drive transmission gear 81. Therefore, the width (tooth width) of the second helical teeth (second protrusions) 1263dt measured in the direction of the rotation axis L1 is smaller than the width (tooth width) of the first gear portion 1263c measured in the direction of the rotation axis L1. In other words, the second gear portion 1263d includes the second helical teeth (second protrusions) 1263dt, the width of which is narrower than the width of the first helical teeth of the first gear portion 1263c having the maximum width (tooth width) in the direction of the rotation axis L1.

[0345] Furthermore, the width (length) of the second protrusion 1263dt in the rotational direction (direction I) or the circumferential direction is smaller than the width (length) of one tooth of the first gear portion 1263c in the rotational direction (direction I) or the circumferential direction. In other words, the second gear portion 1263d includes the second protrusion 1263dt, the width of which in the rotational direction (direction I) or the circumferential direction is narrower than the width of the first helical tooth of the first gear portion 1263c having the largest width (length) in the rotational direction (direction I) or the circumferential direction.

[0346] Furthermore, the second projection 1263dt has a contact portion CP2 which contacts the second main assembly gear portion 81d. Figure 41 As shown, the contact portion CP2 is provided at the corner portion of the second protrusion 1263dt. The corner portion (contact point CP2) is provided so that the corner portion (contact point CP2) contacts one tooth of the second main assembly gear portion 81d only at one point in the direction of the rotation axis L1. The radius of curvature of the corner portion can be set to a desired value, and the corner portion can have a sharper shape by making the radius of curvature smaller, or a less sharp corner can be formed by increasing the radius of curvature, as shown in the second protrusion 1363dt shown in Example 13 to be described below.

[0347] By being driven by the drive transmission gear 81, the drive transmission gear 81 receives a thrust F1209 in the J direction and moves in the J direction as in the first embodiment. Then, the surface 81d2 of the second main assembly gear portion 81d located on the upstream side in the I direction contacts the contact portion CP2 of the second helical tooth 1163dt of the second gear portion 1263d, and receives a thrust F1210 in the H direction. Thus, the drive transmission gear 81 is positioned at a balanced position based on the same principle as in Embodiment 1, thereby establishing a backlash-free state. Furthermore, in the backlash-free state relative to the drive in the rotational direction, the first gear portion 1263c receives the driving force FD, and the second gear portion 1263d receives a limiting force FB at the contact portion CP2 of the second helical tooth 1263dt.

[0348] [Example 13]

[0349] Next, refer to Figure 42 Next, Example 13 will be described. This example differs from Example 1 in the structure of the portion corresponding to the second gear portion provided on the drive-side flange. Specifically, whereas the second gear portion 63d of Example 1 is a helical gear, this example, unlike Example 1, comprises a plurality of cylindrical protrusions. Since the remaining features are the same as those of Example 1, their description will be omitted.

[0350] Figure 42 Part (a) is a perspective view of the drive side flange 1363. Figure 42 Part (b) is a sectional view of the meshing engagement portion between the drive transmission gear 81 and the driving side flange 1363, and the cross section is in contact with the meshing pitch circle between the drive transmission gear and the driving side flange.

[0351] The driving side flange 1363 is provided with a first gear portion (first unit side gear portion) 1363c and a second gear portion (second unit side gear portion) 1363d. The first gear portion 1363c is the same as the first gear portion 63c of the embodiment 1.

[0352] The second gear portion 1363d includes a plurality of cylindrical second protrusions (teeth) 1363dt that protrude radially from a tooth-bottom cylindrical portion (base cylindrical portion) 1363Bd extending along the rotation axis L1. The second gear portion 1363d is a rotating portion that rotates integrally with the first gear portion 1363c. The plurality of second protrusions 1363dt are arranged in the same position relative to the direction of the rotation axis L1 (on the same plane perpendicular to the rotation axis L1).

[0353] Furthermore, the tips S of the plurality of second protrusions 1363dt are arranged on a predetermined circumference centered on the rotation axis L1 when viewed from the rotation axis L1, and are spaced equally in the circumferential direction. The tip circle of the second gear portion 1363d is the circle that represents the rotational trajectory traced by the free end S of the plurality of second protrusions 1363dt that is furthest from the rotation axis (rotation axis L1) of the second gear portion 1363d when the drive-side flange 1363 rotates. In this embodiment, all second protrusions 1363dt have the same shape, and therefore, the free end S of all second protrusions 1363dt are located at the same distance from the rotation axis L1, so that all free end S trace the same rotational trajectory. Furthermore, the diameter / radius of this rotational trajectory circle corresponds to the tip circle diameter / tip circle radius of the second gear portion 1363d.

[0354] The plurality of second protrusions 1363dt are protrusions whose widths in the direction of rotation axis L1 and in the rotational direction (I direction) are sized to be inserted between the teeth (inter-tooth portions) of the second main assembly gear portion 81d of the drive transmission gear 81. Therefore, the width of the second protrusions 1363dt measured in the direction of rotation axis L1 is smaller than the width (tooth width) of the first gear portion 1363c measured in the direction of rotation axis L1. In other words, the second gear portion 1363d has second protrusions 1363dt whose width in the direction of rotation axis L1 is narrower than the width of the first helical teeth of the first gear portion 1363c, which have the largest width (tooth width) in the direction of rotation axis L1. The width (length) of the second protrusions 1363dt in the rotational direction (I direction) or the circumferential direction is greater than the width (length) of a single tooth of the first gear portion 1363c in the rotational direction (I direction) or the circumferential direction. In other words, the second gear portion 1363d includes a second protrusion 1363dt, the width of which in the rotational direction (I direction) or the circumferential direction is smaller than the width of the first spiral tooth of the first gear portion 1363c having the maximum width (length) in the rotational direction (I direction) or the circumferential direction.

[0355] Furthermore, the second projection 1363dt has a contact portion CP2 which contacts the second main assembly gear portion 81d. Figure 42As shown in part (b), the contact portion CP2 is on the curved portion of the surface of the second protrusion 1363dt. The curved portion of the surface of the second protrusion 1363dt can be referred to as a corner portion. The corner portion (contact point CP2) is arranged so that the corner portion (contact point CP2) contacts one tooth of the second main component gear portion 81d only at one point in the direction of the rotation axis L1. The curvature radius of the corner portion can be set to a desired value, and the curvature radius can be made smaller to form a corner portion with a sharper shape, or the curvature radius can be made larger to form a less sharp corner portion.

[0356] When the drive transmission gear 81 is driven, the drive transmission gear 81 receives a thrust in the J direction and moves in the J direction as in Embodiment 1. Then, the surface 81d2 of the second main assembly gear portion 81d located on the upstream side in the I direction contacts the contact portion CP2 of the second protrusion 1363dt of the second gear portion 1163d, and receives a thrust F1310 in the H direction. Thus, the drive transmission gear 81 is positioned at a balanced position based on the same principle as in Embodiment 1, and a backlash-free state is established. Furthermore, in the backlash-free state, with respect to the drive in the rotational direction, the first gear portion 1363c receives a driving force FD, and the second gear portion 1363d receives a limiting force FB at the contact portion CP2 of the second protrusion 1363dt.

[0357] Therefore, the second gear portion 1363d is capable of engaging with other gears (e.g., the second main component gear portion 81d) by using multiple second protrusions 1363dt and is capable of receiving rotational drive force and / or thrust, and therefore in this respect, it can be considered as a gear.

[0358] Furthermore, the plurality of second protrusions 1363dt are not limited to a cylindrical shape and may have a shape that protrudes at least in a radial direction relative to the rotation axis L1 and may be, for example, a polygonal column shape. Furthermore, all of the plurality of second protrusions 1363dt do not necessarily have the same shape.

[0359] [Example 14]

[0360] Next, refer to Figure 43 Next, Example 14 will be described. This example differs from Example 1 in the structure of the portion corresponding to the second gear portion provided on the drive-side flange. Specifically, whereas the second gear portion 63d of Example 1 was a helical gear, this example, unlike Example 1, comprises a plurality of cylindrical protrusions. Since the remaining features are identical to Example 1, their description will be omitted. Furthermore, the only difference between this example and Example 13 lies in the arrangement of the plurality of cylindrical protrusions.

[0361] Figure 43Part (a) is a cross-sectional view of the teeth and protrusions of the driving side flange 1463, and its cross section is in contact with a circle centered on the rotation axis L1. Figure 43 Part (b) is a sectional view of the meshing engagement portion between the drive transmission gear 81 and the driving side flange 1463, and its cross section is in contact with the meshing pitch circle between the drive transmission gear and the driving side flange.

[0362] The driving side flange 1463 is provided with a first gear portion (first unit side gear portion) 1463c and a second gear portion (second unit side gear portion) 1463d. The first gear portion 1463c is the same as the first gear portion 63c of the embodiment 1.

[0363] The second gear 1463d includes a plurality of cylindrical second protrusions 1463dt that protrude in a radial direction relative to the rotation axis L1. The second gear portion 1463d is a rotatable portion that can rotate integrally with the first gear portion 1463c. The plurality of second protrusions 1463dt are arranged at positions offset in the direction of the rotation axis L1.

[0364] In addition, the free end portions S of the plurality of second protrusions 1463dt (see Figure 43 The portion (a)) is arranged on a predetermined circumference centered on the rotation axis L1 as viewed along the rotation axis L1. The plurality of second protrusions 1463dt are protrusions whose width measured in the direction of the rotation axis L1 and the width measured in the rotation direction (I direction) are designed so that the protrusions can be inserted between the teeth (inter-tooth portion) of the second main component gear portion 81d of the drive transmission gear 81. In addition, the plurality of second protrusions 1463dt are inserted between the teeth (inter-tooth portion) of the second main component gear portion 81d of the drive transmission gear 81, and are arranged at positions where they can receive the limiting force FB from the second main component gear portion 81d in a state without tooth gap. Specifically, as Figure 43As shown in part (a), a plurality of imaginary torsion lines (helical lines) L9 twisted at the same angle as the helical angle α2 of the second main component gear portion 81d are drawn on a cylindrical surface centered on the rotation axis L1 at a predetermined pitch P9. The pitch P9 is the same as the pitch of the plurality of second helical teeth 81dt of the second main component gear portion 81d of the drive transmission gear 81 in a direction perpendicular to the tooth surface. Moreover, the plurality of second protrusions 1463dt are arranged so that the following conditions are satisfied with respect to the plurality of torsion lines L9. The condition is that the plurality of torsion lines L9 can be arranged so that some of the plurality of torsion lines L9 are in contact with some of the plurality of second protrusions 1463dt, and no torsion line among the plurality of torsion lines L9 passes through a cross section of the plurality of second protrusions 1463dt. This embodiment is capable of performing the same function as the plurality of second protrusions 1363dt of Example 13, namely, by arranging the plurality of second protrusions 1463dt so as to satisfy this condition, the plurality of second protrusions 1463dt receive the restricting force FB from the second main assembly gear portion 81d in a backlash-free state. Furthermore, similarly to Example 13, the corner portions (contact points CP2) of the second protrusions 1463dt are arranged so that the corner portions can contact one tooth of the second main assembly gear portion 81d only at one corner portion (contact point CP2) in the direction along the rotation axis L1.

[0365] When the drive transmission gear 81 is driven, as shown in FIG. Figure 43 As shown in part (b) of the embodiment, the drive transmission gear 81 receives the thrust F1409 and moves in the J direction as in Example 1. Furthermore, the surface 81d2 of the second main assembly gear portion 81d located on the upstream side in the I direction contacts the contact portion CP of the second protrusion 1463dt of the second gear portion 1463d and receives the thrust F1410 in the H direction. Therefore, the drive transmission gear 81 is positioned at the equilibrium position based on the same principle as in Example 1 to establish a backlash-free state. In addition, in the backlash-free state, with respect to the drive in the rotational direction, the first gear portion 1463c receives the driving force FD, and the second gear portion 1463d receives the limiting force FB at the contact portion CP2 of the second protrusion 1463dt.

[0366] Since the second gear portion 1463d is capable of engaging with other gears (e.g., the second main component gear portion 81d) by using a plurality of second protrusions 1463dt and is capable of receiving rotational drive force and / or thrust, and therefore in this respect, it can be considered to be a gear.

[0367] In addition, the shape of the plurality of second protrusions 1463dt is not limited to a cylindrical shape, and may also be a shape protruding at least in the radial direction relative to the rotation axis L1, and all of the plurality of second protrusions 1463dt do not necessarily have the same shape.

[0368] [Example 15]

[0369] Next, refer to Figure 45 , Example 15 will be described. The drive transmission structure in the cartridge B is different from that in Example 1. Figure 45 Part (a) is a partial sectional view of the cartridge B in the vicinity of the drum 62, taken along a line including the rotation axis L1. Figure 45 Part (b) is a view of the drum 62 and the developing roller 632 of the box B when viewed in the direction perpendicular to the rotation axis L1.

[0370] The gear that meshes with the drive transmission gear 81 does not have to be integrally fixed to the end of the drum 62. Figure 45 As shown in part (a) of the drawing, a driven gear 1563, which meshes with the drive transmission gear 81, is rotatably supported at both end portions by a shaft 1578 fixed to one end of the cleaning frame 1571. Specifically, the shaft 1578 supports the driven gear 1563 while passing through it. The driven gear 1563 comprises a first gear portion (first unit-side gear portion) 1563c, a helical gear having a helical angle α1, and a second gear portion (second unit-side gear portion) 1563d, a helical gear having a helical angle α2, similar to the first gear portion 63c and the second gear portion 63d provided on the drive-side flange 63 of Example 1. Furthermore, a developing roller gear 632 is integrally provided at one end portion of the developing roller 632 with the developing gear 630 meshing with the second gear portion 1563d of the driven gear 1563, and a drum drive gear 92 is integrally provided at the other end portion of the developing roller 632. Furthermore, a drum gear 93, which meshes with the drum drive gear 92, is integrally mounted to one end of the drum 62 by clamping or the like, and is rotatably supported by the drum shaft. Furthermore, a drum flange 1564 is mounted to the other end of the drum by clamping or the like, and is rotatably supported by the shaft 1578. With this structure, the driving force received by the driven gear 1563 from the drive transmission gear 81 is transmitted to the drum 62 in the order of the developing roller gear 630, the developing roller 632, the drum drive gear 92, and the drum gear 93.

[0371] [Example 16]

[0372] Next, refer to Figure 48, Example 16 will be described. In this embodiment, the structure of the portion corresponding to the first gear portion and the second gear portion provided on the driving side flange is different from that in Example 1. Specifically, the first gear portion 63c and the second gear portion 63d of Example 1 are helical gears, but in this embodiment, each gear portion is provided with a plurality of protrusions (protrusions forming each tooth of the gear), which is different from Example 1. Since other points are the same as in Example 1, their description will be omitted.

[0373] Figure 48 Part (a) is a cross-sectional view of the teeth and protrusions of the driving side flange 1663, and its cross section is in contact with a circle centered on the rotation axis L1. Figure 48 Part (b) is a cross-sectional view of the meshing engagement portion between the drive transmission gear 81 and the driving side flange 1663, and the cross section is in contact with the meshing pitch circle between the drive transmission gear and the driving side flange.

[0374] The first gear portion (first unit-side gear portion, first unit-side helical gear portion) 1663c includes a plurality of cylindrical first protrusions 1663ct that protrude from a tooth bottom cylindrical portion (base cylindrical portion) extending along the rotation axis L1 in a radial direction relative to the rotation axis L1. The plurality of first protrusions 1663ct are arranged at the same position and at different positions relative to the direction of the rotation axis L1.

[0375] In addition, the free ends S of the plurality of first protrusions 1663ct (see Figure 42 Part (a)) is arranged on a predetermined circumference centered on the rotation axis L1 as viewed along the rotation axis L1. The plurality of first protrusions 1663ct are protrusions whose width in the direction of the rotation axis L1 and the width in the rotation direction (I direction) are designed so that the protrusions can be inserted between the teeth (inter-tooth portion) of the first main component gear portion 81c of the drive transmission gear 81. In addition, the plurality of first protrusions 1663ct are arranged at positions such that they are inserted between the teeth (inter-tooth portion) of the first main component gear portion 81c of the drive transmission gear 81, and receive the driving force FD from the first main component gear portion 81c in a state without tooth gap. Specifically, as Figure 48As shown in part (a), multiple imaginary torsion lines L15 twisted at the same angle as the helical angle α1 of the first main component gear portion 81c are drawn on a cylindrical surface centered on the rotation axis L1 (helical line) at a predetermined pitch P11. This pitch P11 is the same as the pitch of the multiple first helical teeth 81ct of the first main component gear portion 81c of the drive transmission gear 81 in a direction perpendicular to the tooth surface. Then, the multiple first protrusions 1663dt are arranged so that the following conditions are satisfied with respect to the multiple torsion lines L5. The condition is that the multiple torsion lines L11 can be arranged so that some of the multiple torsion lines L15 contact some of the multiple first protrusions 1663ct, and no torsion line in the multiple torsion lines L11 passes through the cross section of the multiple first protrusions 1663ct. By arranging the multiple first protrusions 1663ct to satisfy this condition, the multiple first protrusions 1663ct engage with the first main component gear portion 81c in a backlash-free state and rotate to receive the driving force FB.

[0376] The second gear portion (second unit-side gear portion, second unit-side helical gear portion) 1663d includes a plurality of cylindrical second protrusions 1663dt that protrude radially relative to the rotation axis L1. The second gear portion 1663d is a rotatable portion that rotates integrally with the first gear portion 1663c. The plurality of second protrusions 1663dt are arranged at positions offset relative to the direction of the rotation axis L1.

[0377] In addition, the free end portions S of the plurality of second protrusions 1663dt (see Figure 42 The portion (a) is arranged on a predetermined circumference centered on the rotation axis L1 when viewed along the rotation axis L1. The plurality of second protrusions 1663dt are protrusions whose width in the direction of the rotation axis L1 and the width in the rotation direction (I direction) are designed so that the protrusions can be inserted between the teeth (inter-tooth portion) of the second main component gear portion 81d of the drive transmission gear 81. In addition, the plurality of second protrusions 1663dt are arranged at positions such that they can be inserted between the teeth (inter-tooth portion) of the second main component gear portion 81d of the drive transmission gear 81, and can receive the limiting force FB from the second main component gear portion 81d in a zero-tooth gap state. Specifically, as Figure 48As shown in part (a), a plurality of imaginary torsion lines L14 twisted at the same angle as the helical angle α2 of the second main component gear portion 81d are drawn on a cylindrical surface centered on the rotation axis L1 (helical line) at a predetermined pitch P10. The pitch P10 is the same as the pitch of the plurality of second helical teeth 81dt of the second main component gear portion 81d of the drive transmission gear 81 in a direction perpendicular to the tooth surface. Furthermore, the plurality of second protrusions 1663dt are arranged so that the following conditions are satisfied with respect to the plurality of torsion lines L14. The condition is that the plurality of torsion lines L14 can be arranged so that some of the plurality of torsion lines L14 are in contact with some of the plurality of second protrusions 1663dt, and no torsion line among the plurality of torsion lines L14 passes through a cross section of the plurality of second protrusions 1663dt. By arranging multiple second protrusions 1663dt to satisfy this condition, multiple second protrusions 1663dt can perform the same functions as the multiple second protrusions 1363dt of Example 13 can perform, that is, the protrusions engage with the second main component gear portion 81d in a tooth gap-free state to rotate and receive the limiting force FB.

[0378] like Figure 48 As shown in part (b) of the embodiment, when the drive transmission gear 81 is driven, the drive transmission gear 81 moves in the J direction as in Example 1. This is because the first main component gear portion 81c contacts the multiple first protrusions 1663ct and receives a thrust in the J direction. In the drive transmission gear 81 that has moved in the J direction, the surface 81d2 of the second main component gear portion 81d on the upstream side in the I direction eventually contacts the contact portion CP2 of the second protrusion 1663dt of the second gear portion 1663d and receives a thrust F1610 in the H direction. In addition, the surface 81c1 of the first main component gear portion 81c on the downstream side in the I direction contacts the contact portion CP1 of the first protrusion 1663ct of the first gear portion 1663c and receives a thrust F1609 in the J direction. Therefore, the drive transmission gear 81 is positioned at the equilibrium position based on the same principle as in Example 1, and a backlash-free state is established. Furthermore, in the backlash-free state, regarding the driving in the rotation direction, the first gear portion 1663c receives the driving force FD, and the second gear portion 1663d receives the restricting force FB at the contact portion CP of the second protrusion 1463dt.

[0379] The first gear portion 1663c can be engaged with other gears (e.g., the first main component gear portion 81d) by using the plurality of first protrusions 1663ct, and it can receive a rotational drive force and / or thrust, and therefore in this respect, it can be considered to be a gear (helical tooth gear). That is, it can be said that the surfaces of the plurality of first protrusions 1663ct (the plurality of contact portions CP1) constitute a plurality of helical tooth surfaces provided by being divided in the direction of the rotation axis L1, or constitute a helical tooth surface provided by being divided into a plurality of parts in the circumferential direction and centered on the rotation axis L1 of the drive side flange 1663.

[0380] Therefore, by connecting multiple contact portions CP1, a torsion line L15 can be defined. Multiple first protrusions 1663ct are arranged to be able to contact a tooth of the first main component gear portion 81c at multiple positions separated from each other in the direction of the rotation axis L1. It can be said that multiple contact portions CP1 that can simultaneously contact a tooth of the first main component gear portion 81c are set at positions separated from each other relative to the direction of the rotation axis L1. In this way, it can be said that the multiple first protrusions 1663ct arranged separately in the direction of the rotation axis L1 constitute a tooth (helical tooth) that meshes with a tooth of the first main component gear portion 81c. Therefore, the multiple first protrusions 1663ct serve as helical tooth gears, and the first gear portion 1663c is a first helical gear portion.

[0381] Furthermore, a circle drawn as a rotation locus when the free end portion (point) farthest from the rotation axis L1 among the plurality of first protrusions 1663ct rotates is the addendum circle of the first gear portion 1663c, and the diameter of the circle is the addendum circle diameter.

[0382] Similarly, the second gear portion 1663d can be engaged with other gears (e.g., the second main assembly gear portion 81d) by using the plurality of second protrusions 1663dt, and can receive a rotational drive force and / or thrust, and therefore in this respect, it can be considered to be a gear. That is, it can be said that the surfaces of the plurality of second protrusions 1663dt (the plurality of contact portions CP2) constitute a plurality of helical tooth surfaces provided by being divided in the direction of the rotation axis L1, or constitute a helical tooth surface provided by being divided into a plurality of parts in the circumferential direction and centered on the rotation axis L1 of the drive side flange 1663.

[0383] Therefore, by connecting multiple contact portions CP2, a torsion line L14 can be defined. Multiple second protrusions 1663dt are arranged to contact a tooth of the second main component gear portion 81d at multiple positions separated from each other in the direction of the rotation axis L1. It can be said that multiple contact portions CP2 that can simultaneously contact a tooth of the second main component gear portion 81d are arranged at positions separated from each other in the direction of the rotation axis L1. In this way, it can be said that the multiple second protrusions 1663dt separated and arranged in the direction of the rotation axis L1 constitute a tooth (helical tooth) that meshes with a tooth of the second main component gear portion 81d. Therefore, the multiple second protrusions 1663dt serve as helical tooth gears, and the second gear portion 1663d is a second helical tooth gear portion.

[0384] Furthermore, a circle drawn as a rotation locus when the free end portion (point) farthest from the rotation axis L1 among the free end portions of the plurality of second protrusions 1663dt rotates is the addendum circle of the second gear portion 1663d, and the diameter of the circle is the addendum circle.

[0385] Furthermore, each of the plurality of first protrusions 1663ct and the plurality of second protrusions 1663dt is not limited to a cylindrical shape and may have a shape that protrudes at least in the radial direction relative to the rotation axis L1. Furthermore, the plurality of first protrusions 1663ct need not be a plurality of completely separate protrusions and may include a plurality of contact portions CP1. For example, the cross-sectional shape in a tangential direction perpendicular to the radial direction relative to the rotation axis L1 may have a stepped shape, wherein portions of the cross-sectional shape are connected. The same applies to the plurality of second protrusions 1663dt. Furthermore, not all of the plurality of first protrusions 1663ct may have the same shape, and not all of the plurality of second protrusions 1663dt may have the same shape.

[0386] [Example 17]

[0387] The difference between Example 17 and Example 1 is as follows. First, the layout of the structure in the main component A of the device on which box B can be installed is different. As a result, the posture of box B in the main component A of the device is different. In addition, the supporting structure of the drive side flange 1763 and the engagement structure of the drive transmission gear 1781 and the idler gear 1780 are different. The drive transmission structure to the developing roller 1732 is the same as the other modified examples of Example 1. In addition, the positional relationship in the axial direction between the first gear portion that receives the driving force FD and the second gear portion that receives the limiting force FB is the same as that of Example 9. The other points are the same as in Example 1, so a detailed description thereof will be omitted. In addition, among the elements of this embodiment, the elements (example: drum 1762) corresponding to the elements of Example 1 (example: drum 62) are associated with the corresponding elements of Example 1 (for example, the figure mark "1762" corresponds to "62"). Regarding these elements, the content that is not specifically described is the same as the corresponding elements of Example 1.

[0388] <Configuration of Main Assembly of Apparatus>

[0389] Figure 50 17 is a cross-sectional view of the apparatus main assembly A on which the cartridge B is mounted (the cross section is perpendicular to the rotation axis L1). The apparatus main assembly A of the image forming apparatus 17100 includes an exposure device (laser scanner unit) 1703 and a sheet tray 1704 for accommodating a sheet material PA. In addition, the apparatus main assembly A includes a pickup roller (not shown) provided along a conveyance path of the sheet material PA, a feed roller pair 1705b, a transfer guide 1706, a transfer roller 1707, a feed guide 1708, a fixing device 1709, a discharge roller pair 1710, and a discharge tray 1711.

[0390] <Posture of Box B in Device Main Assembly A>

[0391] like Figure 50 As shown, the cartridge B is positioned in the apparatus main assembly A with the cleaning unit 1760 and the developing unit 1720 positioned substantially horizontally. At this time, the transfer roller 1707 is positioned below the drum 1762.

[0392] <Support Structure of Cleaning Unit 1760 for Drum Unit 1769>

[0393] Next, refer to Figure 51 Part (a), Figure 51 Part (b) Figure 52 Part (a), Figure 52 Part (b) Figure 52 Part (c), Figure 58 and Figure 59 , the supporting structure of the drum unit 1769 by the cleaning unit 1760 will be described.

[0394] Figure 51 Part (a) is an exploded perspective view of the cleaning unit 1760, and shows a state in which the cleaning unit 1760 is viewed from the developing unit side so that the inner side of the drum supporting member 1773 can be seen. Figure 51 Part (b) is an exploded perspective view of the cleaning unit 1760, and shows a state in which the cleaning unit 1760 is viewed from the developing unit side so that the outside of the drum supporting member 1773 can be seen. Figure 52 Part (a) is a perspective view of the drum support member 1773 when viewed from the inside. Figure 52 Part (b) is a sectional view of the guided portion 1773g of the drum supporting member 1773 supporting the driving side flange 1763, taken along a cross section perpendicular to the rotation axis L1. Here, the sectional view shows a state in which the section is viewed from the inner side of the drum supporting member 1773. Figure 52 The portion (c) is along the mounting direction M (see FIG. 1 ) including the rotation axis L1 and mounted to the apparatus main assembly A with the cartridge B. Figure 57 ) is a sectional view of a portion near the drive side flange 1763 of box B mounted on the main component A of the device, taken along a plane perpendicular to the drawing. Figure 58 It is a sectional view of the cleaning unit 1760 and the drive transmission gear 1781 as viewed from the outside of the drum supporting member 1773 , and its cross section passes through the hole 1773 d of the drum supporting member 1773 supporting the driving side flange 1763 and is perpendicular to the rotation axis L1 . Figure 59 It is a partial perspective view of the vicinity of the drive side flange 1763 of box B.

[0395] like Figure 51 Part (a) and Figure 51 As shown in part (b) of , the cleaning unit 1760 includes a frame member 1771 and a drum supporting member 1773 fixed to the frame member 1771, which constitute a drum frame supporting the drum 1762. The driving side flange 1763 is provided with a cylindrical protrusion (supported portion) 1763g, which is centered on the rotation axis L1 and protrudes outward (downstream in the J direction) from the end surface of the first gear portion 1763c on the rotation axis L1 so as to protrude from the end of the driving side flange 1763 toward the downstream side in the J direction. The drum supporting member 1773 is provided with a hole 1773d recessed in the direction of the rotation axis L1 (J direction) for supporting the protrusion 1763g. As shown in FIG. Figure 52 Part (a) and Figure 52As shown in part (b) of the drawing, the inner peripheral surface of the hole 1773d has surfaces 1773e and 1773f and two circumferential surfaces 1773h and 1773i, each of which is parallel to the rotation axis L1. In addition, the two surfaces 1773e and 1773f are not parallel to each other and are arranged to provide a substantially V-shaped concave shape when viewed from the direction of the rotation axis L1. Surfaces 1773e and 1773f are support surfaces (support portions) having support points that contact and support the protrusion 1763g. As shown in FIG. Figure 58 As shown, the substantially V-shaped concave shape provided by the two surfaces 1773e and 1773f is oriented to oppose force FH, which is parallel to force FG, originating at the rotation axis L1, so as to receive meshing engagement force FG between the tooth surfaces of the gears when the driving force is transmitted from the drive transmission gear 1781 to the drive-side flange 1763. Specifically, the bisector of the angle formed by the extension lines of surface 1773e and surface 1773f, as viewed along the rotation axis L1, is substantially parallel to force FH. The orientation of the two surfaces 1773e and 1773f is not limited to this example and can be selected in consideration of various forces that apply load to the drive-side flange 1763.

[0396] After the drum unit 1769 is incorporated into the interior of the frame member 1771, the drum support member 1773 is mounted to the frame member 1771 and fixed so that the protrusion 1763g of the drive side flange 1763 fits into the hole 1773d of the drum support member 1773. Thus, the drum unit 1769 is rotatably supported by the frame member 1771 and the drum support member 1773. In addition, as Figure 59 and Figure 114 As shown in part (b) of the drawing, in the completed state as the cartridge B, a part of the driving side flange 1763 (a part of the first gear portion 1363 c and the second gear portion 1363 d ) and a part of the drum 1762 are not covered by the drum frame (the drum supporting member 1773 and the frame member 1771 ) but are exposed to the outside of the cartridge B. That is, it can be said that the drum frame has an opening so that a part of the driving side flange 1763 (a part of the first gear portion 1363 c , a part of the second gear portion 1363 d , etc.) and a part of the drum 1762 are exposed toward the outside.

[0397] like Figure 52 As shown in part (c) of the drawing, when the cartridge B is mounted in the apparatus main assembly A, the arcuate surface of the guided portion 1773g contacts the two positioning portions 1715a of the first drive side plate 1715 of the apparatus main assembly A, and the position of the rotation axis L1 of the cartridge B relative to the apparatus main assembly A is determined in two directions perpendicular to the rotation axis (the mounting direction M and the orthogonal direction MP perpendicular to the mounting direction M) (see FIG. Figure 57). The guided portion 1773g is a protruding portion having a shape that protrudes outward (in the J direction) in the direction of the rotation axis L1, and the above-mentioned hole 1773d is provided on the inner side of the protruding portion. The main component A of the device is provided with a pressing member (not shown) that presses the box B so as to press the guided portion 1773g toward the two positioning portions 1715a. In addition, the meshing force FG on the tooth surface of the gear when the driving force is transmitted from the drive transmission gear 1781 to the drive side flange 1763 is also used to press the guided portion 1773g toward the two positioning portions 1715a. In addition, the transfer roller 1707 (see Figure 50 ) The force of the pressing drum 1762 is also used to press the guided portion 1773g toward the positioning portion 1715a in the orthogonal direction MP.

[0398] At least a portion of the guided portion 1773g, at least a portion of the two flat surface portions 1773f and 1773e, and at least a portion of the protrusion 1763g are placed in the same position in the direction of the rotation axis L1. In other words, at least a portion of the guided portion 1773g, at least a portion of the two flat portions 1773f and 1773e, and at least a portion of the protrusion 1763g are arranged on a surface perpendicular to the rotation axis L1. Through this arrangement, deformation of the drum support member 1773 in which it tilts relative to the rotation axis L1 can be suppressed, and tilting (deflection) of the drive side flange 1763 relative to the rotation axis L1 can be suppressed. As a result, degradation of the meshing accuracy between the drive side flange 1763 and the drive transmission gear 1781 can be suppressed. In addition, by making the protrusion 1763g abut the two flat surface portions 1773f and 1773e, the assembly clearance is concentrated in one direction (along the direction of the bisector of the angle formed between the extension lines of the flat surface portions 1773e and 1773f when viewed along the rotation axis L1), thereby improving the position accuracy of the drive side flange 1763 in the direction perpendicular to the rotation axis L1, and suppressing the deterioration of the meshing engagement accuracy with the drive transmission gear 1781.

[0399] In this embodiment, the protrusion 1763 g is formed integrally with the driving-side flange 1763 , but the protrusion 1763 g may be formed of another portion of metal or the like and press-fitted into the driving-side flange 1763 .

[0400] Next, the positioning of the driving side flange 1763 in the axial direction will be described. Figure 51 Part (a) and Figure 51As shown in part (b) of FIG, the first gear portion 1763c of the drive-side flange 1763 has a protrusion 1763c1 on its downstream end surface in the H direction, which slightly protrudes in the H direction. Furthermore, a protrusion 1763f is provided on its downstream end surface in the J direction (upstream end surface in the H direction). Furthermore, the frame member 1771 includes a rib 1771p and a side wall 1771m, which extend perpendicularly to the rotation axis L1. The protrusion 1763c1 contacts the side surface of the rib 1771p, and the protrusion 1763f contacts the side surface of the side wall 1771m. The drive-side flange 1763 is slidably fitted and retained between the rib 1771p and the side wall 1771m in the direction of the rotation axis L1. This positions the drive-side flange 1763 on the frame member 1771 in the direction of the rotation axis L1, and consequently, determines the position of the drum unit 1769 within the frame member 1771.

[0401] <Installation and Removal of Cartridge B Relative to the Main Assembly of the Apparatus A and Positioning within the Main Assembly of the Apparatus A>

[0402] Figure 113 Part (a) is a view of the cartridge B mounted in the apparatus main assembly A mounted on a horizontal mounting surface as viewed in the direction of the rotational axis L1 (direction K), with the horizontal direction being HD and the vertical direction being VD. A plane perpendicular to the rotational axis L1 is parallel to the vertical direction VD. Figure 113 Part (b) is as follows Figure 113 Part (a) is a view of box B when viewed in the direction HD1 parallel to the horizontal direction HD. Figure 114 Part (a) is as follows Figure 113 Part (a) is a view of box B when viewed in the direction VD1 parallel to the vertical direction VD. Figure 114 Part (b) is as follows Figure 113 A view of the box B when viewed from the direction VD2 parallel to the vertical direction VD shown in part (a). Figure 50 It can be understood that, as viewed in the direction of the rotation axis L1, the straight line connecting the rotation center of the developing roller 1732 and the rotation center of the photosensitive drum 1762 (the rotation axis L1) is substantially parallel to the mounting direction M. Therefore, in the following description, the mounting direction M can be considered to be a direction perpendicular to the rotation axis L1 and parallel to the straight line connecting the rotation center of the developing roller 1732 and the rotation center of the photosensitive drum 1762 (the rotation axis L1).

[0403] Similar to Embodiment 1, the mounting direction M in which the cartridge B is mounted to the apparatus main assembly A and the removal direction (the direction opposite to the mounting direction M) in which the cartridge B is removed from the apparatus main assembly A are directions substantially perpendicular to the rotation axis L1. In addition, the mounting direction in which the drum unit 69 is mounted to the apparatus main assembly A and the removal direction in which the drum unit 69 is removed from the apparatus main assembly A are the same as the mounting direction M in which the cartridge B is mounted to the apparatus main assembly A and the removal direction in which the cartridge B is removed from the apparatus main assembly A, respectively.

[0404] like Figure 113 As shown in part (a), in addition to the above-mentioned guided portion 1773g, the drum supporting member 1773 is also provided with a guided portion 1773s1, a guided portion 1773s2 and a guided portion 1773s3. These guided portions are protrusions having a shape protruding from the main component part of the drum supporting member 1773 in the direction of the rotation axis L1. When box B is installed on the main component A of the device and removed from the main component A of the device, box B contacts and is guided by a guide portion (not shown) provided on the main component A of the device. As shown in other figures, the guided portion 1773s1 can be omitted. Taking necessity into consideration, the guided portion 1773s3 can also be omitted. However, by providing the guided portion 1773s1 and the guided portion 1773s3, the installation and removal of box B are made more stable. In addition, the guided portion 1773s1 is a protrusion that is long in the installation direction M (or long in a direction perpendicular to the rotation axis L1 and parallel to the straight line connecting the rotation center of the developing roller 1732 and the rotation center of the photosensitive drum 1762 (rotation axis L1)). By making the guided portion 1773s1 a long protrusion in this way, the rigidity of the drum supporting member 1773 is improved. In addition, although the guided portion 1773s1 and the guided portion 1773g are provided as one connecting protrusion, they can be provided as separate protrusions. However, when provided as one connecting protrusion, the rigidity of the drum supporting member 1773 is improved.

[0405] In addition, as described above, in the state where the cartridge B is mounted in the apparatus main assembly A, the guided portion 1773g contacts the two positioning portions 1715a of the apparatus main assembly A, and the position of the rotation axis L1 of the cartridge B relative to the apparatus main assembly A is determined in two directions (the mounting direction M and the orthogonal direction MP) perpendicular to the rotation axis L1 (see FIG. Figure 52 Part (c) and Figure 57 ). Further, by bringing the guided portion 1773s2 into contact with the positioning portion of the apparatus main assembly A (not shown), the position (attitude) of the cartridge B relative to the apparatus main assembly A is determined in the rotational direction about the rotation axis L1.

[0406] Furthermore, the positioning of the cartridge B relative to the apparatus main assembly A in the direction of the rotation axis L1 is the same as that of Embodiment 1. Specifically, as Figure 113Part (b) and Figure 114 As shown in part (a), the drum supporting member 1773 has a recessed assembly portion 1773h recessed along the mounting direction M, and a protruding assembly portion (not shown) protruding along the mounting direction M of the device main component A is assembled into the assembly portion 1773h, thereby determining the position of box B relative to the device main component A in the direction of the rotation axis L1.

[0407] In addition, if Figure 113 As shown in part (a) of the drawing, the drum supporting member 1773 is provided with a substantially cylindrical developing unit supporting portion 1773b extending in the direction of the rotation axis L1. The developing unit supporting portion 1773b supports the cylindrical portion 1721a placed around the developing coupling member 1789 and the coupling portion 1789a of the frame 1721 of the developing unit 1720 so that the cylindrical portion can rotate (swing) around the rotation axis DA. The rotation axis DA is coaxial with the rotation axis of the developing coupling member 1789 and is parallel to the rotation axis L1. By receiving a force from a force applying portion (not shown) of the main assembly A of the device at a force receiving portion 1721b of the frame 1721 of the developing unit 1720, the developing unit 1720 is able to rotate (swing) around the rotation axis DA in the DS direction relative to the cleaning unit 1760. By this rotation, the developing roller 1732 can be spaced apart from the drum 1762.

[0408] In addition, if Figure 113 As shown in part (a) of the drawing, when the cartridge B is viewed in the direction of the rotation axis L1, the guided portion 1773s2 is arranged on a straight line LT passing through the rotation axis L1 and the rotation axis DA, and the developing unit supporting portion 1773b and the rotation axis DA are arranged between the rotation axis L1 and the guided portion 1773s2 in a direction parallel to the straight line LT. Therefore, the cleaning unit 1760 can firmly support the relatively heavy developing unit 1720. Therefore, it can be said that the developing unit supporting portion 1773b and the rotation axis DA are arranged between the rotation axis L1 and the guided portion 1773s2 in any one of the mounting direction M (or the longitudinal direction of the guided portion 1773s1), the orthogonal direction MP perpendicular to the mounting direction M (or the direction perpendicular to the longitudinal direction of the guided portion 1773s1), the horizontal direction HD, and the vertical direction VD.

[0409] In addition, when the area is divided into two areas by the straight line LT, when the box B is observed along the direction of the rotation axis L1, the guided portion 1773s1 is arranged in one area, and the guided portion 1773s3 is arranged in another area, and therefore, the posture of the box B during the installation and removal of the box B is stable.

[0410] In addition, if Figure 113 Part (b) Figure 114Part (a) and Figure 114 As shown in part (b), the drum frame of the cleaning unit 1760 includes the above-mentioned drum supporting member (first supporting member) 1773 and the frame member 1711, and in addition, the drum frame includes a non-driving side drum supporting member (second supporting member) 1712 mounted to the frame member 1711. As described above, in the drum unit 1769, the driving side flange 1763 (first flange member) is rotatably supported by the drum supporting member 1773. On the other hand, the non-driving side flange (second flange member) 1764 of the drum unit 1769 is rotatably supported by the non-driving side drum supporting member 1712. The non-driving side flange 1764 is a member fixed to the downstream end portion of the drum 1762 in the H direction. That is, the drum supporting member (first supporting member) 1773 is arranged at the first end of the frame in the direction of the rotation axis L1 of the drum frame, and the non-driving side drum supporting member (second supporting member) 1712 is arranged at the second end opposite to the first end. Of the two ends of the drum 62 in the direction of the rotation axis L1, the first end of the photosensitive member is an end located closer to the first end of the frame than the distance from the second end of the frame, and the second end of the photosensitive member on the opposite side of the first end is an end located closer to the second end of the frame than the distance from the first end of the frame. Figure 114 As can be understood from the portion (a) and the portion (b) of 114, the non-driving side drum supporting member 1712 includes a protruding shape portion 1712a having a shape protruding downstream in the mounting direction M. Here, from Figure 50As can be understood, when viewed in the direction of the rotation axis L1, the straight line connecting the rotation center of the developing roller 1732 and the rotation center of the photosensitive drum 1762 (rotation axis L1) is parallel to the mounting direction M. Therefore, the protruding shape portion 1712a has a shape that protrudes toward the downstream of the drum support member 1773 or the drum 1762 with respect to the following direction, which is perpendicular to the rotation axis L1 and points from the rotation center of the developing roller 1732 to the rotation center of the photosensitive drum 1762 (a direction substantially parallel to the mounting direction M). The memory board 1740 on which the nonvolatile memory chip is mounted is mounted to the protruding shape portion 1712a. The memory board 1740 is provided with an electrode portion (electrode surface) 1740a, which is a surface that is electrically connected to the nonvolatile memory chip and can be electrically connected by contact with an electrode portion (not shown) on the main component side of the main component A of the device. With respect to the direction of the rotation axis L1, the electrode portion 1740a is provided at a position near the end portion (second frame end portion) on the side (non-drive side) opposite to the end portion (first frame end portion) on the side (drive side) where the drum supporting member 1773 and the drive side flange 1763 are provided. Specifically, with respect to the direction of the rotation axis L1, the area in which the electrode portion 1740a is provided is an area including the position of the end portion on the downstream side of the drum 1762 in the H direction (the second end portion of the photosensitive member). However, with respect to the direction of the rotation axis L1, the area in which the electrode portion 1740a is provided may be located at a position closer to the outside of the drum frame (or the outside of the box B) than the position of the end portion on the downstream side of the drum 1762 in the H direction (the second end portion of the photosensitive member). In addition, with respect to the direction of the rotation axis L1, the area in which the electrode portion 1740a is provided and the area in which the non-drive side flange 1764 is provided are at least partially at the same position (at least partially overlap). However, with respect to the direction of the rotation axis L1, the area where the electrode portion 1740a is provided is closer to the outside of the drum frame (or the outside of the cartridge B) than the area where the non-drive side flange 1764 is provided (the downstream position in the H direction). Furthermore, the electrode portion 1740a is arranged on the downstream side of the rotation axis L1 and the photosensitive drum 1762 with respect to the mounting direction M. Furthermore, the electrode portion 1740a is arranged on the downstream side of the rotation axis L1 or the photosensitive drum 1762 with respect to the direction perpendicular to the rotation axis L1 and pointing from the rotation center of the developing roller 1732 to the rotation center of the photosensitive drum 1762 (a direction substantially parallel to the mounting direction M). Furthermore, the memory plate 1740 is supported by the cleaning unit 1760 in a posture in which the electrode portion (electrode surface) 1740a is oriented perpendicularly to the mounting direction M.

[0411] <Drive side flange 1763>

[0412] Next, refer to Figure 54 Part (b) and Figure 60 , the driving side flange 1763 will be described. Figure 54 Part (b) is a schematic cross-sectional view of the gear portion of the drive side flange 1763. This cross section is a plane that contacts the meshing pitch circle when meshing with the drive transmission gear 1781. Figure 60 Part (a) and Figure 60 Part (b) is a cross-sectional view of the drum unit 1769 in the vicinity of the driving side flange 1763, taken along a plane including the rotation axis L1.

[0413] The drive-side flange 1763 includes a first gear portion (first unit-side gear portion, first unit-side helical gear portion) 1763c and a second gear portion (second unit-side gear portion, second unit-side helical gear portion) 1763d, which are coaxial with each other. The first gear portion 1763c is located upstream in the H direction (downstream in the J direction) relative to the second gear portion 1763d. That is, the second gear portion 1763d is located between the first gear portion 1763c and the drum 1762 along the direction of the rotation axis L1. The first gear portion 1763c includes a plurality of first helical teeth (teeth, first protrusions) 1763ct arranged at different positions in the circumferential direction around the rotation axis L1, and the second gear portion 1763d includes a plurality of second helical teeth (teeth, second protrusions) 1763dt arranged at different positions in the circumferential direction around the rotation axis L1. Both the first helical teeth 1763ct and the second helical teeth 1763dt have an involute tooth profile and are protrusions that protrude in the radial direction relative to the rotation axis L1. The first gear portion 1763c and the second gear portion 1763d are integrally molded from resin and rotatable as a whole. Therefore, it can be said that the first gear portion 1763c and the second gear portion 1763d are first and second rotatable portions that rotate as a whole. The first gear portion 1763c meshes with the first main assembly gear portion 1781c of the drive transmission gear 1781, and the second gear portion 1763d meshes with the second main assembly gear portion 1781d of the drive transmission gear 1781.

[0414] The first gear portion 1763c and the second gear portion 1763d of the drive-side flange 1763 have the same twisting direction, and their tooth surfaces twist so as to advance in the K direction as they advance in the J direction. The twisting directions of the first and second gear portions 1763c, 1763d are opposite to those of the first and second main assembly gear portions 1781c, 1781d of the drive transmission gear 1781. Furthermore, as in Example 1, the helix angle of the second gear portion 1763d is greater than that of the first gear portion 1763c. The helix angle of the first gear portion 1763c is the same as that of the first main assembly gear portion 1781c, which will be described below, and the helix angle of the second gear portion 1763d is the same as that of the second main assembly gear portion 1781d, which will be described below. Furthermore, the first and second gear portions 1763c, 1763d of the drive-side flange 1763 have the same number of teeth.

[0415] In addition, if Figure 60 As shown in section (a) of the embodiment, the width (tooth width) Wc of the first helical tooth (tooth, first protrusion) 1763ct measured in the direction of rotation axis L1 is greater than the width (tooth width) Wd of the second helical tooth (tooth, second protrusion) 1763dt measured in the direction of rotation axis L1. That is, each of the first gear portion 1763c and the second gear portion 1763d has at least one tooth that satisfies the following formula A1, where Wc is the tooth width of the first helical tooth 1763ct (tooth, first protrusion) in the direction of rotation axis L1, and Wd is the tooth width of the second helical tooth 1763dt in the direction of rotation axis L1: Wc > Wd (Formula A1). When the drive-side flange 1763 is driven by the drive transmission gear 1781 in a balanced state, the driving force FD received by the first gear portion 1763c is greater than the restraining force FB received by the second gear portion 1763d. Therefore, this relationship is preferably satisfied.

[0416] In addition, the width (meshing width) of the portion where the first gear portion 1763c meshes (contacts) with the first main component gear portion 1781c in the rotation direction L1 and the engagement width (meshing width) of the second helical gear portion 1763c with the second main component gear portion 1781d are preferably larger because the drive transmission accuracy is better. However, if the meshing width is set to be larger than the required width, the widths of the first gear portion 1763c and the second gear portion 1763d in the direction of the rotation axis L1 are large, and the drive side flange 1763, the drum unit 1769, the cartridge B, and finally the main component A of the device will increase in size. Therefore, the tooth width Wc1 of the first helical tooth (tooth) 1763ct having the widest tooth width in the first gear portion 1763c and the tooth width Wd1 of the second helical tooth (tooth) 1763dt having the widest tooth width in the second gear portion 1763d preferably satisfy the following formula A2, and further preferably satisfy formula A3.

[0417] Wd1≤(4 / 5)×Wc1 (Formula A2)

[0418] Wd1≤(3 / 4)×Wc1 (Formula A3)

[0419] In addition, from the viewpoint of the strength of the second helical teeth (teeth) 1763dt of the second gear portion 1763d, it is preferable that the tooth width of the second helical teeth (teeth) 1763dt is greater than a certain level, and the tooth width Wc1 and the tooth width Wd1 satisfy the following formula A4.

[0420] Wd1≥(1 / 10)×Wc1(Formula A4)

[0421] Furthermore, as in Embodiment 1, the width (length) We of the cylindrical portion 1763e (or the gap g) in the direction of the rotation axis L1 is selected so as to satisfy the formulas B1, B2, and B3 based on the widths Wc and Wd:

[0422] When the tooth width Wc of the first gear portion 1763 c is not constant, the tooth width Wc1 of the tooth having the widest tooth width is assumed as the tooth width.

[0423] We≥Wc / 5 (Formula B1)

[0424] We≤Wc (Formula B2)

[0425] We≤Wd (Formula B3).

[0426] In this embodiment, the teeth of the first gear portion 1763c have the same tooth width, and the teeth of the second gear portion 1763d also have the same tooth width, with tooth width Wc being 8.2 mm and tooth width Wd being 5.2 mm. The width We is 3.1 mm.

[0427] In addition, if Figure 60 As shown in part (b), when the driving side flange 1763 and the drive transmission gear 1781 are engaged, the meshing pitch diameters D63c and D63d of the first gear portion 1763c and the second gear portion 1763d are substantially the same. Similarly, the meshing pitch diameters of the first main component gear portion 1781c and the second main component gear portion 1781d are substantially the same. Thus, the meshing between the first gear portion 1763c and the first main component gear portion 1781c and the meshing between the second gear portion 1763d and the second main component gear portion 1781d can be appropriate without tooth tip collision.

[0428] In addition, as in Example 1, the tooth top circle diameter Dt63c of the first gear portion 1763c and the tooth root circle diameter Db63d of the second gear portion 1763d are substantially the same, so that the meshing with the first main component gear portion 1781c and the second main component gear portion 1781d establishes a correct meshing engagement without tooth top collision.

[0429] Specifically, the tooth tip diameter Dt63c of the first gear portion 1763c is preferably larger than the tooth root diameter Db63d of the second gear portion 1763d, or is larger than 0.8 times (more preferably 0.9 times) the tooth tip diameter Dt63d of the second gear portion 1763d. Furthermore, the tooth tip diameter Dt63c of the first gear portion 1763c is preferably smaller than 1.1 times the tooth tip diameter Dt63d of the second gear portion 1763d.

[0430] Furthermore, the root diameter Db63c of the first gear portion 1763c is preferably smaller than the root diameter Dt63d of the second gear portion 1763d. Furthermore, the root diameter Db63c of the first gear portion 1763c is preferably greater than 0.9 times the root diameter Db63d of the second gear portion 1763d.

[0431] Furthermore, the tooth tip diameter Dt63d of the second gear portion 1763d is larger than the tooth root diameter Db63c of the first gear portion 1763c, or is larger than 0.8 times (more preferably 0.9 times) the tooth tip diameter Dt63c of the first gear portion 1763c. Furthermore, the tooth tip diameter Dt63d of the second gear portion 1763d is preferably smaller than 1.1 times the tooth tip diameter Dt63c of the first gear portion 1763c.

[0432] Furthermore, the root diameter Db63d of the second gear portion 1763d is preferably smaller than the root diameter Dt63c of the first gear portion 1763c. Furthermore, the root diameter Db63d of the second gear portion 1763d is preferably greater than 0.9 times the root diameter Db63c of the first gear portion 1763c.

[0433] In this embodiment, the tip diameter Dt63c, pitch diameter D63c, and root diameter Db63c of the first gear portion 1763c are 22.3 mm, 21.1 mm, and 19.6 mm, respectively. The tip diameter Dt63d, pitch diameter D63d, and root diameter Db63d of the second gear portion 1763d are 22.1 mm, 21.1 mm, and 19.8 mm, respectively. The diameter of the cylindrical portion 1763e is 17.5 mm.

[0434] Furthermore, the module and / or the amount of tooth addendum modification are made different between the first gear portion 1763c and the second gear portion 1763d, so that the meshing pitch diameters D63c and D63d are the same while the helix angles of the first gear portion 1763c and the second gear portion 1763d are made different from each other. Similarly, with respect to the drive transmission gear 1781, the module and / or the amount of tooth addendum modification are made different between the first main assembly gear portion 1781c and the second main assembly gear portion 1781d.

[0435] Furthermore, the driving-side flange 1763 is provided with a cylindrical portion (intermediate portion, small diameter portion, shaft portion) 1763e between the first gear portion 1763c and the second gear portion 1763d in the direction of the rotation axis L1. The maximum diameter D63e centered about the rotation axis L1 of the cylindrical portion 1763e is smaller than the addendum diameter Dt63c of the first gear portion 1763c and the addendum diameter Dt63d of the second gear portion 1763d. Furthermore, in this embodiment, the maximum diameter D63e centered about the rotation axis L1 of the cylindrical portion 1763e is smaller than the root diameter Db63c of the first gear portion 1763c and the root diameter Db63d of the second gear portion 1763d. However, if the driving-side flange 1763 is driven by the drive transmission gear 1781 while not in contact with the drive transmission gear 1781, the maximum diameter D63e centered about the rotation axis L1 of the cylindrical portion 1763e is not limited to the above. As will be described below in Examples 22 and 23, the structure can cause the distance (radius) R63e from the rotation axis L1 to the outer diameter of the cylindrical portion 1763e to be at least temporarily smaller than the tooth top circle radius Rt63ct of the first gear portion 1763c or the tooth top circle radius Rt63d of the second gear portion 1763d, so that the driving side flange 1763 and the drive transmission gear 1781 engage with each other to transmit driving force.

[0436] It goes without saying that the parts showing the relationship between the dimensions using the various diameters of the first gear portion 1763c, the second gear portion 1763d, and the cylindrical portion 1763e also apply when the diameter is replaced by the radius.

[0437] <Drive Transmission Gear 1781>

[0438] Next, refer to Figure 53 and Figure 54 Part (a) of the present invention will describe the drive transmission gear 1781 of the main component A of the device engaged with the drive side flange 1763. Figure 53 Part (a) and Figure 53 Part (b) is a decomposed perspective view of the peripheral portion of the drive transmission gear 1781 of the main component A of the device, wherein part (a) is a view as viewed from the second drive side plate 1783 side, and part (b) is a view as viewed from the main frame 1784 side. Figure 54 Part (a) is a schematic cross-sectional view of the gear portion of the drive transmission gear 1781. This cross section is in contact with the meshing pitch circle when meshing with the driving side flange 1763.

[0439] The drive transmission gear 1781 coaxially includes a first main component gear portion (first main component helical gear portion) 1781c and a second main component gear portion (second main component helical gear portion) 1781d as a helical gear portion. The first main component gear portion 1781c is arranged on the upstream side in the H direction (downstream side in the J direction) relative to the second main component gear portion 1781d. The first main component gear portion 1781c includes a plurality of first main component helical teeth 1781ct, and the second main component gear portion 1781d includes a plurality of second main component helical teeth 1781dt. The first main component helical teeth 1781ct and the second main component helical teeth 1781dt both have an involute tooth profile. The first main component gear portion 1781c and the second main component gear portion 1781d are integrally resin molded and can rotate integrally. In addition, the torsion direction of the first main component gear portion 81c and the second main component gear portion 81d are the same, and the tooth surfaces are twisted so as to shift in the I direction as they travel in the J direction. In addition, similar to Embodiment 1, the helix angle of the second main assembly gear portion 1781d is greater than the helix angle of the first main assembly gear portion 1781c. In addition, the number of teeth of the first main assembly gear portion 81c and the second main assembly gear portion 81d are the same. In a state where the cartridge B is mounted on the apparatus main assembly A, the first gear portion 1763c meshes with the first main assembly gear portion 1781c, and the second gear portion 1763d meshes with the second main assembly gear portion 1781d.

[0440] Figure 112 1781 is a perspective view of another structural example of the drive transmission gear 1781. Figure 112 As shown, a rib-shaped portion (protruding portion, radially protruding main portion) 1781p protruding in a radial direction relative to the rotation axis L2 can be provided between the first main component gear portion 1781c and the second main component gear portion 1781d in the direction of the rotation axis L2. Depending on the manufacturing method of the drive transmission gear 1781, by providing the rib-shaped portion 1781p, it is possible to improve molding accuracy, suppress degradation, or reduce manufacturing costs. The diameter of the rib-shaped portion 1781p is substantially the same as the diameter of the tooth top circle of the first main component gear portion 1781c and the diameter of the tooth top circle of the second main component gear portion 1781d. The rib-shaped portion 1781p can be provided on the entire circumference, or can be provided only partially in the circumferential direction centered on the rotation axis L2. Here, by providing the cylindrical portion 1763e for the drive side flange 1763, a gap g is formed between the first gear portion 1763c and the second gear portion 1763d in the direction of the rotation axis L1 (refer to Figure 60 etc.). Due to the provision of this gap g, even when the drive transmission gear 1781 has the rib-shaped portion 1781p, the rib-shaped portion 1781p and the driving side flange 1763 are prevented from contacting each other, and the gear portion of the driving side flange 1763 and the drive transmission gear 1781 can be properly engaged with each other. At this time, the rib-shaped portion 1781p is inserted into (enters) the gap g between the first gear portion 1763c and the second gear portion 1763d.

[0441] like Figure 53 Part (a) and Figure 53 As shown in part (b) of the drawing, the main component A of the device includes a motor (not shown), an idler wheel 1780, a drive transmission gear 1781, a second drive side plate 1783, a main frame 1784, a drive shaft 1782, a reinforcing member 1798 and a compression spring 1785. The second drive side plate 1783 is a component corresponding to the second drive side plate 83 of Example 1. The driving force from the motor is transmitted to the drive transmission gear 1781 by means of the idler wheel 1780. The idler wheel 1780, the drive transmission gear 1781 and the reinforcing member 1798 are supported by the drive shaft 1782 as a fixed shaft so as to be able to rotate coaxially with the rotation axis L2 as the rotation axis and to be able to move in the direction of the rotation axis L2. One end of the drive shaft 1782 is fixed to the second drive side plate 1783, and the other end 1782b is assembled in the hole 1784a of the main frame 1784 and supported thereby. The drive shaft 1782 is arranged so that the rotation axis L2 of the drive transmission gear 1781 is parallel to the rotation axis L1 of the drum 62 in a state in which the cartridge B is mounted on the apparatus main assembly A.

[0442] A compression spring 1785 is provided between the other end portion 1780b of the idler gear 1780 and the second drive side plate 1783, and the idler gear 1780 is urged toward the main frame 1784 (H direction) relative to the direction of the rotation axis L2. A recessed portion 1780a recessed in the direction of the rotation axis L2 is provided at the end portion of the idler gear 1780 opposite to the drive transmission gear 1781, and a protrusion (drive force transmission portion) 1780a1 is provided on the inner side of the recessed portion 1780a.

[0443] At the end of drive transmission gear 1781 opposite idler gear 1780, a protrusion 1781a1, which protrudes in the direction of rotation axis L2, is provided at a position opposite recessed portion 1780a1 of idler gear 1780. Protrusion 1781a1 has a surface 1781e at its upstream end and an inclined surface 1781h at its downstream end in rotation direction I. Surface 1781e is perpendicular to a plane perpendicular to rotation axis L2, and inclined surface 1781h is inclined relative to the plane perpendicular to rotation axis L2. By engaging protrusion 1780a1 of idler gear 1780 with surface 1781e of protrusion 1781a1, driving force is transmitted from idler gear 1780 to drive transmission gear 1781, causing them to rotate integrally in rotation direction I.

[0444] On the other hand, when the drive transmission gear 1781 rotates in the rotation direction I relative to the idler gear 1780, the inclined surface 1781h of the protrusion 1781a1 of the drive transmission gear 1781 comes into contact with the protrusion 1780a1 of the idler gear 1780. As a result, a force tending to separate the idler gear 1780 from the drive transmission gear 1781 acts in the direction of the rotation axis L2, and the idler gear 1780 moves in the J direction against the spring force of the compression spring 1785, with the protrusion 1780a1 riding on the protrusion 1781a1. As a result, this structure prevents the drive force in the rotation direction I from being transmitted from the drive transmission gear 1781 to the idler gear 1780. During installation of the cartridge B in the apparatus main assembly A, the drive transmission gear 1781 can be rotated in the rotation direction I by engaging with the driving side flange 1763, but in this case, due to the above-mentioned structure, the drive force in the rotation direction I is not transmitted from the drive transmission gear 1781 to the idler gear 1780. Therefore, when the user installs box B, there is no need to rotate the motor for driving the idler pulley 1780 or the photosensitive drum 1762, thereby reducing the load required when installing box B in the main component A of the device.

[0445] In addition, the drive transmission gear 1781 is provided with a hole 1781f, and an engaging portion 1781g having a plurality of recessed and protruding shapes is provided on the inner peripheral portion of the hole. The reinforcing member 1798 is provided with an engaging portion 1798b having a plurality of recessed and protruding shapes on its outer peripheral portion and is inserted into the hole 1781f. The engaging portion 1781g of the drive transmission gear 1781 and the engaging portion 1798b of the reinforcing member 1798 are meshed and engaged with each other. The reinforcing member 1798 contacts the drive shaft 1782 and is directly supported by the drive shaft 1782, and the drive transmission gear 1781 is indirectly supported by the drive shaft 1782 by means of the reinforcing member 1798. However, the drive transmission gear 1781 may be configured to be directly supported by the drive shaft 1782.

[0446] However, in the case of manufacturing a drive transmission gear 1781 having a relatively large diameter by resin molding as in the present embodiment, it is preferred that the drive transmission gear 1781 is supported by the drive shaft 1782 by means of a reinforcing member 1798, because this is advantageous from the viewpoints of both molding accuracy and strength. This is because, when manufacturing a gear having a relatively large radial wall thickness (the radial distance from the inner peripheral surface of the hole through which the shaft passes to the root circle of the gear) in a resin molded member, a weight-reducing shape needs to be provided in order to avoid deterioration of the gear molding accuracy caused by shrinkage marks of the resin, etc. When the weight-reducing shape is provided, the strength of the gear may be reduced. Therefore, in the present embodiment, the drive transmission gear 1781 is not directly supported by the drive shaft 1782, but an additional resin-molded reinforcing member 1798 is provided to provide a resin-molded drive transmission gear 1781 that suppresses the above-mentioned deterioration of molding accuracy and can suppress the reduction in strength.

[0447] <Drive transfer operation>

[0448] Next, refer to Figure 54 and Figure 55 , the meshing operation between the drive transmission gear 1781 and the driving side flange 1763 will be described. Figure 54 Part (c), Figure 54 Part (d), Figure 55 Part (a), Figure 55 Part (b) and Figure 55 Part (c) is a schematic cross-sectional view of the meshing engagement portion between the gear portion of the drive transmission gear 1781 and the gear portion of the driving side drum flange 1763. This section is in contact with the meshing pitch circle between the drive transmission gear 1781 and the driving side flange 1763. Figure 54 Part (c), Figure 54 Part (d), Figure 55 Part (a), Figure 55 Part (b) and Figure 55Part (c) shows the state with the passage of time after the drive transmission gear 1781 is started.

[0449] First, in a state where the cartridge B is not mounted to the main assembly A, the drive transmission gear 1781 is urged in the direction H by the compression spring 1785 and abuts against the main frame 1784, as shown in FIG. Figure 54 shown in part (a).

[0450] <Operations after drive startup>

[0451] After the cartridge B is mounted in the main assembly A, the drive transmission gear 1781 is driven by the idler gear 1780 (see Figure 53 ) is driven by a motor (not shown) of the apparatus main assembly A to rotate in the I direction. The driving side flange 1763 receives a driving force from the drive transmission gear 1781 rotating in the I direction and rotates in the K direction.

[0452] like Figure 54 As shown in part (c) of , the following situation will be described, in which, immediately after the drive transmission gear 1781 starts to rotate in the I direction, the force FD is first transmitted through the meshing engagement between the second main component gear portion 1781d of the drive transmission gear 1781 and the second gear portion 1763d of the drive side flange 1763. The second main component gear portion 1781d generates a thrust that pushes the second gear portion 1763d in the H direction. However, the drive side flange 1763 is restricted from moving in the H direction by the rib 1771p (see Figure 51 1763d) and receives a reaction force in the J direction corresponding to the thrust in the H direction. Therefore, the second main assembly gear portion 1781d receives a thrust F5 in the J direction due to the reaction force received from the second gear portion 1763d. This thrust F5 moves the drive transmission gear 1781 in the J direction.

[0453] When the drive transmission gear 1781 moves in the J direction while continuing to rotate further, as shown in FIG. Figure 54 As shown in part (d) of the figure, first gear portion 1763c also meshes with first main assembly gear portion 1781c to transmit driving force FD, and at the same time, thrust F6 is generated in first main assembly gear portion 1781c. Thrust F6 is the same thrust in the J direction as thrust F5 previously received by second main assembly gear portion 1781d through meshing with second gear portion 1763d. As a result, drive transmission gear 1781 further moves in the J direction.

[0454] When the drive transmission gear 1781 is further rotated and moved in the J direction, the second main assembly gear portion 1781d becomes disengaged from the second gear portion 1763d, as shown in FIG. Figure 55On the other hand, the meshing engagement between the first gear portion 1781c and the first gear portion 1763c is maintained, and the first gear portion 1781c receives the thrust F8 in the direction J. At this time, the drive transmission gear 81 transmits the driving force FD only through the engagement between the first main assembly gear portion 1781c and the first gear portion 1763c to rotate the driving side flange 1763.

[0455] When the drive transmission gear 1781 further rotates and moves in the J direction, the second main assembly gear portion 1781d eventually contacts the downstream side (in the I direction) of the tooth surface (contact portion) 1763d2 of the second gear portion 1763d, as shown in FIG. Figure 55 Part (b) and Figure 55 As shown in part (c) of . The surface 1781c1 of the first main component gear portion 1781c and the surface 1763c1 of the first gear portion 1763c maintain contact with each other. That is, the teeth of the first gear portion 1763c are in contact with the first main component gear portion 1781c arranged on the upstream side in the I direction, and the teeth of the second gear portion 1763d are in contact with the second main component gear portion 1781d arranged on the downstream side in the I direction. In addition, the first gear portion 1763c and the second gear portion 1763d are integrally molded by resin, and therefore, the teeth of the first gear portion 1763c are fixed so as not to move (rotate) in the I direction relative to the teeth of the second gear portion 1763d, and the teeth of the second gear portion 1763d are fixed so as not to move (rotate) in the I direction relative to the teeth of the first gear portion 1763c. Therefore, in this state, the first main assembly gear portion 1781c of the drive transmission gear 1781 presses the tooth surface (contact portion) 1763c1 against the tooth surface 1781c1 to rotate the drive-side flange 1763, and the tooth surface 1781d2 of the second main assembly gear portion 1781d of the drive transmission gear 1781 contacts the tooth surface 1763d2, with the tooth surface 1781d2 being sandwiched by the drive-side flange 1763. Then, the movement of the drive transmission gear 1781 in the direction of the rotation axis L1 stops. At this time, the position of the drive transmission gear 1781 in the direction of the rotation axis L1 is the equilibrium position.

[0456] In equilibrium, if Figure 55As shown in part (b) of FIG, force F9, force F10, and force F1 are applied to the drive transmission gear 1781 relative to the direction of the rotation axis L1. Force F9 is the thrust in the J direction received by the first main assembly gear portion 1781c through the meshing engagement force with the first gear portion 1763c, force F10 is the thrust in the H direction received by the second main assembly gear portion 1781d through the meshing engagement force with the second gear portion 6173d, and force F1 is the urging force of the compression spring 1785 received by means of the idler gear 1780. In addition, the driving side flange 1763 receives a force from the drive transmission gear 1781 to abut against the rib 1771p or the side wall 1771m so that it is positioned relative to the direction of the rotation axis L1, and generates a reaction force F11 in the direction of the rotation axis L1 that balances the thrust received from the drive transmission gear 1781. Figure 55 Part (b) shows the driving side flange 1763 positioned so as to contact the rib 1771p. In the equilibrium state, with respect to the direction of the rotation axis L1, if friction is ignored, the forces F9, F10, F1, and F11 are balanced, so that the drive transmission gear 1781 and the driving side flange 1763 are positioned in the direction of the rotation axis L1.

[0457] In addition, if Figure 55 As shown in part (c) of FIG. , in a balanced state, the drive-side flange 1763 is sandwiched (contacted) between the first main assembly gear portion 1781c and the second main assembly gear portion 1781d of the drive transmission gear 1781 in the K direction (rotational direction), so that it is in a state of receiving the following force. Specifically, the tooth surface (contact portion) 1763c1 of the first gear portion 1763c contacts the first main assembly gear portion 1781c arranged upstream in the K direction (first circumferential direction), thereby receiving a driving force FD as a force having a component in a direction that rotates the drive-side flange 1763 in the K direction (predetermined direction). Simultaneously, the tooth surface (contact portion) 1763d2 of the second gear portion 1763d contacts the second main assembly gear portion 1781d arranged downstream in the K direction (first circumferential direction), thereby receiving a restricting force (braking force) FB as a force having a component in a direction that suppresses (limits) the rotation of the drive-side flange 1763 in the K direction. Therefore, it can be said that the first gear portion 1763c is a driving force receiving portion that receives the driving force FD, and the second gear portion 1763d is a restricting force receiving portion that receives the restricting force FB. Figure 55 Part (b) shows the reaction force FF to the driving force FD received by the first main assembly gear portion 1781c and the reaction force FE to the restricting force FB received by the second main assembly gear portion 1781d.

[0458] Furthermore, when the first main assembly gear portion 1781c of the drive transmission gear 1781 first meshes with the first gear portion 1763c of the drive side flange 1763 and transmits the driving force FD immediately after the drive transmission gear 1781 starts to rotate in the I direction, a rotation of the first main assembly gear portion 1781c of the drive transmission gear 1781 is generated. Figure 54 Part (d) or Figure 55 Thereafter, the drive transmission gear 1781 moves toward the driving side in the J direction while transmitting the driving force FD to the first gear portion 1763c in the same manner as described above, and the state changes to Figure 55 Part (b) and Figure 55 Part (c) shows the equilibrium state.

[0459] As described above, in this embodiment as well, the state in which the first gear portion 1763c receives the driving force FD and the second gear portion 1763d receives the limiting force FB is a backlash-free state in which there is no backlash (play) in the direction (I direction) between the driving side flange 1763 and the drive transmission gear 1781. In this manner, the driving side flange 1763 is rotationally driven in the K direction while maintaining the backlash-free state. While the drive is transmitted by engaging with each other in the backlash-free state, drive transmission with high rotational accuracy is possible.

[0460] Furthermore, relative to the direction of rotation axis L1, first gear portion 1763c is positioned closer to protrusion 1763g, the supported portion supported by surfaces 1773e and 1773f, than second gear portion 1763d. In drive-side flange 1763, the force applied to the tooth surface of first gear portion 1763c, which receives driving force FD, is greater than the force applied to the tooth surface of second gear portion 1763d, which receives limiting force FB. Consequently, driving force FD acts to tilt the rotation axis L1 of drum unit 1769, potentially leading to the possibility that drum 1762 may tilt relative to the ideal rotation axis L1. However, as in this embodiment, by positioning first gear portion 1763c, which receives driving force FD, closer to protrusion 1763g, the supported portion, than second gear portion 1763d, it is possible to suppress the tilting of the rotation axis L1 of drum unit 1769 caused by receiving driving force FD.

[0461] <Drive Transmission Structure to Developing Roller 1732>

[0462] Furthermore, the driving force transmission structure to the developing roller 1732 in this embodiment is similar to that described in the other modified examples of Embodiment 1. Figure 44 A driving force transmission structure for transmitting driving force is provided, which is engaged with a coupling member of the apparatus main assembly A so that the driving force is transmitted to the developing roller 532 by means of an input developing coupling member 89.

[0463] Will refer to Figure 56 and 57 Describe the specific structure. Figure 56 Part (a) is a perspective view of a transmission system that drives the developing roller 1732 of the developing unit 1720. Figure 56 Part (b) is a partial perspective view of the developing unit 1720 near the connecting member 1789. Figure 56 Part (c) is a perspective view of box B. Figure 57 It is a partial perspective view of the apparatus main assembly A in the vicinity of the main assembly side coupling member 1799.

[0464] The developing unit 1720 includes a developing coupling member 1789 having a coupling portion 1789a and a gear portion 1789b, an idler wheel 1790 meshing with the gear portion 1789b, an idler wheel 1791 meshing with the idler wheel 1790, and a developing roller gear 1730 fixed to one end portion of the shaft portion of the developing roller 1732 and meshing with the idler wheel 1791, which constitute a developing drive system for driving the developing roller 1732.

[0465] In the main assembly A of the apparatus, a main assembly side coupling member 1799 driven by a motor (not shown) is supported by the first drive side plate 1715. The main assembly side coupling member 1799 is arranged to be movable in the direction of the rotation axis. By rotating the main assembly side coupling member 1799 and the coupling portion 1789a of the developing coupling member 1789 integrally in an engaged state, the driving force is transmitted from the main assembly side coupling member 1799 to the developing coupling member 1789. The driving force is then transmitted from the developing coupling member 1789 to the developing roller 1732 in the order of the idler gears 1790 and 1791 and the developing roller gear 1730.

[0466] In addition, the developing unit 1720 is provided with a colorant moving member (stirring member) (not shown), which stirs or conveys the colorant in the colorant holding container, and the driving force received by the developing connecting member 1789 is transmitted to the colorant moving member by means of another gear to drive the colorant moving member.

[0467] The member driven by the driving force from the developing coupling member 89 is not limited to the above-mentioned developing roller 1732 and the toner moving member (not shown), but it may be some member (for example, a charging member, a sealing member, a cleaning member, etc.) other than the drum unit 1769 included in the cartridge B. Therefore, the member to which the driving force is transmitted from the developing coupling member 1789 (a member connected to the developing coupling member 1789 so as to be able to transmit the driving force) is not limited to the developing roller 1732.

[0468] As described above, the apparatus main assembly A is provided with two systems of driving force output means, that is, the drive transmission gear 1781 and the main assembly side coupling member 1799 as the driving force output means to the cartridge B. Thus, for example, control can be performed such that one of the drive transmission gear 1781 and the main assembly side coupling member 1799 is stopped while the other is driven. As a specific example, control can be performed such that the developing roller 1732 is driven while the drum 1762 is stopped.

[0469] In addition, in cartridge B, the drive-side flange 1763 is not included in the development drive system for driving the developing roller 1732 or in the member connected to the developing coupling member 1789 for transmitting the driving force. Therefore, even if the user rotates the drum 1762 in a state where the cartridge B has been removed from the apparatus main assembly A, the member connected to the developing roller 1732 or the developing coupling member 1789 for drive transmission is prevented from rotating with the rotation of the drum 1762. Therefore, the possibility that the developing roller 1732 or the developing coupling member 1789 and the member connected so as to transmit the driving force are unnecessarily driven, thereby causing toner leakage, etc., can be reduced.

[0470] As described above, in this embodiment, the developing roller 1732 is driven by the driving force input to the developing coupling member 1789, but the driving force can be transmitted from the driving side flange 1763 to the developing roller gear 1730 as in Embodiment 1 to drive the developing roller 1732.

[0471] As described above, according to this embodiment, the same effects as those of the first embodiment can be provided. In addition, the elements of each of the above-described embodiments can be applied to the structure of this embodiment. Specifically, the structure of the first helical teeth (first protrusions) 1763ct of the first gear portion 1763c of the drive side flange 1763 and the second helical teeth (second protrusions) 1763dt of the second gear portion 1763d can be modified to use the helical teeth, spur gear teeth, protrusions, etc. shown in Examples 2, 3, 4, 5, 6, 10, 11, 12, 13, 14, or 16.

[0472] [Example 18]

[0473] This embodiment differs from Example 17 in that an annular elastic member is provided to cover the drive-side flange 1763. Other points are the same as those in Example 17, and detailed descriptions thereof will be omitted. Furthermore, among the elements of this embodiment corresponding to those of Example 1, reference numerals associated with the corresponding elements of Example 1 are given. Regarding these elements, matters not specifically described are the same as those of the corresponding elements of Example 1.

[0474] Figure 61 It is a partial perspective view of the drum unit 1869 near the driving side flange 1863. Figure 62 It is a sectional view of the second gear portion 1863d and the second main assembly gear portion 1881d, and its cross section is perpendicular to the rotation axis L1.

[0475] The driving side flange 1863 has the same shape as the driving side flange 1763 of Embodiment 17. In this embodiment, an elastic ring 1801 (an elastically deformable annular elastic member) is provided to cover the entire periphery or a portion of the periphery of the second gear portion (second unit side gear portion) 1863d.

[0476] Elastic ring 1801 is a thin rubber or sponge, and preferably has a thickness of approximately 0.01 to 1 mm for rubber (e.g., nitrile rubber), and preferably has a thickness of approximately 1 to 6 mm for sponge. Furthermore, it is desirable that the inner diameter of the elastic ring, before being attached to drive-side flange 1863, is approximately 0.5 to 0.9 times the outer diameter of second gear portion 1863d. In this embodiment, the outer diameter of second gear portion 1863d is 20 mm, and the inner diameter of elastic ring 1801 is 14 mm. When the outer diameter of second gear portion 1863d is 20 mm, it is desirable that the inner diameter of elastic ring 1801 be appropriately selected within the range of 10 to 18 mm, which is slightly smaller than 20 mm. If the inner diameter of the elastic ring is greater than 18 mm, it may disengage from second gear portion 1863d. If the inner diameter of the elastic ring is less than 10 mm, the force securing second gear portion 1863d may be too strong, causing deformation of the second gear portion 1863d.

[0477] like Figure 62 As shown, when the cartridge B is mounted to the apparatus main assembly A, the elastic ring 1801 is elastically deformed to follow the shapes of the second helical teeth 1863dt of the second gear portion 1863d and the second helical teeth 1781dt of the drive transmission gear 81, so that the second gear portion 1863d and the second main assembly gear portion 1781d are meshedly engaged with each other by means of the elastic ring 1801. In addition, the first gear portion (first unit side gear portion) 1863c is meshed with the first main assembly gear portion 1781c.

[0478] When the drive transmission gear 1781 rotates in the direction of arrow I, force is transmitted from the second main assembly gear portion 1781d to the second gear portion 1863d via the elastic ring 1801. Therefore, the second gear portion 1863d provides the same function as the second gear portion 1763d of Example 17. That is, when the drive transmission gear 1781 rotates in the direction of arrow I, there is no backlash (play) in the rotation direction (direction I) between the driving side flange 1863 and the drive transmission gear 1781 as in the case of Example 17, that is, a backlash-free state is produced.

[0479] The elastic ring 1801 can be provided with a plurality of protrusions at the inner peripheral portion of the driving side flange 1863, and the plurality of protrusions protrude in the direction toward the rotation axis L1 to fill the plurality of gaps 1863ds of the plurality of second helical teeth 1863dt of the second gear portion 1863d when the box B is not in contact with the drive transmission gear 1781 (for example, before the box B is installed in the main component A of the device).

[0480] In addition, in this embodiment, the elastic ring 1801 is arranged on the outer periphery of the second gear portion 1863d, but the elastic ring 1801 can be arranged on all or part of the outer periphery of the first gear portion 1863c, or on all or part of the outer peripheries of both the second gear portion 1863d and the first gear portion 1863c. In these cases as well, the force is transmitted between the tooth surfaces of each gear by means of the elastic ring 1801. Therefore, the first gear portion 1863c and the second gear portion 1863d provide the same function as the first gear portion 1763c and the second gear portion 1763d of Example 17. In other words, when the drive transmission gear 1781 rotates in the direction of arrow I, there is no tooth backlash (play) between the drive side flange 1863 and the drive transmission gear 1781 in the direction of rotation (direction I), that is, a backlash-free state is produced.

[0481] In addition, the driving side flange 1863 has the same shape as the driving side flange 1763 of Example 17, but the tooth tip shape and the size of the gear can be appropriately changed in consideration of the thickness of the elastic ring 1801.

[0482] As described above, according to this embodiment, the same effects as those of embodiment 17 can be obtained. Furthermore, the elements of each of the above embodiments can be applied to the structure of this embodiment. Specifically, the structure of the first helical teeth (first protrusions) 1863ct of the first gear portion 1863c and the second helical teeth (second protrusions) 1863dt of the second gear portion 1863d of the drive-side flange 1863 can be modified to use the helical teeth, spur gear teeth, protrusions, etc. of embodiments 2, 3, 4, 5, 6, 10, 11, 12, 13, 14, or 16.

[0483] [Example 19]

[0484] This embodiment differs from Example 17 in that the rotation axis (L19, etc.) of the first gear portion (externally toothed gear portion 1902b, etc.) receiving the driving force FD and the rotation axis (L1) of the second gear portion (1963d) receiving the regulating force FB are not coaxial but parallel. Other points are the same as those in Example 17, and detailed descriptions thereof will be omitted. Furthermore, elements of this embodiment corresponding to those of Example 1 are given the same reference numerals as those of the corresponding elements of Example 1. Regarding these elements, matters not specifically described are the same as those of the corresponding elements of Example 1.

[0485] <Drum Unit 1969>

[0486] Figure 63 FIG is a partial perspective view of the drum unit 1969. Figure 63 As shown, the driving side flange 1963 of the drum unit 1969 includes an internal gear portion 1963f centered on the drum rotation axis L1, a second gear portion 1963d, a protrusion 1963g, a small diameter portion 1963e, and a flange portion 1963h. The internal gear portion 1963f is a spur gear. The drum unit 1969 also includes a gear 1902, which will be described in detail below ( Figure 65 The gear 1902 includes an external gear portion 1902b as a first gear portion and an internal gear portion 1902a meshing with the internal gear portion 1902f.

[0487] The protrusion 1963g has a generally cylindrical shape and is arranged to protrude from the internal gear portion 1963f along the drum rotation axis L1 in the direction opposite to the drum 1962 side (downstream side with respect to the J direction). The small diameter portion (cylindrical portion) 1963e has a generally cylindrical shape and is arranged to protrude beyond the internal gear portion 1963f along the drum rotation axis L1 toward the drum 1962 side (downstream side in the H direction). The second gear portion 1963d is a helical tooth having a helical angle α2 as in Example 17 and is arranged on the drum 1962 side (downstream side in the H direction) of the small diameter portion 1963e. The flange portion 1963h has a thin disc shape having a diameter equal to or greater than the diameter of the drum 1962 and is arranged on the drum 1962 side (downstream side in the H direction) of the second gear portion 1963d.

[0488] <Support Structure for Drum Unit 1969>

[0489] Next, refer to Figure 64 、 65 , 66 and 67, the structure for supporting the drum unit 1969 will be described.

[0490] Figure 6419 is a side view (as viewed in a direction perpendicular to the rotation axis L1) of the cleaning unit 1960 to which the drum unit 1969 is mounted. Figure 65 is an exploded perspective view of a driving side portion of the cleaning unit 1960. Figure 66 1960 is a partial cross-sectional view of the cleaning unit 1960 in the vicinity of the driving-side flange 1963 , and the cross section includes the rotation axis L1 . Figure 67 1963f is a partial cross-sectional view of the cleaning unit 1960, which is a cross-sectional view perpendicular to the rotation axis L1 and passing through the internal gear portion 1963f when viewed in the J direction.

[0491] like Figure 64 As shown, a cleaning frame 1960a of the cleaning unit 1960 supports the drum unit 1969. The cleaning frame 1960a of the cleaning unit 1960 includes a frame member 1971 and a drum supporting member 1973. The cleaning frame 1971 is provided with a drum sliding portion 1971g.

[0492] The driving side flange 1963 is rotatably supported by the drum supporting member 1973 in the same manner as in Embodiment 17. Similar to Embodiment 17, when the drive transmission gear 1781 rotates in a predetermined direction after the driving side flange 1963 of the drum unit 1969 engages with the drive transmission gear 1781, the driving side flange 1963 and the drive transmission gear 1781 rotate in conjunction with each other, and as described above, a thrust force in the H direction is generated in the drum unit 1969. By this thrust force, the non-driving side flange 1964 and the drum sliding portion 1971g come into contact with each other, and the movement of the drum unit 1969 in the H direction is restricted.

[0493] like Figure 65 As shown in FIG, the support member 1973 is supported by the frame member 1971. In the frame member 1971, a cylindrical portion 19710b as a positioning portion relative to the support member 1973 is provided so as to protrude toward the drum unit 1969 side. In the support member 1973, a cylindrical portion 19730r as a positioning portion relative to the frame member 1971 is provided so as to protrude toward the drum unit 1969 side.

[0494] The inner peripheral surface 19710d of the cylindrical portion 19710b is formed into an arc shape and is arranged at a position such that the center of the arc is located on the drum rotation axis L1. In addition, the outer peripheral surface 19730b of the cylindrical portion 19730r is formed into an arc shape and is arranged at a position such that the center of the arc is located on the drum rotation axis L1. On the other hand, although the outer peripheral surface 19710c of the cylindrical portion 19710b is formed into the shape of an arc surface, the center axis L19 of the arc surface (coaxial with the rotation axis L19 of the gear 1902) is arranged to be parallel to but not coaxial with the drum rotation axis L1. In other words, the outer peripheral surface 19710c of the cylindrical portion 19710b is arranged at a position eccentric to the inner peripheral surface 19710d.

[0495] The outer peripheral surface 19710c of the cylindrical portion 19710b rotatably supports the gear 1902 about the rotation axis L19. Gear 1902 has a generally cylindrical shape and includes an internally toothed gear portion 1902a located coaxially with the rotation axis L19 of the cylinder and an externally toothed gear portion 1902b located on the outer peripheral side, serving as a first gear portion (first unit-side gear portion). Internally toothed gear portion 1902a has flat teeth, while externally toothed gear portion 1902b has helical teeth with a helix angle α1 and has the same number of teeth as the second gear portion (second unit-side gear portion) 1963d of the drive-side flange 1963. Furthermore, a support portion 1902c is provided on one end of gear 1902, and a cylindrical portion 1902d is provided on the other end. The supporting portion 1902c has a generally cylindrical shape and is provided along the rotation axis L19 so as to protrude beyond the externally toothed gear portion 1902b and the internally toothed gear portion 1902a in a direction away from the drum 1962 (downstream side in the J direction). The cylindrical portion 1902d has a generally cylindrical shape and is provided along the rotation axis L19 so as to protrude beyond the externally toothed gear portion 1902b and the internally toothed gear portion 1902a toward the drum 1962 side (downstream side in the H direction).

[0496] like Figure 66As shown in the embodiment 17, the inner peripheral surface (supported portion) of the supporting portion 1902c is engaged with the outer peripheral surface 19710c of the cylindrical portion 19710b, and the gear 1902 is rotatably supported on the frame member 1971 around the rotation axis L19. In addition, the outer peripheral surface 19730b of the cylindrical portion 19730r is engaged with the inner peripheral surface 19710d of the cylindrical portion 19710b, and the supporting member 1973 is positioned and supported by the frame member 1971. The driving side flange 1963 penetrates the inner peripheral portion of the gear 1902 and is provided on the cleaning frame 1960a. In the driving side flange 1963, the protrusion 1963g is rotatably supported by the supporting member 1973 on the rotation axis L1 as in the case of Example 17.

[0497] In addition, if Figure 67 As shown, internal gear portion 1963f of driving-side flange 1963 is a spur gear and has the same number of teeth as internal gear portion 1902a of gear 1902. Internal gear portion 1902a of gear 1902 is configured to fit into internal gear portion 1963f, and the tooth surfaces of internal gear portion 1902a and internal gear portion 1963f engage with each other in the rotational direction. In other words, internal gear portion 1902a and internal gear portion 1963f mesh with each other to transmit rotational drive force.

[0498] As described above, the outer peripheral surface 19710c of the cylindrical portion 19710b of the frame member 1971 is disposed at an eccentric position relative to the inner peripheral surface 19710d. Therefore, the gear 1902 supported by the outer peripheral surface 19710c is engaged at an eccentric position relative to the drive side flange 1963 supported on the inner peripheral surface 19710d by the support member 1973. That is, the gear 1902 and the drive side flange 1963 are rotatably arranged in a state where the rotation axis L19 and the rotation axis L1 are parallel to each other and are not coaxial, and the rotational drive force can be transmitted to each other. Figure 67 In the figure, the positions of rotation axis L19 and rotation axis L1 are indicated by the intersection of a horizontal dot-dash line extending in the left-right direction and a vertical line extending vertically, and the difference between the horizontal line corresponding to rotation axis L19 and the horizontal line corresponding to rotation axis L1 can be seen. Gear 1902 can also be referred to as a non-coaxial rotating member connected to drive-side flange 1963 to enable transmission of drive force.

[0499] <Transmission of Driving Force to Drum Unit 1969>

[0500] Next, refer to Figure 68 and 69 , the transmission of driving force to the drum unit 1969 will be described. Figure 681781 is a cross-sectional view showing an engaged state between the drum unit 1969 and the drive transmission gear 1781, and its cross section includes the rotation axis L1. Figure 69 1963f is a sectional view showing an engaged state between the drum unit 1969 and the drive transmission gear 1781, taken along a plane which is perpendicular to the rotation axis L1 and passes through the internal gear portion 1963f as viewed in the J direction.

[0501] like Figure 68 As shown, as in Embodiment 17, the second main assembly gear portion 1781d of the drive transmission gear 1781 meshes with the second gear portion 1963d of the driving side flange 1963. In addition, the first main assembly gear portion 1781c of the drive transmission gear 1781 meshes with the externally toothed gear portion (first gear portion) 1902b of the gear 1902, and the internally toothed gear portion 1902a of the gear 1902 engages with the internal gear portion 1963f of the driving side flange 1963.

[0502] like Figure 69 As shown, by the rotation of the drive transmission gear 1781 in the direction of arrow I, the gear 1902 receives the driving force through the meshing engagement between the externally toothed gear portion 1902b and the first main assembly gear portion 1781c, causing the gear 1902 to rotate in the direction of arrow KW about the rotation axis L19. At this time, the internally toothed gear portion 1902a engages with the internal gear portion 1963f of the driving side flange 1963 in the rotational direction, and transmits the driving force to the driving side flange 1963. As a result, the driving side flange 1963 rotates in the direction of arrow K about the rotation axis L1.

[0503] By the rotation of the driving transmission gear 1781 in the direction of arrow I, the externally toothed gear portion 1902b receives the rotation in the direction of arrow H (see FIG. 17). Figure 68 ) thrust. Therefore, if Figure 68 As shown, the gear 1902 moves in the direction of arrow H, the cylindrical portion 1902d abuts against the end surface of the second gear portion 1963d of the driving side flange 1963, and the movement of the gear 1902 in the direction of arrow H is restricted (stopped).

[0504] On the other hand, the drive transmission gear 1781 receives thrust due to meshing with the externally toothed gear portion 1902b, and moves in the direction of arrow J. Then, similarly to Embodiment 17, the second main assembly gear portion 1781d moves to the equilibrium position where it engages with the second gear portion 1963d of the driving side flange 1963, and stops moving in the direction of the rotation axis L1.

[0505] In this balanced state, the external gear portion (first gear portion) 1902b receives the driving force FD from the first main component gear portion 1781c. Gear 1902 can be regarded as a rigid component, and therefore, the driving force FD is transmitted to the driving side flange 1963 by the meshing (engagement) between the internal gear portion 1902a and the internal gear portion 1963f. That is, the driving side flange 1963 is in a state of receiving the driving force FD by means of gear 1902. In addition, the driving side flange 1963 is in a state of receiving the limiting force (braking force) FB from the second main component gear portion 1781d by the second gear portion 1963d. The teeth of the second gear portion 1963d are fixed so as not to move (rotate) in a direction opposite to the direction I relative to the teeth of the first gear portion 1902b. Therefore, the drum unit 1969 (drum 1962, driving side flange 1963 and gear 1902) is driven in a state without tooth clearance. Therefore, even when the structure of this embodiment is used, the same effect as that of Example 17 can be provided.

[0506] Immediately after the drive transmission gear 1781 starts rotating, the driving side flange 1963 can rotate in the K direction due to the engagement between the second gear portion 1963d and the second main assembly gear portion 1781d, and the gear 1902 can rotate in the KW direction due to the engagement between the internal gear portion 1902a and the internal gear portion 1963f. In this case as well, during the movement of the drive transmission gear 1781 in the J direction, the first main assembly gear portion 1781c meshes with the external gear portion 1902b, and eventually reaches the above-mentioned equilibrium state.

[0507] As described above, in this embodiment, the rotation axis L19 of the external gear portion 1902b (first gear portion) and the rotation axis L1 of the second gear portion 1963d are not coaxial with each other but parallel. Then, in a balanced state, the gear 1902 has the following parts (i) to (iii). (i) Input part: at least a portion of the external gear portion 1902b that meshes with the drive transmission gear 1781 (at least a portion of the first gear portion), (ii) Transmission part: the portion of the internal gear portion 1902a that meshes with the internal gear portion 1963f to transmit the driving force to the driving side flange 1963, (iii) Output part: the portion between the input part (i) and the output part (ii). Since parts (i) to (iii) of the gear are substantially rigid bodies in the K direction, they move integrally along the K direction. Therefore, in a balanced state, parts (i) to (iii) of the gear 1902 and the second gear portion 1963d of the drive-side flange 1963 move integrally in the K direction (the direction of rotation about the rotation axis L1). Therefore, forces corresponding to the driving force FD and the limiting force FB act on the drive-side flange 1963, enabling drive without backlash and providing the same effects as those of Example 17. Furthermore, as long as the first gear portion receiving the driving force FD and the second gear portion receiving the limiting force FB can move integrally in the K direction in a balanced state, it can be understood that the first gear portion and the second gear portion do not always need to be integrally fixed to the drive-side flange 1963 as in Examples 1-8.

[0508] Furthermore, this embodiment illustrates an example of a structure in which the rotation axis of the first gear portion receiving the driving force FD and the rotation axis of the second gear portion receiving the limiting force FB are not coaxial. Specifically, the rotation axis of the second gear portion 1963d receiving the limiting force FB is coaxial with the rotation axis L1 of the drive-side flange 1963, while the rotation axis of the first gear portion 1902b receiving the driving force FD is not coaxial with the rotation axis L1 of the drive-side flange 1963. Specifically, the first gear portion 1902b is provided on the gear 1902, which is a non-coaxial rotating member connected to the drive-side flange 1963 to enable transmission of the driving force. However, the structure in which the rotation axis of the first gear portion receiving the driving force FD and the rotation axis of the second gear portion receiving the limiting force FB are not coaxial is not limited to this example.

[0509] As another example, the rotation axis of the first gear portion that receives the driving force FD is coaxial with the rotation axis of the drive-side flange, and the rotation axis of the second gear portion that receives the limiting force FB may not be coaxial with the rotation axis of the drive-side flange. In the case of this structure, specifically, the first gear portion is provided on the drive-side flange, and the second gear portion is provided on a non-coaxial rotating member connected to the drive-side flange for driving force transmission. As a more specific example of this structure, in the drive-side flange 1763 of Example 17, the first gear portion 1763c is used as it is, and the gear 1902 provided with the second gear portion is provided in the same manner as in this embodiment instead of the second gear portion 1763d.

[0510] As a further example, the rotational axis of the first gear portion receiving the driving force FD, the rotational axis of the second gear portion receiving the limiting force FB, and the rotational axis of the drive-side flange may not be coaxial with each other. In this configuration, specifically, the first gear portion is provided on a first non-coaxial rotating member connected to the drive-side flange for driving force transmission, and the second gear portion is provided on a second non-coaxial rotating member connected to the drive-side flange for driving force transmission and rotating non-coaxially with the non-coaxial rotating member. As a more specific example of this configuration, in drive-side flange 1763 of Example 17, a gear 1902 having a first gear portion is provided in place of first gear portion 1763c in the same manner as in this embodiment, and a gear 1902 having a second gear portion is provided in place of second gear portion 1763d in the same manner as in this embodiment.

[0511] The connection structure capable of transmitting the driving force between the drive side flange 1963 and the non-coaxial rotating member (gear 1902) is not limited to the spur gear meshing structure of, for example, the internal gear portion 1902a and the internal gear portion 1963f. For example, the connection structure may enable the driving force to be transmitted through a helical gear or a plurality of protrusions arranged in the circumferential direction. In addition, a non-coaxial driving force transmission coupling such as a cross coupling (described in detail in Modified Example 2 of Example 19) can be used as the connection structure capable of transmitting the driving force between the drive side flange 1963 and the non-coaxial rotating member (gear 1902).

[0512] <Modification Example 1 of Embodiment 19>

[0513] In the above-mentioned embodiment 19, the internal gear portion 1963f of the driving side flange 1963 and the internal gear portion 1902a of the gear 1902 have the same number of teeth and rotate integrally, but in this modified example, the rotation speeds of the driving side flange 1963 and the gear 1902 are different from each other. Figure 70 is an exploded perspective view of a driving side portion of the cleaning unit 1960. Figure 71 : is a sectional view showing an engaged state between the drum unit 1969 and the drive transmission gear 1781 , taken along a cross section which is perpendicular to the rotation axis L1 and passes through the internal gear portion 1963 f as viewed in the J direction.

[0514] Instead of the gear 1902 having the above-described structure, a gear 1903 is provided as a non-coaxial rotating member, and instead of the driving side flange 1963, a driving side flange 1963 is provided. Similar to the above-described structure, the gear 1903 is rotatably supported by the outer peripheral surface 1971c of the cylindrical portion 1971b of the cleaning frame 1971, and the driving side flange 1963 is rotatably supported by the supporting member 1973 through the gear 1903.

[0515] like Figure 71 As shown, the inner tooth portion 1903a of the gear 1903 has a larger structure relative to the first gear portion 1963c of the driving side flange 1963 and is more eccentric than the above structure. Figure 71 , the positions of the rotation axis L19 and the rotation axis L1 are indicated by the intersection of the horizontal dot-dash line and the vertical dot-dash line.

[0516] In the balanced state, at least a portion of the external gear portion 1903b of the gear 1903 that meshes with the drive transmission gear 1781 (at least a portion of the first gear portion) moves integrally with the second gear portion 1963d in the rotational direction about the rotation axis L1. Therefore, the same effects as those of the nineteenth embodiment can be provided.

[0517] In the present embodiment, the first gear portion 1963c of the driving side flange 1963 and the internal gear portion 1903a of the gear 1903 are spur gears, but helical gears may be employed if the structure allows for eccentricity.

[0518] <Modification Example 2 of Embodiment 19>

[0519] A structure using an Oldham joint as a driving force transmission structure between a non-coaxial rotation member and the driving side flange 1963 will be described. Figure 72 FIG is a partial perspective view of the drum unit 1969. Figure 72 As shown, the driving side flange 1963 includes a gear portion 1963d, a protrusion 1963g, a small diameter portion 1963e, and a flange portion 1963h, which are arranged centered on the drum rotation axis L1.

[0520] The small diameter portion 1963e has a generally cylindrical shape and is arranged to protrude from the gear portion 1963c on the side opposite to the drum 1962 (the downstream side in the J direction) along the drum rotation axis L1. The small diameter portion 1963e is provided with a recess 1963r recessed toward the drum 1962 side (the downstream side in the H direction). The side surface portion 1963s of the recess 1963r has a planar shape parallel to the direction of the drum rotation axis L1 and is arranged at equal intervals relative to the drum rotation axis L1 interposed therebetween. In addition, the recess 1963r is provided at two positions symmetrical with respect to the small diameter portion 1963g interposed therebetween in a direction perpendicular to the drum rotation axis L1.

[0521] The projection 1963g has a cylindrical shape and is provided so as to protrude from the small diameter portion 1963e in a direction away from the drum 1962 (downstream in the J direction) along the drum rotation axis L1. The flange portion 1963h has a thin disk shape having a diameter equal to or larger than the diameter of the drum 1962 and is provided on the drum 1962 side (downstream in the H direction) of the gear portion 1963d. The gear portion 1963d has helical teeth with a helical angle of α2 as in Example 17.

[0522] Furthermore, the drum unit 1969 includes a gear 1904 having a gear portion 1904 c as a first gear portion (which will be described in detail later) and a driven coupling 1905 .

[0523] Next, refer to Figure 73 , the structure of the cleaning unit will be described. Figure 73 : is an exploded perspective view of the driving side of the cleaning unit, wherein part (a) is a view as viewed from the driving side toward the non-driving side, and part (b) is a view as viewed from the non-driving side toward the driving side. Figure 73 Part (a) and Figure 73 As shown in part (b) of , the supporting member 1973 is supported by the frame member 1971. The hole 1971d is a positioning portion relative to the supporting member 1973, and is provided on the side surface of the frame member 1971, wherein the hole 1971d is formed in an arc shape, and the center of the arc is provided to be aligned with the position corresponding to the drum rotation axis L1. In addition, the frame member 1971 is provided with a cylindrical portion 1971b protruding downstream along the H direction. The inner peripheral surface 1971c of the cylindrical portion 1971b has an arc shape, and the center line L19 of the arc surface is provided at a position which is not coaxial with the drum rotation axis L1 but parallel thereto. In other words, the hole 1971d is provided at a position eccentric to the inner peripheral surface 1971c.

[0524] Gear 1904, a non-coaxial rotating member, is rotatably supported on inner circumferential surface 1971c of cylindrical portion 1971b. Gear 1904 has a generally cylindrical shape and is provided with a through-hole 1904a, a gear portion 1904c serving as a first gear portion on the outer circumference, and a cylindrical portion 1904d coaxial with the axis of the cylindrical body at its center. Gear portion 1904c has helical teeth with a helix angle α1. Protrusions 1904b are provided to protrude downstream in the H direction from the side surface of gear 1904.

[0525] When the rotation axis of gear 1904 is gear rotation axis L19, side surface portions 1904e and 1904f of protrusion 1904b have a planar shape parallel to gear rotation axis L19 and are positioned at equal intervals across gear rotation axis L19. Furthermore, protrusion 1904b has an arcuate shape that does not protrude beyond the tooth bottom portion of gear portion 1904c in the radial direction relative to rotation axis L1. Furthermore, protrusion 1904b is positioned perpendicular to gear rotation axis 1901 at two locations symmetrical with respect to through-hole 1904a interposed therebetween. Cylindrical portion 1904d protrudes downstream in direction J. Gear 1904 is rotatably supported by frame member 1971 by fitting cylindrical portion 1904d into inner circumferential surface 1971c of cylindrical portion 1971b of frame member 1971.

[0526] The driven coupling 1905 is mounted on the downstream side of the gear 1904 in the H direction. The driven coupling 1905 has a generally cylindrical shape and is provided with a through hole 1905a and a cylindrical portion 1905d coaxially around the cylinder axis. A protrusion 1905b is provided on the downstream side of the cylindrical portion 1905d in the H direction so as to protrude downstream in the H direction. In addition, a recess 1905c is provided on the downstream side of the cylindrical portion 1905d in the J direction and is recessed toward the downstream side in the H direction. The protrusion 1905b has parallel surfaces spaced apart at a distance equal to the distance between the side surface portions 1963s of the recessed portion 1963r, centered on the cylinder axis, and the recessed portion 1905c has parallel surfaces spaced apart at a distance equal to the distance between the side surface portions 1904e, 1904f of the protrusion 1904b, centered on the cylinder axis, and furthermore, the protrusion 1905b and the recessed portion 1905c extend in orthogonal directions passing through the cylinder axis.

[0527] The protrusion 1904b of the gear 1904 is fitted into the recessed portion 1905c of the driven coupling 1905 in the direction of the rotation axis L1 of the cylinder, and the protrusion 1904b is rotated in the direction indicated by the double-headed arrow 190Y (see FIG. Figure 73The portion (b) is movable (slidable) in the recessed portion 1905c. The direction of 190Y is parallel to a plane perpendicular to the rotation axis L1. In addition, the protrusion 1904b can transmit the driving force for rotating the driven coupling 1905 about the rotation axis L1 to the recessed portion 1905c.

[0528] Furthermore, the protrusion 1963g of the driving side flange 1963 penetrates the through hole 1905a of the driven coupling 1905 and the through hole 1904a of the gear 1904. Here, the diameter size of the through hole 1905a and the through hole 1904a is much larger than the outer diameter of the protrusion 1963g.

[0529] Furthermore, protrusion 1905b of driven coupling 1905 fits into recessed portion 1963r of driving-side flange 1963 in the direction of rotation axis L1, and protrusion 1905b is movable (slidable) within recessed portion 1963r in the direction indicated by double-headed arrow 190X. Direction 190X is parallel to a plane perpendicular to rotation axis L1 and is perpendicular to direction 190Y when viewed along rotation axis L1. Furthermore, protrusion 1905b can transmit the driving force for rotating driving-side flange 1963 about rotation axis L1 to recessed portion 1963r.

[0530] As in Embodiment 17, the free end portion of the protrusion 1963g is rotatably supported by the drum supporting member 1973.

[0531] As described above, the inner peripheral surface 1971c of the cylindrical portion 1971b of the frame member 1971 is eccentrically positioned relative to the hole 1971d. Therefore, the gear 1904 supported on the inner peripheral surface 1971c and the driving side flange 1963 supported coaxially with the hole 1971d are rotatably supported at an eccentric position.

[0532] Next, refer to Figure 74 and 75 , the engagement with the drive transmission gear 1781 will be described. Figure 74 1781 is a view showing the drum unit 1969 meshing with the drive transmission gear 1781, and is a view viewed in a direction perpendicular to the rotation axis L1. Figure 75 Part (a) to Figure 75 Part (e) is a sectional view showing the engagement state between the drum unit 1969 and the drive transmission gear 178, and is a sectional view taken along a plane perpendicular to the rotation axis L1 and passing through the protrusion 1904b of the gear 1904 as viewed in the H direction. Figure 75, the position of the rotation axis L19 is represented by the intersection of the horizontal chain line extending left and right and the vertical chain line extending vertically, and on the other hand, for simplicity, the position of the rotation axis L1 is omitted because it is the center of the protrusion 1963g. In addition, Figure 75 The black dots shown on the driven coupling 1905 in FIG. 1 are marks indicating specific portions of the driven coupling 1905 and are described for easy understanding of the rotational phase of the driven coupling 1905 .

[0533] like Figure 74 As shown, the second main assembly gear portion 1781d of the drive transmission gear 1781 is engaged with the second gear portion 1963d of the driving side flange 1963, and the first main assembly gear portion 1781c is engaged with the gear 1904 (first gear portion).

[0534] like Figure 75 Part (a) to Figure 75 As shown in part (e), by the rotation of the drive transmission gear 1781 in the I direction, the driving force is transmitted from the drive transmission gear 1781 to the gear portion 1904c (first gear portion), so that the gear 1904 rotates in the KW direction around the gear rotation axis L19. The driving force of the drive transmission gear 1781 is transmitted to the driving side flange 1963 by means of the driven coupling 1905 engaged with the gear 1904, so that the driving side flange 1963 rotates in the K direction around the rotation axis L1 (see Figure 72 ).

[0535] When the gear 1904 and the drum unit 1969 rotate, the driven coupling 1905 moves in the recessed portion 1963r of the driving side flange 1963 so that the protrusion 1905b (see Figure 74 ) moves in the 190X direction relative to the driving side flange 1963. In addition, by the movement of the protrusion 1904b in the recessed portion 1905c, the gear 1904 moves in the 190Y direction relative to the driven coupling 1905. Thus, the gear 1904 (rotation axis L19) and the driving side flange 1963 (rotation axis L1) can transmit the driving force for rotation between the gear 1904 and the driving side flange 1963 while maintaining an eccentric position (non-coaxial and parallel state).

[0536] Then, through the operation as in Example 19, the drive transmission gear 1781 is moved to the equilibrium position and is in a balanced state. In the balanced state, the drive transmission gear 1781 receives force FB at the second gear portion 1963d and receives a force corresponding to the driving force FD received by the gear portion 1904c (first gear portion) of the gear 1904 at the side surface portion 1963s via the driven coupling 1905. The teeth of the second gear portion 1963d are in a fixed state, so that they cannot move (rotate) in the direction opposite to the direction I relative to the teeth of the first gear portion 1904c. Therefore, a backlash-free state is provided, and the same effects as those of Example 17 can be provided.

[0537] As described above, according to Example 19, Modification Example 1 of Example 19, and Modification Example 2 of Example 19, the same effects as those of Example 17 can be provided. Furthermore, the elements of each of the above-described embodiments can be applied to the structure of this embodiment. Specifically, the structure of the first helical teeth (first protrusions) of the first gear portion and the second helical teeth (second protrusions) of the second gear portion can be modified to the helical gears, spur gears, and / or protrusions described in Examples 2, 3, 4, 5, 6, 10, 11, 12, 13, 14, or 16.

[0538] [Example 20]

[0539] Next, refer to Figure 76 、 77 , 78 and 79, Example 20 will be described below. The difference between this embodiment and Example 17 is that the first gear portion (external tooth portion 2002b) that receives the driving force FD rotates coaxially with the rotation axis L1 of the second gear portion 2063d that receives the force FB only in a part of the area. In other words, in this embodiment, compared with Example 17, it can be said that the movement of the first gear portion (external tooth portion 2002b) is not composed only of rotation around one rotation axis L1. The other points are the same as those in Example 17, and therefore, their detailed description will be omitted. In addition, among the elements of this embodiment, the elements corresponding to the elements of Example 1 are given the figure marks associated with the corresponding elements of Example 1. Regarding these, the matters for which the specific description is omitted are the same as the corresponding constituent elements of Example 1.

[0540] <Drum Unit 2069>

[0541] Figure 76 It is a partial perspective view of the drum unit 2069. Figure 77 It is an exploded perspective view of the driving side of the cleaning unit 2060 and the drum unit 2069. Figure 78 2063f is a cross-sectional view of the driving-side flange 2063 of the cleaning unit 2060 at the position of the gear portion 2063f.

[0542] like Figure 76 As shown, the driving side flange 2063 includes a gear portion 2063f around the drum rotation axis L1, a second gear portion (second unit side gear portion) 2063d, a protrusion 2063g, a small diameter portion 2063e and a flange portion 2063h. The gear portion 2063f has a pulley shape corresponding to a toothed belt.

[0543] The protrusion 2063g has a generally cylindrical shape and is arranged to protrude beyond the gear portion 2063f along the drum rotation axis L1 in a direction away from the drum 2062 side (downstream in the J direction). The small-diameter portion 2063e has a generally cylindrical shape with a diameter equal to or greater than that of the gear portion 2063f and equal to or smaller than that of the second gear portion 2063d. It is positioned closer to the drum 2062 than the gear portion 2063f in the direction of the drum rotation axis L1 (downstream in the H direction). The second gear portion 2063d is a helical gear having a helical angle α2 as in Example 17 and is positioned on the drum 2062 side of the small-diameter portion 2063e (downstream in the H direction). The flange portion 2063h has a thin disc shape with a diameter equal to or greater than that of the drum 2062 and is positioned closer to the drum 2062 than the second gear portion 2063d (downstream in the H direction).

[0544] like Figure 77 As shown, the drum unit 2069 also includes a belt 2002 (see Figure 77 Belt 2002 is provided with an outer tooth portion 2002b serving as a first gear portion (first unit-side gear portion) on its outer periphery, and an inner tooth portion 2002a meshing with gear portion 2063f on its inner periphery. Belt 2002 is an elastic belt-like member. Outer tooth portion 2002b is helical with a helical angle α1.

[0545] Next, refer to Figure 77 and 78 , the structure of the cleaning unit 2060 on the driving side will be described. Figure 77As shown, the support member 2073 is supported by the frame member 2071. The frame member 2071 is provided with a generally cylindrical hole 20710a. The support member 2073 is provided with a generally cylindrical hole 20730a facing the hole 20710a at a position facing the hole 20710a. The pulley 2001 is provided between the hole 20710a and the hole 20730a. The pulley 2001 has a generally cylindrical shape extending in an axial direction parallel to the rotation axis L1. The pulley 2001 is provided with supported portions 2001a and 2001b in the form of generally cylindrical protrusions at opposite ends in a direction parallel to the rotation axis L1, and a tooth portion 2001c in the form of a pulley corresponding to the inner tooth portion 2002a of the belt 2002 is provided on the circumferential surface of the central portion. Furthermore, pulley 2001 is provided with a flange portion 2001d having a larger diameter than that of tooth portion 2001c between supported portion 2001a and tooth portion 2001c. Supported portions 2001a and 2001b are rotatably supported by holes 20710a and 20730a, respectively, so that pulley 2001 can rotate about a rotation axis parallel to rotation axis L1.

[0546] <Support Structure of Drum Unit 2069>

[0547] The structure in which the driving side flange 2063 and the drum 2062 in the drum unit 2069 are supported by the supporting member 2073 and the frame member 2071 is the same as that in Example 19, and therefore its description is omitted. Figure 78 As shown, in the belt 2002 of the drum unit 2069, the inner tooth portion 2002a is supported by the pulley 2001 and the gear portion 2063f of the drive-side flange 2063 and the tooth portion 2001c of the pulley 2001, while the gear portion 2063f of the drive-side flange 2063 is meshed with each other. Furthermore, the belt 2002 is supported by the drive-side flange 2063 and the pulley 2001 with appropriate tension so that the portion not in contact with either the drive-side flange 2063 or the pulley 2001 is not significantly flexed. Furthermore, the belt 2002 can circulate and move by the rotation of the drive-side flange 2063 (gear portion 2063f) and the pulley 2001 (tooth portion 2001c).

[0548] <Transmission of Driving Force to Drum Unit 2069>

[0549] Next, refer to Figure 79 and 80 , the engagement state with the drive transmission gear 1781 will be described. Figure 79 is a sectional view showing an engagement state between the drum unit 2069 and the drive transmission gear 1781, taken along a plane perpendicular to the rotation axis L1 and passing through the belt 2002 as viewed in the J direction, and Figure 8017 is a cross-sectional view showing an engagement state between the drum unit 2069 and the drive transmission gear 1781 , taken along a plane including the rotation axis L1 .

[0550] like Figure 79 As shown, by the rotation of the drive transmission gear 1781 in the direction of arrow I, the outer teeth portion 2002b of the belt 2002 engages with the first main assembly gear portion 1781c and circulates in the direction of arrow KC, which is the direction of circular movement. As the belt 2002 circulates, the gear portion 2063f of the drive-side flange 2063, which engages with the inner teeth portion 2002a of the belt 2002, rotates in the direction of arrow K. At this time, assuming that the portion of the belt 2002 that engages with the inner teeth portion 2002a is the rotating portion 2002R, the rotating portion 2002R rotates in the direction K about the rotation axis L1. Therefore, the circular movement direction KC of the rotating portion 2002R of the belt 2002 is the same as the K direction. Therefore, when the portion of the outer teeth portion 2002b as the first gear portion included in the rotating portion 2002R is the rotating gear portion 2002bR, the rotating gear portion 2002bR rotates coaxially and integrally with the driving side flange 2063 and the second gear portion 2063d about the rotation axis L1. In addition, when the belt 2002 circulates in the KC direction, the pulley 2001 rotates in the direction of arrow V20.

[0551] By the rotation of the drive transmission gear 1781 in the direction of arrow I, the outer tooth portion 2002b receives a thrust in the direction of arrow H by meshing engagement with the first main assembly gear portion 1781c, and the belt 2002 tends to move in the direction of arrow H. However, as Figure 80 As shown, the diameter of the small diameter portion 2063e of the driving side flange 2063 is larger than the diameter of the gear portion 2063f, and therefore, the end surface 2002E of the belt 2002 abuts against the end surface 2063e of the small diameter portion 2063e, so that the movement of the belt 2002 in the direction of arrow H is restricted (stopped).

[0552] On the other hand, the drive transmission gear 1781 receives thrust by meshing engagement with the external teeth portion 2002b and moves in the direction of arrow J. Then, similarly to Embodiment 17, the second main assembly gear portion 1781d moves to a balanced position where it engages with the second gear portion 2063d of the driving-side flange 1963, and movement in the direction of the rotation axis L1 stops. The operation and action of the first gear portion (external teeth portion 2002b) and the second gear portion 2063d from the start of driving of the drive transmission gear 1781 until the drive transmission gear 1781 reaches the balanced position are the same as those in Embodiment 19.

[0553] In this balanced state, the rotating gear portion 2002bR of the outer tooth portion (first gear portion) 2002b receives the driving force FD from the first main component gear portion 1781c. Since the rotating portion 20...

Claims

1. A photosensitive member unit detachably mountable to a main assembly of an image forming apparatus, the image forming apparatus comprising a first main assembly side helical gear portion and a second main assembly side helical gear portion coaxially rotatable, the photosensitive member unit comprising: a photosensitive member rotatable about its rotation axis; a first unit-side helical gear portion, the first unit-side helical gear portion being adapted to mesh with and engage with the first main assembly-side helical gear portion; as well as a second unit-side helical gear portion adapted to engage with the second main assembly-side helical gear portion; The torsion direction of the teeth of the second unit side helical gear part is the same as the torsion direction of the teeth of the first unit side helical gear part. wherein the helix angle of the teeth of the second unit side helical gear portion is greater than the helix angle of the teeth of the first unit side helical gear portion, and The first unit side helical gear portion and the second unit side helical gear portion are rotatable in a state where the first unit side helical gear portion is meshed with the first main assembly side helical gear portion and the second unit side helical gear portion is meshed with the second main assembly side helical gear portion.

Images