Photoconductor unit

Abstract

To develop a photoreceptor unit.SOLUTION: A photoreceptor unit that is attachable to and detachable from a device body of an image forming device comprises a photoreceptor rotatable about a rotation axis, a first gear portion, and a second gear portion having a plurality of teeth. The first gear portion is a helical gear portion with helical teeth twisted in a first circumferential direction. The second gear portion is disposed between the first gear portion and the photoreceptor with respect to the direction of the rotation axis of the photoreceptor. A gap is provided between the first gear portion and the second gear portion with respect to the direction of the rotation axis of the photoreceptor. The plurality of teeth of the second gear portion each comprise: (i) a first projection extending along at least the direction of the rotation axis of the photoreceptor; and (ii) a second projection arranged downstream of at least a portion of the first projection in the first circumferential direction and closer to the first gear portion than at least a portion of the first projection with respect to the direction of the rotation axis of the photoreceptor.SELECTED DRAWING: Figure 120

Description

Technical field

[0001] The present invention relates to a photoreceptor unit and a cartridge that are detachable from an electrophotographic image forming apparatus, and an electrophotographic image forming apparatus using the same.

[0002] An electrophotographic image forming apparatus forms an image on a recording medium using an electrophotographic image forming method. Examples of electrophotographic image forming devices include, for example, electrophotographic copying machines, electrophotographic printers (LED printers, laser beam printers, etc.), facsimile machines, word processors, and the like. [Background technology]

[0003] In an electrophotographic image forming apparatus (hereinafter also simply referred to as an "image forming apparatus"), a toner image is formed on an electrophotographic photoreceptor (photosensitive drum or drum), and the toner image is directly or indirectly transferred to a recording medium. This forms an image on the recording material.

[0004] Generally, such image forming apparatuses require toner (developer) replenishment, maintenance of various members, and the like. Therefore, there is a cartridge-type image forming apparatus that has a structure in which a cartridge is removably attached to the image forming apparatus, and by replacing the cartridge, replenishment of toner, maintenance, etc. can be performed.

[0005] The cartridge has at least one of a drum and a process means, and is removably attached to the main body of the image forming apparatus (apparatus main body). The process means is a means for forming an image, and those that act on the drum mainly include a developing means, a charging means, a transfer means, a static eliminating means, a cleaning means, and the like. Examples of the cartridge include a process cartridge that has a drum and at least one process means and can be integrally attached to and removed from the main body of the apparatus, a drum cartridge that has a drum, a developer cartridge that has a developer means, and the like. According to such a cartridge system, it becomes possible to easily perform toner replenishment and maintenance of the image forming apparatus.

[0006] As configurations for transmitting driving force from the device main body to the cartridge, there are those that use gears as shown in Patent Document 1, and those that use couplings as shown in Patent Document 2. [Prior art documents] [Patent document]

[0007] [Patent Document 1] Japanese Patent Application Publication No. 63-4252 [Patent Document 2] Japanese Patent Application Publication No. 8-328449 [Summary of the invention] [Problem to be solved by the invention]

[0008] The present invention (this disclosure) aims to develop a photoreceptor unit, a cartridge, or an electrophotographic image forming apparatus. [Means to solve the problem]

[0009] The present invention (present disclosure) provides at least a photoconductor unit that is removably attachable to the main body of an image forming apparatus, and includes a photoconductor that is rotatable around a rotation axis, a first gear section, and a plurality of teeth. 2 gear parts, the first gear part has oblique teeth twisted in a first circumferential direction centering on the rotation axis of the photoreceptor as it moves away from the photoreceptor along the rotation axis of the photoreceptor. the second gear part is disposed between the first gear part and the photoreceptor with respect to the direction of the rotation axis of the photoreceptor, and with respect to the direction of the rotation axis of the photoreceptor, A gap is provided between the first gear part and the second gear part, and the plurality of teeth of the second gear part include (i) a first protrusion extending at least in the direction of the rotation axis of the photoreceptor; (ii) downstream of at least a portion of the first protrusion in the first circumferential direction and further downstream of at least a portion of the first protrusion in the direction of the rotational axis of the photoreceptor; Disclosed is a photoreceptor unit characterized in that the photoreceptor unit includes a tooth provided with a second protrusion disposed near the first gear portion.

Effect of the invention

[0010] According to the present invention (this disclosure), a photoreceptor unit, a cartridge, or an electrophotographic image forming apparatus can be developed. [Brief explanation of drawings]

[0011]

Figure 1

Figure 2

[0012] [Example 1] <Overall configuration of image forming apparatus> FIG. 2 is a cross-sectional view of the image forming apparatus 100 as an electrophotographic image forming apparatus, and the cross section is perpendicular to the rotation axis L1 of the photosensitive drum 62, which will be described later. The image forming apparatus 100 is a laser beam printer using electrophotographic technology, and a cartridge B including a photosensitive drum 62 is removably attached to the main body A of the apparatus. In other words, the portion of the image forming apparatus 100 excluding the cartridge B is the apparatus main body A. When the cartridge B is installed in the apparatus main body A, it is possible to form an image on a recording medium (sheet material) PA such as paper.

[0013] <Device main body configuration> The apparatus main body A includes an exposure device (laser scanner unit) 3 and a sheet tray 4 that stores sheet materials PA. Further, the apparatus main body A includes a pickup roller 5a, a pair of conveyance rollers 5b, a transfer guide 6, a transfer roller 7, a conveyance guide 8, a fixing device 9, a pair of discharge rollers 10, and a discharge tray along the conveyance direction D of the sheet material PA. Has 11. The fixing device 9 includes a heating roller 9a and a pressure roller 9b.

[0014] <Cartridge configuration> Next, the overall configuration of cartridge B will be explained using FIGS. 3, 4, 5, 6, and 7. FIG. 3 is a sectional view of the cartridge B, and the cross section is perpendicular to the rotation axis L1 of the photosensitive drum 62, which will be described later. 4 and 5 are exploded perspective views illustrating the structure of cartridge B. FIG. 6(a) is an exploded perspective view illustrating the configuration of the drum unit 69. FIG. 6(b) is an exploded perspective view illustrating the configuration of the cleaning unit. FIG. 7 is a cross-sectional view of a drive unit that transmits drive from the apparatus main body A to the cartridge B of the image forming apparatus. Note that in this embodiment, descriptions of screws and the like used to connect each component will be omitted.

[0015] Cartridge B is a process cartridge, and mainly includes an electrophotographic photoreceptor and process means that act on the electrophotographic photoreceptor. The process means are a charging means, a developing means, and a cleaning means, which will be described later. Cartridge B mainly has a structure including a cleaning unit (drum unit) 60 and a developing unit 20, and the electrophotographic photoreceptor and process means are provided in the cleaning unit 60 or the developing unit 20.

[0016] Note that the longitudinal direction of the drum 62 is parallel to the direction of the rotation axis L1 of the drum 62 (rotation axis direction). The side of the drum 62 to which the driving force is transmitted from the device main body A in the direction of its rotational axis is called the drive side, and the opposite side is called the non-drive side. Furthermore, the direction from the non-drive side to the drive side along the rotation axis L1 of the drum 62 (parallel to the rotation axis L1) is defined as the J direction, and the direction from the drive side toward the non-drive side is defined as the H direction. Furthermore, when defining the J direction and the H direction in the apparatus main body A, they are defined to match the J direction and the H direction defined when the cartridge B is installed in the apparatus main body A.

[0017] <Cleaning unit (drum unit)> As shown in FIG. 3, 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 that supports these. The cleaning frame (drum frame) 60a includes a frame member 71 and a drum bearing member 73.

[0018] As shown in FIG. 6(a), the photosensitive drum 62, which is a rotating body, is a cylindrical electrophotographic photosensitive member, and is made of an aluminum cylinder with a photosensitive layer coated on its outer peripheral surface. A driving side flange (driving force receiving member) 63 is fixed to the driving side (one end side) of the drum 62, and a non-driving side flange 64 is fixed to the non-driving side (other end side) of the drum 62 by caulking. A unit in which the drum 62, the driving side flange 63, and the non-driving side flange 64 are integrated in this way (that is, a unit that can rotate integrally with the drum 62) is called a drum unit 69.

[0019] Generally, the cleaning unit 60 is sometimes called a drum unit, but in this case, when the contents of the cartridge B are roughly classified and recognized, the drum 62 is used as a pair with the developing unit 20 having a developing means. This is the name when the entire cleaning unit 60 is recognized as a unit with Therefore, the drum unit as a name for the cleaning unit 60 as a whole is a different concept from the drum unit 69 (a unit that can rotate integrally with the drum 62) in this embodiment. In the following description, the drum unit refers to a unit that can rotate integrally with the drum 62.

[0020] The drum 62, the drive side flange 63, and the non-drive side flange 64 rotate integrally around the rotation axis L1 of the drum. That is, the respective rotational axes of the driving side flange 63, the non-driving side flange 64, and the drum unit 69 are coaxial with the rotational axis L1 of the drum 62. Therefore, hereinafter, the rotation axes of the drum 62, drive side flange 63, non-drive side flange 64, and drum unit 69 in the assembled drum unit 69 will all be referred to as the rotation axis L1.

[0021] Further, the driving side flange 63 and the non-driving side flange 64 are also integrally fixed in the direction of the rotation axis L1. The driving side flange 63 and the non-driving side flange 64 are members made of resin. The drive side flange 63 includes a first gear portion 63c and a second gear portion 63d, which will be described in detail later.

[0022] As shown in FIG. 6(b), the drum unit 69 is rotatably supported by the drum frame 60a (frame member 71 and drum bearing member 73) about the rotation axis L1. Specifically, the drive side flange 63 is provided with a hole 63g coaxial with the rotation axis L1, and a shaft member 86 press-fitted into the drum bearing member 73 is inserted into the hole 63g. Possibly supported. The non-drive side flange 64 has a hole (not shown) that is coaxial with the rotation axis L1, and a shaft member 78 press-fitted into the hole 71c of the frame member 71 is inserted into this hole. is rotatably supported. In this way, the non-drive side flange 64 and the drive side flange 63 are bearing parts rotatably supported by the shaft members 86 and 78.

[0023] Further, as shown in FIG. 7, the second gear part 63d of the drive side flange 63 has a protrusion part 63d1 that protrudes in the H direction on the end face on the downstream side in the H direction, and A protrusion 63f protruding in the J direction is provided on the end face. Further, the frame member 71 includes a rib 71p and a side wall 71m that are provided to extend in a direction perpendicular 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 fitted with a clearance fit between the rib 71p and the side wall 71m. Therefore, there may be cases where the protrusion 63d1 contacts the side surface of the rib 71p and cases where the protrusion 63f contacts the side surface of the side wall 71m, but the fit play (gap) is extremely small (about 150 μm at maximum). It can be said that they are positioned at substantially the same position in both cases. In this way, it can be said that the drum unit 69 including the drive side flange 63 is positioned with respect to the drum frame 60a in the direction of the rotation axis L1 by the rib 71p or the side wall 71m.

[0024] In this embodiment, the longitudinal direction of the cartridge B, the drum frame 60a, and the frame member 71 is parallel to the direction of the rotational axis L1 of the drum 62.

[0025] Further, as shown in FIG. 3, in the cleaning unit 60, a charging roller (charging member) 66 as a charging means and a cleaning member 77 as a cleaning means are arranged in contact with the outer peripheral surface of the drum 62, respectively. The cleaning member 77 includes a rubber blade 77a that is a blade-shaped elastic member made of rubber as an elastic material, and a support member 77b that supports the rubber blade 77a. The rubber blade 77a is in contact with the drum 62 in a counter direction to the rotation direction of the drum 62. That is, the rubber blade 77a is in contact with the drum 62 such that its tip faces upstream in the rotational direction of the drum 62. The waste toner removed from the surface of the drum 62 by the cleaning member 77 is accommodated (stored) in a waste toner chamber 71b formed by the frame member 71 and the cleaning member 77. A sheet 65 for suppressing leakage of waste toner from the gap between the frame member 71 and the drum 62 is attached to the edge of the frame member 71 so as to come into contact with the drum 62.

[0026] The charging roller 66 is rotatably supported at both ends in the rotation axis direction by charging roller bearings 67 supported by the frame member 71. The rotational axis of the charging roller 66 is approximately parallel to the rotational axis L1 of the drum 62. The charging roller 66 is pressed against the drum 62 by a charging roller bearing 67 being pressed toward the drum 62 by an urging member 68. The charging roller 66 rotates as the drum 62 rotates.

[0027] <Developing unit> As shown in FIG. 3, the developing unit 20 includes a developing roller 32, a magnet roller 34, a developing blade 42, a conveyance member 43, a developing frame 20a that supports these, and the like. The developing frame 20a includes a developing container 23, a bottom member 22, a bearing member 24 (see FIG. 5), a bearing member 37 (see FIG. 4), a developing side cover 26 (see FIG. 4), and a developing side cover 27 (see FIG. 5). ). The developing unit 20 has a toner supply chamber 28 and a toner chamber 29 formed therein by a developing container 23 and a bottom member 22.

[0028] As shown in FIGS. 4 and 5, within the toner supply chamber 28, the developing roller 32 is rotatably supported by a bearing member 24 and a bearing member 37 at both ends in the rotational axis direction. The bearing member 24 and the bearing member 37 are attached to the developer container 23. A developing roller (developing member) 32 serving as a developing means is a cylindrical member, and a magnet roller 34 is disposed inside it. A developing blade 42 that defines (regulates) the thickness of the toner (toner layer) carried on the surface of the developing roller 32 is arranged.

[0029] Spacing members 38 are attached to both ends of the developing roller 32 in the direction of its rotational axis, and when the spacing members 38 come into contact with the surface of the drum 62, the surface of the developing roller 32 is fixed to the surface of the drum 62. determining the distance. Specifically, the distance is determined so that a small gap is formed between the surface of the developing roller 32 and the surface of the drum 62.

[0030] Further, as shown in FIG. 3, a sheet 33 for preventing toner from leaking from the gap between the developing frame 20a and the developing roller 32 is placed at the edge of the bottom member 22 so as to come into contact with the developing roller 32. is attached to. Further, within the toner chamber 29, a conveying member (stirring member) 43 is rotatably provided. By rotating, the conveying member 43 stirs the toner contained in the toner chamber 29 and conveys the toner from the toner chamber 29 to the toner supply chamber 28.

[0031] <Combination of cleaning unit and developing unit> Cartridge B is assembled by combining the cleaning unit 60 and the developing unit 20. As shown in FIGS. 4 and 5, first, the center of the first supporting boss 26a of the developing container 23 is connected to the first hanging hole 71i on the driving side of the frame member 71, and the developing area is connected to the second hanging hole 71j on the non-driving side. Align the center of the second support boss 27a. Then, by moving the developing unit 20 in the direction of arrow G, the first developing support boss 26a and the second developing supporting boss 27a fit into the first hanging hole 71i and the second hanging hole 71j. Thereafter, by assembling the drum bearing member 73 to the cleaning unit 60, detachment of the developing unit 20 from the cleaning unit 60 is restricted. Thereby, the developing unit 20 is movably connected to the cleaning unit 60. Specifically, the developing unit 20 is rotatably (rotatably) connected to the cleaning unit 60 around the first developing support boss 26a and the second developing supporting boss 27a.

[0032] Further, as shown in FIG. 4, the first end 46Rb of the drive side spring (biasing member) 46R is fixed to the surface 26b of the developing side cover 26, and the second end 46Ra is fixed to the frame member 71 of the cleaning unit 60. touches surface 71k. Further, as shown in FIG. 5, the first end 46Lb of the non-drive side spring (biasing member) 46L is fixed to the surface 27b of the developing side cover 27, and the second end 46La is fixed to the surface 71l of the frame member 71. comes into contact with. Non-drive side spring 46L and drive side spring 46R are compression springs. The biasing force of these springs generates a biasing force between the developing frame 20a and the cleaning frame 60a so as to press the developing roller 32 toward the drum 62. As a result, as described above, the spacing member 38 is pressed against the surface of the drum 62, and is held with a predetermined gap formed between the surface of the developing roller 32 and the surface of the drum 62.

[0033] <Image formation process> Next, the image forming process will be explained. A control unit (not shown) receives a print command signal sent from a host computer or the like, and generates a print start signal based on the print command signal, thereby starting the image forming process.

[0034] When the image forming process starts, first, the drum 62 is driven to rotate in the direction of arrow R (see FIGS. 2 and 3) at a predetermined circumferential speed (process speed). A charging bias voltage is applied to the charging roller 66, and the surface (outer peripheral surface) of the drum 62 is charged substantially uniformly. Furthermore, as shown in FIG. 2, the exposure device (exposure means) 3 emits laser light L according to image information to be printed. The laser light L passes through a laser opening 71h provided in the frame member 71 of the cartridge B, and is irradiated onto the surface of the drum 62 charged by the charging roller 66, so that the surface of the drum 62 is scanned by the laser light L. As a result, an electrostatic latent image corresponding to the image information is formed on the photosensitive layer on the surface of the drum 62.

[0035] On the other hand, as shown in FIG. 3, in the developing unit 20, the toner (developer) T in the toner chamber 29 is stirred and conveyed by the rotation of the conveying member 43, and sent to the toner supply chamber 28. The toner T is carried on the surface of the developing roller 32 by the magnetic force of the magnet roller (fixed magnet) 34. The developing roller 32 is a developer carrier that carries toner T on its surface, and visualizes (develops) the electrostatic latent image formed on the drum 62 described above with the toner. The toner T is triboelectrically charged by the developing blade 42. Further, the developing blade 42 regulates the thickness of the layer of the toner T (layer thickness) on the peripheral surface of the developing roller 32 to a desired thickness. The toner T carried on the surface of the developing roller 32 is supplied to and adheres to the area of ​​the drum 62 corresponding to the electrostatic latent image. As a result, the electrostatic latent image on the drum 62 is visualized (developed) as a toner image. The drum 62 can be said to be an image carrier that carries an electrostatic latent image or a toner image (developer image) on its surface.

[0036] In addition, as shown in Fig. 2, in synchronization with the output timing of the laser beam L, the sheet material PA stored in the sheet tray 4 at the bottom of the apparatus main body A is moved by the pickup roller 5a and the pair of transport rollers 5b into the apparatus main body. It is sent to the conveyance path in A. Thereafter, the sheet material PA is guided by the transfer guide 6 and conveyed to the transfer nip between the drum 62 and the transfer roller (transfer means) 7. In this transfer nip, the toner image formed on the drum 62 is transferred onto the sheet material PA.

[0037] The sheet material PA, on which the toner image has been transferred after passing through the transfer nip, is guided by a conveyance guide 8 and conveyed to a fixing device (fixing means) 9. Then, the sheet material PA passes through the fixing nip between the heating roller 9a and the pressure roller 9b of the fixing device 9. In this fixing nip, the sheet material PA is pressurized and heated to fuse and fix the toner image to the sheet material PA. The sheet material PA that has passed through the fixing nip is conveyed to a pair of discharge rollers 10 and discharged onto a discharge tray 11.

[0038] On the other hand, as shown in FIG. 3, the surface of the drum 62 after passing through the transfer nip comes into contact with a cleaning blade 77, and the toner remaining on the surface of the drum 62 is removed, and the drum 62 can be used again for the above-described image forming process. It becomes like this. The toner removed from the drum 62 by the cleaning blade 77 is stored in the waste toner chamber 71b of the cleaning unit 60 as waste toner.

[0039] In this 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 means that act on the drum 62.

[0040] <Cartridge installation and removal> Next, the attachment of the cartridge B to the apparatus main body A will be specifically explained using FIGS. 8, 9, and 10. FIG. 8(a) is a sectional view of the drive side of the device main body A with the door 13 open, and FIG. 8(b) is a sectional view of the non-drive side of the device main body A with the door 13 open. It is. The cross sections shown in FIGS. 8(a) and 8(b) are cross sections perpendicular to the rotation axis L1. FIG. 9 is a diagram for explaining the positioning of the cartridge B in the longitudinal direction (direction of the rotation axis L1), in which the fitting part 15j of the apparatus main body A is positioned on a horizontal plane parallel to the rotation axis L1 (the installation surface of the apparatus main body A). FIG. FIG. 9(a) shows a state immediately before the cartridge B is fitted into the fitting portion 15j, and FIG. 9(b) shows a state where the cartridge B is fitted into the fitting portion 15j. FIG. 10(a) is a sectional view of the drive side of the device main body A with the door 13 closed, and FIG. 10(b) is a sectional view of the non-drive side of the device main body A with the door 13 closed. It is. The cross sections shown in FIGS. 10(a) and 10(b) are cross sections perpendicular to the rotation axis L1.

[0041] First, we will explain how to install cartridge B into device main body A. The apparatus main body A is provided with a first driving side plate 15 and a non-driving side plate 16 so as to sandwich the cartridge B attached to the apparatus main body A in the direction of the rotation axis L1. Furthermore, a door 13 for opening and closing the insertion port 17 is rotatably attached to the device main body A. The first drive-side side plate 15 has an upper guide rail 15g and a lower guide rail 15h that guide the cartridge B when the cartridge B is installed and removed. The non-drive side plate 16 has an upper guide rail 16d and a lower guide rail 16e that guide the cartridge B when the cartridge B is attached and removed. Further, the drum bearing member 73 of the cartridge B is provided with a guided portion 73g and a rotation stopping portion 73c, and the frame member 71 has a positioning portion 71d and a rotation stopping portion 71g. Therefore, the guided portion 73g and the rotation stopper 73c are arranged on the drive side of the cartridge B, and the guided portion 73g and the rotation stopper 73c are arranged on the non-drive side of the cartridge B, respectively.

[0042] When the door 13 of the device main body A is opened and the insertion slot 17 formed between the first drive side plate 15 and the non-drive side plate 16 is open, cartridge B is inserted into the device main body through the insertion slot 17. It can be inserted into or taken out from A. At this time, by moving the cartridge B in a direction substantially perpendicular to the rotational axis L1 of the drum 62, the cartridge B can be inserted into, mounted on, and removed from the apparatus main body A. In other words, the mounting direction M of the cartridge B into the device main body A (see Figure 9(a)) and the removal direction from the device main body A (opposite direction to the mounting direction M) are directions substantially perpendicular to the rotation axis L1. It is. Since the rotational axis L1 of the cartridge B installed in the device main body A is parallel to the rotational axis L2 of the drive transmission gear 81, the installation direction M of the cartridge B into the device main body A and from the device main body A It can also be said that the removal direction is substantially orthogonal to the rotational axis L2. Further, when the cartridge B is attached to or removed from the apparatus main body A, the drum unit 69 moves integrally with the cartridge B relative to the apparatus main body A, and is attached to or removed from the apparatus main body A. . Therefore, the direction in which the drum unit 69 is attached to and removed from the apparatus main body A is the same as the direction M in which the cartridge B is attached to and removed from the apparatus main body A, respectively.

[0043] <Cartridge installation and positioning> When the cartridge B is inserted into the main body A of the apparatus through the cartridge insertion port 17, the guided portion 73g and rotation stopper portion 73c on the driving side of the cartridge B are connected to the upper guide rail 15g and the guide rail 15h. Each will be guided. The positioning portion 71d and the rotation stopping portion 71g on the non-driven side of the cartridge B are guided by the upper guide rail 16d and the lower guide rail 16e. By thus inserting the cartridge B while being guided by each guide rail of the apparatus main body A, the installation of the cartridge B into the apparatus main body A is finally completed.

[0044] As shown in FIGS. 9(a) and 9(b), the drum bearing member 73 serves as a positioned portion (axially positioned portion) that is positioned relative to the apparatus main body A in the direction of the rotational axis L1. It has a fitted portion 73h. The fitted portion 73h has a concave shape (or groove shape or slit shape) recessed in the mounting direction M (direction perpendicular to the rotational axis L1). On the other hand, the first drive-side side plate 15 of the device main body A has a fitting portion 15j that can fit with the fitted portion 73h. The fitting portion 15j has a convex shape protruding in a direction opposite to the mounting direction MD.

[0045] In the process of inserting the cartridge B into the main body A of the apparatus, as shown in FIG. (longitudinal direction) is determined. Note that the fitted portion 73h and the fitted portion 15j are fitted with a clearance, but the fitting play (gap) is set to be extremely small (about 150 μm at the maximum). Therefore, regardless of whether the fitted portion 73h abuts against the fitting portion 15j in the H direction or the J direction, it can be said that the cartridge B is positioned at substantially the same position in the direction of the rotational axis L1.

[0046] In addition, as shown in FIGS. 8(a), 8(b), 10(a), and 10(b), the first drive-side side plate 15 includes a positioning portion 15a, a positioning portion 15b, and a rotation stop portion 15c. The non-drive side plate 16 has a positioning portion 16a, a positioning portion 16b, and a rotation stop portion 16c. Cartridge pressing members 1 and 2 are attached to the door 13 at both ends in the direction of the rotation axis of the door 13 so as to be movable (rotatable) relative to the door 13. Further, pressure springs 19 and 21 are attached to the first driving side plate 15 and the non-driving side plate 16, respectively.

[0047] Further, as shown in FIG. 3, the drum bearing member 73 of the cartridge B has a pressed portion (biasing force receiving portion) 73e, and the frame member 71 has a pressed portion (biasing force receiving portion) 71n. . The pressed portions 73e and 71n are provided in concave portions disposed on the drive side and non-drive side of the cartridge B, respectively.

[0048] As shown in FIGS. 10(a) and 10(b), 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. The cartridge pressing members 1 and 2 then come into contact with the pressed parts 73e and 71n, and press the pressed parts 73e and 71n by the biasing forces of the pressing springs 19 and 21.

[0049] As a result, on the drive side, the positioned portion 73g of the cartridge B comes into contact with the positioning portion 15a and the positioning portion 15b of the apparatus main body A, and the rotation stopper 73c comes into contact with the rotation stop portion 15c of the apparatus main body A. This restricts the positioning of the drive side portion of the drum frame 60a of the cartridge B in the direction orthogonal to the rotation axis L1 and the rotation around the axis parallel to the rotation axis L1. Furthermore, on the non-driven side, the positioned portion 71d of the cartridge B contacts the positioning portions 16a, 16b of the apparatus main body A, and the rotation stopper portion 71g contacts the rotation stop portion 16c of the apparatus main body A. This restricts the positioning of the non-drive side portion of the drum frame 60a of the cartridge B in a direction perpendicular to the rotational axis L1 and the rotation around an axis parallel to the rotational axis L1.

[0050] By positioning the drum frame 60a of the cartridge B with respect to the apparatus main body A in this manner, the drum unit 69 positioned relative to the drum frame 60a is also indirectly positioned with respect to the apparatus main body A.

[0051] <Drive transmission to drum unit> Next, a configuration for transmitting drive from the apparatus main body A to the drum unit 69 and the drum 62 will be described. FIG. 1 is a perspective view of a portion where drive is transmitted from the apparatus main body A to the drum unit 69. FIG. 11 is an exploded perspective view showing the support structure of the drive transmission gear 81 of the apparatus main body A. FIG. 12 is a perspective view showing the drive transmission section of the apparatus main body A. FIG. 13(a) is a diagram schematically showing the drive transmission gear 81 of the apparatus main body A. FIG. 13(b) is a diagram schematically showing the drive side flange 63 of the cartridge B. FIG. Note that in FIGS. 13(a) and 13(b), the ridge lines at the tips of the gear teeth are shown. FIG. 14 is a diagram schematically showing a drive transmission configuration from the drive transmission gear 81 of the apparatus main body A to the drive side flange 63 to the cartridge B.

[0052] <Drive configuration on the device main body side> As shown in FIG. 11, the device main body A includes a motor (not shown), an idler gear 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 from the motor is transmitted from idler gear 80 to drive transmission gear 81. The idler gear 80 and the drive transmission gear 81 are supported by a drive shaft 82 so as to be rotatable coaxially with each other and movable in the rotation axis direction. The drive shaft 82 has one end 82a fixed to a hole 83a in the second drive side plate 83, and the other end 82b supported in a hole 84a in the main frame 84. The drive shaft 82 is provided so that the rotation axis of the drive transmission gear 81 is parallel to the rotation axis L1 of the drum 62 when the cartridge B is attached to the apparatus main body A.

[0053] Further, a compression spring 85 is provided between the other end 80b of the idler gear 80 and the second drive side plate 83, and the idler gear 80 is biased in the H direction in the rotational axis direction. As mentioned above, the J direction and H direction in the apparatus main body A are defined to match the J direction and H direction of the cartridge B installed in the apparatus main body A. As a result, as shown in FIG. 11, 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 the opposite direction.

[0054] One end 80a of the idler gear 80 is provided with a recess 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 that protrudes in the direction of the rotational axis at a location facing the recess 80a1 of the idler gear 80. By engaging the recess 80a1 of the idler gear 80 and the protrusion 81a of the drive transmission gear 81, driving force is transmitted from the idler gear 80 to the drive transmission gear 81, and the gears rotate integrally. Note that the unevenness relationship between the recess 80a1 and the protrusion 81a1 may be reversed.

[0055] As will be described later, the drive transmission gear 81 meshes with the drive side flange 63 of the cartridge B to transmit the driving force. As shown in FIG. 1, during the image forming process described above, the initial operation after cartridge B is installed, and the preparatory operation for the image forming process (collectively referred to as "during driving"), the drive transmission gear 81 rotates in the I direction, and the drive side flange 63 rotates in the K direction. In other words, the drive direction (rotation direction) of the drive transmission gear 81 while being driven is the I direction, and the drive direction (rotation direction) of the drive side flange 63 while being driven is the K direction. Note that when looking at the drive transmission gear 81 and the drive side flange 63 from the drive side to the non-drive side along the H direction, the I direction is clockwise, and the K direction is counterclockwise.

[0056] <Drive transmission gear 81> As shown in FIGS. 1, 12, and 13(a), the drive transmission gear 81 includes a first main body gear portion (first main body side gear portion, first main body side helical gear portion) as a helical gear portion. 81c and a second main body gear part (second main body side gear part, second main body side bevel gear part) 81d are provided coaxially. The first main body gear portion 81c is disposed on the downstream side in the H direction (upstream in the J direction) than the second main body gear portion 81d. The first body gear portion 81c includes a plurality of first body diagonal teeth 81ct, and the second body gear portion 81d includes a plurality of second body diagonal teeth 81dt. Note that both the first main body bevel tooth 81ct and the second main body bevel tooth 81dt are teeth with an involute tooth profile. The first main body gear portion 81c and the second main body gear portion 81d are integrally molded with resin and rotate integrally. Further, the twisting directions of the first main body gear portion 81c and the second main body gear portion 81d are the same direction, and the tooth surfaces are twisted in such a manner that the tooth surfaces shift toward the I direction as they move toward the J direction. Further, as shown in FIG. 13(a), the torsion angle α2 of the second main body gear portion 81d is larger than the torsion angle α1 of the first main body gear portion 81c (that is, α1<α2 is satisfied). Further, the first main body gear portion 81c and the second main body gear portion 81d have the same number of teeth.

[0057] <Drive side flange 63> On the other hand, as shown in FIGS. 1, 6(b), and 13(b), the drive side flange 63 has a first gear portion (a first unit side gear portion, a first unit side oblique A toothed gear part, first helical gear part) 63c and a second gear part (second unit side gear part, second unit side helical gear part, second helical gear part) 63d are coaxially provided. The first gear section 63c is arranged downstream of the second gear section 63d in the H direction (upstream in the J direction). That is, the first gear portion 63c is disposed between the second gear portion 63d and the drum 62 in the direction of the rotation axis L1. The first gear part 63c includes a plurality of first oblique teeth (first protrusions) 63ct arranged at different positions in the circumferential direction around the rotation axis L1, and the second gear part 63d has the rotation axis L1 as the center. It includes a plurality of second oblique teeth (second protrusions) 63dt arranged at different positions in the circumferential direction. Note that the first oblique teeth 63ct and the second oblique teeth 63dt are both involute teeth, and protrusions protruding in the radial direction centered on the rotation axis L1. The first gear portion 63c and the second gear portion 63d are integrally molded with resin and rotate integrally. Therefore, the first gear portion 63c and the second gear portion 63d are the first rotating portion that rotates integrally with each other. , it can also be seen as a second rotating section. The first gear portion 63c meshes with the first main body gear portion 81c of the drive transmission gear 81, and the second gear portion 63d meshes with the second main body gear portion 81d of the drive transmission gear 81.

[0058] As shown in FIG. 1, the first gear portion 63c and the second gear portion 63d of the drive side flange 63 are twisted in the same direction, and the tooth surfaces shift toward the K direction as they move toward the J direction. This is the direction in which it twists. Note that the twisting direction of the first gear portion 63c and the second gear portion 63d is opposite to the twisting direction of the first main body gear portion 81c and the second main body gear portion 81d of the drive transmission gear 81. Further, as shown in FIG. 13(b), the torsion angle α2 of the second gear portion 63d is larger than the torsion angle α1 of the first gear portion 63c (that is, α1<α2 is satisfied). Note that the torsion angle α1 of the first gear portion 63c is the same as the torsion angle α1 of the first main body gear portion 81c, and the torsion angle α2 of the second gear portion 63d is the same as the torsion angle α2 of the second main body gear portion 81d. be. Further, the first gear portion 63c and the second gear portion 63d of the drive side flange 63 have the same number of teeth. In addition, the width (tooth width) W63c (Wc, Wc1) of the first oblique tooth (first protrusion) 63ct in the direction of the rotation axis L1 is the width of the second oblique tooth (second protrusion) 63dt in the direction of the rotation axis L1. (Face width) Greater than W63d (Wd). In other words, the first gear part 63c and the second gear part 63d each have a tooth width Wc of the first diagonal tooth (teeth, first protrusion) 63ct and a second diagonal tooth (teeth, second protrusion) in the direction of the rotation axis L1. )63dt and has at least one tooth such that the face width Wd satisfies the following formula A1. Wc>Wd...(Formula A1)

[0059] In other words, when the width (tooth width) of the first diagonal tooth 63ct, which has the widest width (tooth width) in the direction of the rotation axis L1 of the first gear part 63c, is Wc1, the second gear part 63d It has a second oblique tooth (second protrusion) 63dt whose width (tooth width) in the L1 direction is smaller than Wc1.

[0060] As will be detailed later, while the drive side flange 1763 is being 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 regulating force FB received by the second gear portion 1763d. Therefore, it is preferable to have such a relationship.

[0061] In addition, the width (meshing width) of the rotation axis L1 of the part where the first gear part 63c meshes (contacts) with the first main body gear part 81c, and the meshing of the second helical gear part 63c with the second main body gear part 81d. The larger the width, the better the drive transmission accuracy. However, if the engagement width is set larger than necessary, the width of the first gear part 63c and the second gear part 63c in the direction of the rotational axis L1 becomes large, which affects the drive side flange 63, drum unit 69, cartridge B, and eventually the device main body A. becomes large. Therefore, the tooth width Wc1 of the first diagonal tooth (teeth) 63ct having the widest tooth width in the first gear portion 63c and the tooth width Wc1 of the second diagonal tooth (teeth) 63dt having the widest tooth width in the second gear portion 63d. It is preferable that the face width Wd1 satisfies the following formula A2, more preferably formula A3. Wd1≦(4 / 5)·Wc1···(Formula A2) Wd1≦(3 / 4)·Wc1···(Formula A3)

[0062] Furthermore, from the viewpoint of the strength of the second diagonal tooth (teeth) 63dt of the second gear portion 63d, it is preferable that the second diagonal tooth (teeth) 63dt have a tooth width of a certain degree or more, and the tooth width Wc1 and the tooth width It is preferable that Wd1 satisfies the following formula A4. Wd1≧(1 / 10)·Wc1···(Formula A4)

[0063] Further, as shown in FIG. 14, the meshing pitch circle diameters D63c and D63d of the first gear part 63c and the second gear part 63d in the meshing between the drive side flange 63 and the drive transmission gear 81 are set to be almost the same. are doing. Furthermore, the tip circle diameters Dt63c and Dt63d of the first gear portion 63c and the second gear portion 63d are set to be approximately the same. Similarly, the meshing pitch circle diameters D81c and D81d of the first main body gear portion 81c and the second main body gear portion 81d are set to be approximately the same. As a result, the meshing between the first gear portion 63c and the first main body gear portion 81c and the meshing between the second gear portion 63d and the second main body gear portion 81d can be properly meshed without contacting the tooth tips. can.

[0064] In order to set the meshing pitch circle diameters D63c and D63d of the first gear part 63c and the second gear part 63d to be almost the same, the shapes of the first gear part 63c and the second gear part 63d must be set as follows. It is preferable to decide.

[0065] Specifically, the size of the tip diameter Dt63c of the first gear portion 63c is larger than the root diameter Db63d of the second gear portion 63d, or the tip diameter Dt63d of the second gear portion 63d. It is preferable to set the value to a value larger than 0.8 times (more preferably 0.9 times). Furthermore, the size of the tip diameter Dt63c of the first gear portion 63c is preferably set to a value smaller than 1.1 times the tip diameter Dt63d of the second gear portion 63d.

[0066] Furthermore, it is preferable that the size of the root diameter Db63c of the first gear portion 63c is set to a smaller value than the tip diameter Dt63d of the second gear portion 63d. Further, the size of the root diameter Db63c of the first gear portion 63c is preferably set to a value larger than 0.9 times the root diameter Db63d of the second gear portion 63d.

[0067] Further, the size of the tip diameter Dt63d of the second gear portion 63d is a value larger than the root diameter Db63c of the first gear portion 63c, or 0.8 times the tip diameter Dt63c of the first gear portion 63c ( It is preferable to set the value to be larger than (more preferably 0.9 times). Further, the size of the tip circle diameter Dt63d of the second gear portion 63d is preferably set to a value smaller than 1.1 times the tip circle diameter Dt63c of the first gear portion 63c.

[0068] Furthermore, it is preferable that the size of the root diameter Db63d of the second gear portion 63d is set to a smaller value than the tip diameter Dt63c of the first gear portion 63c. Further, the size of the root diameter Db63d of the second gear portion 63d is preferably set to a value larger than 0.9 times the root diameter Db63c of the first gear portion 63c.

[0069] Here, the diameters of the first gear part 63c and the second gear part 63d are used to show the relationship between these dimensions, but it is obvious that the same relationship holds even if the diameter is replaced with a radius. Further, in the embodiments to be described later, examples will be shown in which the teeth of the first gear portion 63c and the second gear portion 63d are replaced with a plurality of protrusions of various shapes. In this case, the tip circle is a circle drawn as a rotation locus when the tip (point) farthest from the rotation axis L1 among the tips of multiple projections rotates, and the diameter / radius of this circle is the tip circle diameter. / tooth tip circle radius.

[0070] In this way, in order to make the meshing pitch circle diameters D63c and D63d the same while making the helix angles of the first gear part 63c and the second gear part 63d different, a module is installed between the first gear part 63c and the second gear part 63d. and the amount of transfer. Similarly, regarding the drive transmission gear 81, the first main body gear section 81c and the second main body gear section 81d have different modules and different transfer amounts.

[0071] Further, the drive side flange 63 includes a cylindrical portion (intermediate portion, small diameter portion, shaft portion) 63e 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 on the rotation axis L1 is smaller than the tip diameter Dt63c of the first gear portion 63c and the tip diameter Dt63d of the second gear portion 63d. Furthermore, in this embodiment, the maximum diameter D63e of the cylindrical portion 63e centered on 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 on the rotation axis L1 is not limited to the above unless the drive side flange 63 comes into contact with the drive transmission gear 81 while being driven by the drive transmission gear 81. Furthermore, as will be explained later in Examples 22 and 23, the distance from the rotational axis L1 to the outer diameter of the cylindrical portion 63e is such that the drive side flange 63 and the drive transmission gear 81 can mesh with each other and transmit the driving force. The distance (radius) R63e may be configured to be smaller than the tip circle radius Rt63ct of the first gear portion 63c or the tip circle radius Rt63d of the second gear portion 63d, at least temporarily.

[0072] Here, the diameters of the first gear part 63c, second gear part 63d, and cylindrical part 63e are used to show the relationship among these dimensions, but it is obvious that the same relationship holds even if the diameter is replaced with radius. be. Note that the shape of the cylindrical portion 63e does not have to be a cylindrical shape centered on the rotation axis L1. For example, various shapes can be used, such as a polygonal prism shape and a shape that is not symmetrical 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 by the point farthest from the rotation axis L1 in the intermediate portion 63e is the maximum diameter D63e, and the radius of the circle is the radius R63e. is the maximum value of

[0073] By providing the cylindrical portion 63e, the second gear portion 63d can be placed at a position away from the drum 62 (more downstream in the J direction) so as not to come into contact with the first gear portion 81c. Similarly, the first gear portion 63c can be arranged at a position closer to the drum 62 (more downstream in the H direction) so as not to come into contact with the second main body gear portion 81d. 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. As a result, when the cartridge B is installed in the apparatus main body A, the first gear part 63c contacts the second main body gear part 81d in the direction of the rotation axis L1, and the second gear part 63d contacts the first main body gear part 81d. Contact with the portion 81c can be prevented. Further, when driving the drive transmission gear 81 and moving the drive transmission gear 81 to the balanced position, the first main body gear part 81c contacts the second gear part 63d, and the second main body gear part 81d Contact with the first gear portion 63c can be prevented. The width of the cylindrical portion 63e in the direction of the rotation axis L1 will be described in detail below.

[0074] <Drive transmission to developing roller> FIG. 15 is a diagram showing a drive transmission configuration from the drive side flange 63 to the developing roller 32. The developing roller 32 is fixed to the developing roller shaft 31, and a developing roller gear 30 is provided at one end of the driving side of the developing roller shaft 31 so as to be movable in the direction of the rotational axis of the developing roller shaft 31. The developing roller gear 30 can rotate integrally with the developing roller shaft 31 and the developing roller 32. That is, the developing roller gear 30 is provided so as to be able to transmit drive to the developing roller shaft 31 and the developing roller 32. The developing roller gear 30 is engaged with the first gear portion 63c of the drive side flange 63, and driving force is transmitted thereto.

[0075] The developing roller gear 30 may be configured to mesh with the second gear portion 63d to transmit the driving force. However, by configuring the developing roller gear 30 to mesh with the first gear portion 63c, the length of the developing roller shaft 31 in the rotational axis direction is shortened compared to a configuration in which the developing roller gear 30 meshes with the second gear portion 63d. be able to.

[0076] <Drive transmission operation> Next, the meshing operation between the drive transmission gear 81 and the drive side flange 63 will be explained in order from the mounting of the cartridge B using FIGS. 16, 17, 19, 20, and 21.

[0077] FIG. 16(a) is a schematic diagram of the drive transmission gear 81 and the drive side flange 63 viewed along their rotation axis direction. FIG. 16(b) is a cross-sectional view of the drive transmission gear 81 along the cutting line AF-AF. In the figures after FIG. 16(b), the hatched portions in the figures are cross sections of the peaks of the gear, and the area between the hatched portions corresponds to the portions where the valleys of the gear are located. FIG. 16(c) is a cross-sectional view of the drive side flange 63 along the cutting line AF-AF. FIG. 16(d) is a cross-sectional view of the drive transmission gear 81 taken along the cutting line AF-AF before the cartridge is attached. FIG. 16(e) is a cross-sectional view of the drive transmission gear 81 and the drive side flange 63 taken along the cutting line AF-AF after the cartridge B is attached and before the drive starts.

[0078] FIG. 17 is a cross-sectional view of the drive transmission gear 81 and the drive side flange 63 taken along the cutting plane AF-AF that is in contact with the meshing pitch circle of the drive side flange 63 immediately after the start of driving. c) and Fig. 17(d) as time passes in this order. 19(a), 19(b), and 19(c) are views of the drive transmission gear 81 and the drive side flange 63 as viewed along the H direction.

[0079] FIG. 21(a) is a view of the drive transmission gear 81 and the drive side flange 63 as viewed along a direction perpendicular to the rotational axis direction. FIG. 21(b) is a cross-sectional view taken along cutting line AD-AD of the first main body gear portion 81c during driving. FIG. 21(c) is a cross-sectional view taken along cutting line AD-AD of the second main body gear portion 81d during driving.

[0080] <Meshing when cartridge B is installed> As shown in FIG. 16(d), the drive transmission gear 81 before the cartridge B is installed is caused by the biasing force F1 of the compression spring 85 to cause the other end 81e of the drive transmission gear 81 to move toward the abutting surface of the main frame 84. It is held against 84b. By configuring the drive transmission gear 81 to be held against the abutment surface 84b in this way, the initial position of the drive transmission gear 81 in the rotational axis direction is kept constant, and the engagement with the drive side flange 63 is stabilized. be able to.

[0081] When the cartridge B is installed in the apparatus main body A along the installation direction M (M direction), the drive side flange 63 meshes with the drive transmission gear 81, as shown in FIG. 19(a). 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, movement of the drive side flange 63 in the M direction causes the drive transmission gear 81 to rotate in the I direction (clockwise). At this time, as shown in FIG. 16(e), the first main body gear part 81c or the second main body gear part 81d of the drive transmission gear 81 is connected to the first gear part 63c or the second gear part 63d of the drive side flange 63. They make contact and are pressed in the M direction. A thrust force F3 in the H direction acts on the drive transmission gear 81. However, since the other end 81e of the drive transmission gear 81 hits the abutment surface 84b of the main frame 84 and receives the reaction force F4, the drive transmission gear 81 cannot move in the H direction.

[0082] <Operation after start of drive> Next, a case will be described in which the drive side flange 63 is driven in order to perform an initial operation, a preparatory operation for image formation, and the like. As shown in FIG. 19(b), the drive transmission gear 81 is rotated by a motor (not shown) of the apparatus main body A and rotates in the I direction. As a result, the drive side flange 63 rotates in the K direction. Immediately after the drive transmission gear 81 starts rotating in the I direction, as shown in FIG. 17(a), the second body gear portion 81d of the drive transmission gear 81 first meshes with the second gear portion 63d of the drive side flange 63 and is driven. Suppose that force is transmitted. Then, the second main body gear section 81d causes the second gear section 63d to generate a thrust force in the H direction. However, the drive side flange 63 is restricted from moving in the H direction by the rib 71p, and receives a reaction force in the J direction corresponding to the thrust force in the H direction. Therefore, the second main body gear portion 81d receives a thrust force F5 in the J direction due to the reaction force received from the second gear portion 63d. This thrust force F5 causes the drive transmission gear 81 to move in the J direction.

[0083] As the drive transmission gear 81 moves in the J direction while the rotation continues, the first gear part 63c also meshes with the first main body gear part 81c, as shown in FIG. 17(b), and the first main body gear part 81c Thrust force F6 is generated. The thrust force F6 is the same thrust force in the J direction as the thrust force F7 previously received by the second main body gear portion 81d due to engagement with the second gear portion 63d. As a result, the drive transmission gear 81 further moves in the J direction.

[0084] When the drive transmission gear 81 rotates further and moves in the J direction, the second main body gear portion 81d eventually stops meshing with the second gear portion 63d, as shown in FIG. 17(c). On the other hand, the first gear portion 81c and the first gear portion 63c are maintained in mesh with each other, and a thrust force F8 acts on the first gear portion 81c in the J direction. At this time, the drive transmission gear 81 rotates the drive side flange 63 only by the engagement between the first main body gear part 81c and the first gear part 63c. That is, the tooth surface 81c1 on the downstream side in the I direction of the first main body gear portion 81c is in contact with the tooth surface 63c1 on the upstream side in the I direction of the first gear portion 63c.

[0085] This is because the torsion angle α2 of the second main body gear portion 81d of the drive transmission gear 81 is larger than the torsion angle α1 of the first main body gear portion 81c (α2>α1). The details will be explained below using FIG. 21(b) and FIG. 21(c). Assume that the drive transmission gear 81 moves in the J direction by a movement amount LL due to the thrust force received by the engagement with the drive side flange 63. In FIGS. 21(b) and 21(c), the first main body gear portion 81c and the second main body gear portion 81d are shown by solid lines before movement and by broken lines after movement, respectively. The amount of movement of the first main body gear portion 81c and the second main body gear portion 81d in the rotational direction due to this movement can be expressed as LL / tanα1 and LL / tanα2, respectively. Based on the relationship between the torsion angles α1 and α2, the amount of movement LL / tanα2 of the second main body gear portion 81d in the rotational direction is larger than the amount of movement LL / tanα1 of the first main body gear portion 81c in the rotational direction (LL / tanα1<LL / tanα2). In this way, the amount of movement in the rotational direction corresponding to the amount of movement LL in the J direction is greater for the second main body gear portion 81d than for the first main body gear portion 81c. Therefore, even if the first main body gear part 81c and the first gear part 63c are engaged, the second main body gear part 81d separates from the second gear part 63d.

[0086] When the rotation continues and the drive transmission gear 81 moves to the drive side J, as shown in FIG. It contacts the tooth surface (contact portion) 63d2 on the downstream side in the I direction of the second gear portion 63d. Note that the surface 81c1 of the first main body gear portion 81c and the surface 63c1 of the first gear portion 63c maintain contact. That is, in this state, the first main body gear part 81c of the drive transmission gear 81 presses the tooth surface (contact part) 63c1 with the tooth surface 81c1 to rotate the drive side flange 63, and the second main body gear part of the drive transmission gear 81 The tooth surface 81d2 of the portion 81d comes into contact with the tooth surface 63d2, thereby being sandwiched between the driving side flange 63. Then, the movement of the drive transmission gear 81 in the direction of the rotation axis L1 is stopped. The position in the direction of the rotational axis L1 at this time is defined as the balance position. A state in which the drive transmission gear 81 rotates at a balanced position and transmits the drive to the drive side flange 63 will be described.

[0087] In the balanced state, the following 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 a thrust force in the J direction that the first main body gear portion 81c receives due to the meshing force with the first gear portion 63c, and force F1 is a thrust force H that the second main body gear portion 81d receives due to the meshing force with the second gear portion 63d. The thrust force in the direction, force F1, is the biasing force of the compression spring 85. Further, the drive side flange 63 receives a force from the drive transmission gear 81 and is positioned by the side wall 71m or the rib 71p in the direction of the rotation axis L1, and a reaction force F11 that balances the force received from the drive transmission gear 81 is generated. Note that FIG. 17(d) shows a case where the drive transmission gear 81 is positioned in contact with the side wall 71m. In the balanced state, if friction is ignored, force F9, force F10, force F1, and force F11 are balanced, and the drive transmission gear 81 and the drive side flange 63 are respectively positioned in the direction of the rotation axis L1. It has become.

[0088] Also, in the K direction (rotation direction), the drive side flange 63 is sandwiched (in contact) by the first main body gear part 81c and the second main body gear part 81d of the drive transmission gear 81, and receives the following force. It has been received. In other words, the tooth surface (contact portion) 63c1 of the first gear portion 63c contacts the first main body gear portion 81c disposed on the upstream side in the K direction (first circumferential direction), thereby moving the drive side flange 63 to the K direction. It receives a driving force FD as a force component in the direction of rotation (predetermined direction). At the same time, the tooth surface (contact part) 63d2 of the second gear part 63d comes into contact with the second main body gear part 81d disposed on the downstream side in the K direction (first circumferential direction), thereby causing the K It receives a regulating force (braking force) FB as a component force in the direction that suppresses (regulates) rotation in the direction. Therefore, it can be said that the first gear part 63c is a driving force receiving part that receives the driving force FD, and the second gear part 63d is a regulating force receiving part that receives the regulating force FB. Note that the driving force FD is larger than the regulating force FB.

[0089] Here, since the second gear part 63d is provided integrally with the first gear part 63c in the rotational direction, it is configured such that it cannot rotate relative to the first gear part 63c in the opposite direction of the K direction. . Strictly speaking, since the drive side flange 63 is made of resin and deformation of the teeth and members occurs, the second gear portion 63d that receives the regulating force FB will move in the K direction relative to the first gear portion 63c. After rotating slightly in the opposite direction, the rotation stops and it is fixed. Therefore, the regulating force FB received by the second gear portion 63d acts on (is transmitted to) the first gear portion 63c. Based on the same principle, the driving force FD received by the first gear section 63d acts (is transmitted) to the second gear section 63d.

[0090] In this way, when the first gear section 63c receives the driving force FD and the second gear section 63d receives the regulating force FB, the rotational direction (I direction) is generated between the drive side flange 63 and the drive transmission gear 81. This is a state in which there is no play (backlash), that is, a backlash-free state. In this way, the drive side flange 63 is rotationally driven in the K direction while maintaining the backlash-free state. While meshing and transmitting drive in a backlash-free state, drive transmission with high rotational accuracy is possible.

[0091] Also, the width (tooth width) W63c of the first oblique tooth (first protrusion) 63ct in the direction of the rotation axis L1 is the width (tooth width) W63d of the second oblique tooth (second protrusion) 63dt in the direction of the rotation axis L1. larger than In other words, the second gear part 63d has a second bevel tooth (second protrusion) which is narrower than the first bevel tooth 63ct, which is the widest width (tooth width) in the direction of the rotation axis L1 of the first gear part 63c. )63dt.

[0092] Note that if the second main body gear part 81d and the second gear part 63d do not contact each other at the start of driving, but the first main body gear part 81c and the first gear part 63c contact each other, the above-mentioned FIG. 17(a) and FIG. Driving starts from the state shown in FIG. 17(c) without going through the state shown in 17(b). Then, based on the same principle as described above, the balanced state shown in FIG. 17(d) is achieved. That is, from the state shown in FIG. 17(c), the drive transmission gear 81 moves in the J direction by thrust force F8, and shifts to the balanced state shown in FIG. 17(d).

[0093] <Release of engagement when removing cartridge B> Next, a disengagement operation between the drive transmission gear 81 and the drive side flange 63 when removing the cartridge B after the drive is completed will be explained using FIGS. 18, 19, and 20. FIG. 18 is a cross-sectional view taken along the cut plane AF-AF that is in contact with the engagement pitch circle of the drive transmission gear 81 and the drive side flange 63 when removing the cartridge B after the drive is completed, and FIGS. 18(a) and 18(b) ) shows the state over time. FIG. 20 is a schematic diagram of the drive transmission gear 81 and the drive side flange 63 viewed along the H direction.

[0094] As shown in FIG. 19(c), the cartridge B is removed from the apparatus main body A by moving in the removal direction N (N direction). The N direction is the opposite direction 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, by moving the drive side flange 63 in the N direction, the drive transmission gear 81 is rotated in the K direction (counterclockwise). At this time, as shown in FIG. 18(a), when the drive side flange 63 moves in the N direction, the first gear portion 63c presses the first main body gear portion 81c. Further, FIG. 20 shows the positional relationship between the drive side flange 63 that moves in the N direction and the drive transmission gear 81, with the solid line before movement in the N direction and the broken line after movement. 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 distance LA to distance LB as the drive side flange 63 moves in the N direction. (LA<LB).

[0095] As a result, the meshing position of the teeth of the first gear portion 63c and the first main body gear portion 81c gradually shifts to the tips of the teeth. Therefore, as shown in FIG. 18(b), the play (backlash) in the meshing of the teeth in the rotational direction increases, and the surface 63d2 of the second gear portion 63d and the tooth surface 81d2 of the second main body gear portion 81d. The gap AL between them becomes larger. When a gap AL occurs between the tooth surfaces, no force from the second gear portion 63d acts on the drive transmission gear 81, and thrust in the J direction is generated due to the meshing of the first main body gear portion 81c and the first gear portion 63c. Force F16 works. As a result, when the cartridge B is removed, the drive transmission gear 81 gradually moves in the J direction while rotating in the K direction, and eventually the first gear portion 63c and the first main body gear portion 81c are no longer engaged. As a result, the engagement between the drive side flange 63 and the drive transmission gear 81 is released.

[0096] <Twist angle setting> Next, preferred torsion angles of the first gear portion 63c and the second gear portion 63d will be explained using FIG. 46. 46(a) and 46(b) are cross-sectional views taken along the cut plane AF-AF in contact with the engagement pitch circle of the drive transmission gear 81 and the drive side flange 63 of the second gear portion 63d and the second main body gear portion 81d. It is.

[0097] As described above, when the first gear part 63c is the gear part that receives the driving force FD and the second gear part 63d is the gear part that receives the regulating force FB, the torsion angle α1 of the first gear part 63c and the The setting of the torsion angle α2 of the 2-gear section will be explained. First, it is assumed that the first gear part 63c is a gear part that receives the driving force FD, and the second gear part 63d is a gear part that receives the regulating force FB, so that the torsion angle α2 is larger than the torsion angle α1 (α2 >α1). If the torsion angle α2 is smaller than the torsion angle α1, drive cannot be transmitted in a backlash-less state. That is, the thrust force applied by the first gear part 63c to the first main body gear part 81c and the thrust force applied by the second gear part 63d to the second main body gear part 81d are not balanced, and the direction of the rotation axis L1 of the drive transmission gear 81 The position of is not determined by the balance position.

[0098] The torsion angle α1 of the first gear portion 63c of the drive side flange 63 is preferably 10° or more (α1≧10°), more preferably 15° or more (α1≧15°), and 20° or more (α1≧20°). is even more preferable. This is because, in general, if the tooth width (width of the gear teeth in the direction of the rotational axis L1) is the same, the larger the helix angle, the larger the engagement ratio and the better the rotation accuracy. Further, the twist angle α1 is preferably 40° or less (α1≦40°), and more preferably 35° or less (α1≦35°). This is because, in general, when the helix angle is large, the moldability with a mold deteriorates.

[0099] On the other hand, the torsion angle α2 of the second gear portion 63d of the drum gear 63 is preferably 40° or less (α2≦40°), and more preferably 35° or less (α2≦35°). This is because, in general, when the helix angle is large, the moldability with a mold deteriorates. Further, the torsion angle α2 of the second gear portion 63d of the drum gear is preferably 20° or more (α2≧20°), and more preferably 25° or more (α2≧25°). The reason is that, as shown in FIGS. 46(a) and 46(b), the larger the torsion angle α2 is, the larger the width E of the contact surface with the second main body gear portion 81d in the rotation direction (K direction) becomes. It is. In this embodiment, the twist angle α2 is set to 35°.

[0100] If the width E is small, when the second gear part 63d receives the thrust force F9 (see FIG. 17(d)) ​​received by the first gear part 63c, the tooth surface of the second gear part 63d is deformed, and the second main body gear part 81d becomes wedge-like and moves, making positioning in the direction of the rotation axis L1 unstable. Therefore, in order to reliably receive the thrust force F9 and position the drive transmission gear 81 in the direction of the rotational axis L1, it is necessary to secure a certain width E.

[0101] Taking all the above into account, the torsion angle α1 is preferably 10° or more and 40° or less (15°≦α1≦40°), more preferably 15° or more and 40° or less (15°≦α1≦40°), and 20° or more. More preferably, the angle is 35° or less (20°≦α1≦35°). Further, the twist angle α2 is preferably 20° or more and 40° or less (20°≦α2≦40°), and more preferably 25° or more and 35° or less (25°≦α2≦35°). In this example, the twist angle α1 is set to 20° and the twist angle α2 is set to 35°, which satisfy the above conditions.

[0102] <Width of cylindrical part 63e> Next, the width (length) of the cylindrical portion 63e in the direction of the rotation axis L1 will be explained. FIG. 47(a) is a schematic diagram of the drive-side flange 63 and the drive transmission gear 81 when the cartridge B is attached, viewed from a direction perpendicular to the rotational axis L1. FIG. 47(b) is a schematic diagram of the drive side flange 63 and the drive transmission gear 81 during driving, viewed from a direction perpendicular to the rotational axis L1.

[0103] As described above, by providing the cylindrical portion 63e, the first gear portion 63c comes into contact with the second main body gear portion 81d in the direction of the rotation axis L1, and the second gear portion 63d contacts the first main body gear portion 81d. You can prevent contact with 81c. Furthermore, by providing the cylindrical portion 63e, when the drive transmission gear 81 is driven and the drive transmission gear 81 moves to the balanced position, the first main body gear portion 81c comes into contact with the second gear portion 63d; , it is possible to prevent the second main body gear portion 81d from coming into contact with 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 in the direction of the rotation axis L1 is synonymous with the width (length) of the gap g in the direction of the rotation axis L1.

[0104] The contact described above can occur in two situations: First, as shown in FIG. 47(a), when the cartridge B is installed in the apparatus main body A, the other end 81e of the drive transmission gear 81 is held against the abutment surface 84b of the main frame 84. situation. The second situation is a situation where the drive transmission gear 81 is moving toward the balanced position as shown in FIG. 47(b).

[0105] The positions of the first gear part 63c and second gear part 63d of the drive side flange 63, the positions of the first main body gear part 81c and the second main body gear part 81d of the drive transmission gear 81, and the balance position are determined by the factors shown below. may fluctuate due to the influence of Specifically, (1) the tolerance in the direction of the rotation axis L1 of related parts such as the drive side flange 63, drive transmission gear 81, and cleaning frame (drum frame) 60a, (2) the rotation axis of the drive side flange 63 Tolerance related to the distance between L1 and the rotational axis L2 of the drive transmission gear 81, (3) Tolerance in the phase of the rotational direction of the teeth of the first gear portion 63c and second gear portion 63d of the drive side flange 63, (4) Tolerance in the rotational direction phase of the teeth between the first main body gear part 81c and the second main body gear part 81d of the drive transmission gear 81, (5) deformation of the teeth due to the maximum drive load, and the difference between the drive side flange 63 and the drive transmission gear 81. These are thermal expansion and thermal contraction. Taking these factors into consideration, the width (length) We of the cylindrical portion 63e (or gap g) in the direction of the rotation axis L1 is set.

[0106] Specifically, the width We is set to satisfy the following formula B1, where Wc is the width (tooth width, length) of the teeth of the first gear portion 63c in the direction of the rotation axis L1, and this is used as a reference. It is preferable to do so. We≧Wc / 5...(Formula B1)

[0107] Also, as the width We increases, the width of the cartridge B in the direction of the rotational axis L1 increases, so in order to downsize the cartridge B and the device main body A, the width We should be set so as not to be larger than necessary. Should. Considering this, it is more preferable that the width We is set to satisfy the following formula B2. We≦Wc...(Formula B2)

[0108] In this embodiment, Wc=8.6 mm and We=2.3 mm are set, which satisfy the above equations B1 and B2. Note that when the tooth width Wc of the first gear portion 63c is not constant, the tooth width Wc1 of the tooth with the widest tooth width is assumed to be the tooth width Wc.

[0109] Furthermore, as is clear from FIGS. 13(b), 14, and 47, the width We is defined as Wd, which is the width (tooth width, length) of the teeth of the second gear portion 63c in the direction of the rotational axis L1. When using this as a standard, it is preferable to set it so that the following formula B3 is satisfied. We≦Wd...(Formula B3)

[0110] <About rotational accuracy> The reason why the rotation accuracy is improved in the backlash-free state will be explained below using FIGS. 22 and 49. FIG. 22(a) is a diagram of the drive transmission gear 81 and the drive-side flange 63 viewed along a direction perpendicular to the rotational axis direction. FIG. 22(b) is a partial cross-sectional view of the meshing portion of general helical gears 51 and 53 as a comparative example. FIG. 22(c) is a partial cross-sectional view taken along the cut plane AD-AD, which is in contact with the engagement pitch circle of the drive transmission gear 81 and the drive side flange 63. FIG. 22(d) is a partial perspective view of the helical gear 51. FIG. 22(e) is a partial perspective view of the drive transmission gear 81. FIG. 49 is a graph comparing the drive transmission error when the drive side flange 63 and the helical gear 53 are misaligned.

[0111] As shown in Figure 22(b), in gear drives, due to molding precision and play or deformation of the shaft, the tooth surfaces of the helical gears on the driving side and driven side may not be parallel to each other in the tooth trace direction and may mesh with each other. be. Such a state is generally called a misaligned state. If the alignment of the helical gear (driving side) 51 and the helical gear (driven side) 53, which are general helical gears, deviates by β°, the helical gears 51 and 53 will move at one end of the tooth surface in the axial direction. Compared to a state in which there is no misalignment, the engagement rate is significantly reduced. As a result, rotation accuracy during drive transmission is extremely deteriorated. FIG. 22(d) shows a region of the tooth surface of the helical gear 51 that meshes with the helical gear 53 when the alignment is misaligned, and the width of this region is defined as the width LP.

[0112] On the other hand, as shown in FIG. 22(c), the drive side flange 63 has a first gear portion 63c and a second gear portion 63d of the drive side flange 63, and a first main body gear portion 81c and a second gear portion 81c of the drive transmission gear 81. It rotates by sandwiching the main body gear part 81d. As a result, a pinching force FC (ie, rotational drive brake) acting on the second main body gear portion 81d is generated. The reaction of this pinching force FC is added to the force applied to the tooth surface of the first main body gear portion 81c that presses the first gear portion 63c in the I direction, and becomes a force FB. On the other hand, no residual load is generated in the force FA applied to the tooth surface of the conventionally used helical gear 51 when the same load torque is applied. Therefore, the force FB applied to the tooth surface of the first main body gear portion 81c of this embodiment is larger than the force FA applied to the tooth surface of the helical gear 51. FIG. 22(e) shows the area where the tooth surface of the first main body gear part 81c of the drive transmission gear 81 meshes with the first gear part 63 of the drive side flange 63 when the alignment is misaligned, and the width of this area Let be the width LQ. Since the force FB is larger than the force FA, when comparing the width LP in FIG. 22(d) and the width LQ in FIG. 22(e), the width LQ is larger than the width LP. Therefore, the reduction in the overlapping engagement ratio of the first main body gear portion 81c and the first gear portion 63c when the alignment is misaligned is smaller than that of the helical gears 51 and 53.

[0113] FIG. 49 shows the driven side helical gear 53 and drive side relative to the amount of alignment deviation when using general helical gears 51 and 53 and when using the drive transmission gear 81 and drive side flange 63 of this embodiment. 7 is a graph showing the measurement results of the drive transmission error of the side flange 63. In addition, between the helical gears 51 and 53, the drive transmission gear 81, and the drive side flange 63, the gear specifications such as the number of teeth, the amount of backlash in the interaxial direction of 0.15 mm, and the load torque of 0.25 N. The conditions such as m and rotational speed of 270 rpm were the same, and the shaft and gear were fitted without play. Here, the drive transmission error (%) indicates the deviation ratio of the experimental rotation pitch with respect to the ideal rotation pitch in the period in which the gears engage. For example, if the ideal rotational pitch is 0.7258mm, and the experimental deviation from the ideal rotational pitch is 0.00036mm, it becomes 0.05% (=0.00036 / 0.7258×100). In addition, the amount of alignment deviation (°) is 0° when the axes of the meshing gears are parallel, and the angle β (see Figure 22(b) and Figure 22(c)) in the tooth trace direction of each tooth is offset. This shows the angle between the axes when the axis of the driven gear is tilted. As shown in this graph, when misalignment occurs, deterioration in the rotation accuracy of the drive side flange 63 of this embodiment is suppressed more than that of the general helical gear 53. Therefore, it can be said that the drive transmission configuration using the drive transmission gear 81 and the drive side flange 63 of this embodiment is more resistant to misalignment than the drive transmission configuration using a general helical gear.

[0114] <About wear of drive transmission gear> Next, wear of the drive transmission gear 81 and the helical gear 101 will be explained below using FIG. 24. FIG. 24(a) is a schematic diagram of a drive transmission configuration using a conventional helical gear. FIG. 24(b) is a schematic diagram of the drive transmission configuration of this embodiment. As shown in FIG. 24(a), when the helical gear 101 is rotationally driven, the helical gear 101 receives a thrust force (force in the axial direction) FD due to meshing force. As a result, the helical gear 101 moves in the H direction toward the non-drive side, and the end surface 101a of the helical gear 101 and the abutment surface 184b of the main frame 84 come into contact and slide, causing wear. . On the other hand, as shown in FIG. 24(b), the position of the drive transmission gear 81 of this embodiment in the direction of the rotation axis L1 is determined by the drive side flange 63 and the spring 85 (not shown) during the drive. A gap AA is formed between the H-direction end face 81e and the J-direction end face 81f of the drive transmission gear 81 and the main frame 84 and the second drive-side side plate 83, so that they do not slide. Therefore, wear of the two end surfaces 81e and 81f of the drive transmission gear 81, the main frame 84, and the second drive-side side plate 83 can be suppressed, and durability can be increased.

[0115] <Comparison with conventional coupling drive> Next, a comparison with a configuration in which a drum is driven by a conventional coupling will be explained using FIGS. 26 and 27. FIG. 26(a) is a cross-sectional view of a drive transmission section of a conventional coupling drive, and the cross section includes the rotational axis of the coupling. FIG. 26(b) is a cross-sectional view of the drive transmission section of this embodiment, and the cross section includes the rotation axis (L1) of the drive side flange 63 and the rotation axis of the drive transmission gear 81. FIG. 27 is a graph showing the amount of deformation between the coupling drive and the drive transmission gear.

[0116] As shown in FIG. 26(a), in the conventional coupling drive, a drive side flange 263 having a convex coupling 263a in the shape of a twisted polygonal column is attached to the end of the drum 62 of the cartridge. . The drum flange 263 has a support portion 263b that is a cylindrical portion having a diameter smaller than the diameter of the drum 62. The device main body has a drive transmission gear 281 including a concave coupling 281a into which a coupling 263a is inserted and engaged.

[0117] The coupling 263a is provided at the end of the drive side flange 263 in the rotational axis direction. Therefore, the amount of twist of the drive side flange 263 during coupling drive is larger than the amount of twist of the drive side flange 63 during gear drive of this embodiment shown in FIG. 26(b). As shown in the simulation results of the amount of deformation of the drive members (drum flange 263, drive side flange 63) in the rotational direction, gear drive (drive at drive side flange 63) is better than coupling drive (drum flange 63) in Figure 27. The amount of deformation is smaller than that of 263 drive). Here, the amount of deformation of the drive member in the rotational direction will be explained. This amount of deformation is determined by fixing the drum coupling 263 and the drum 62 side of the drive-side flange 63, and applying the same static load torque of 0.25N to the engagement portion with the drive input member 281 or the meshing portion with the drive transmission gear 81. This is the amount of displacement in the rotational direction of the drive transmission point to the drum 62 when multiplied by m. The drive transmission point is a point fixed to the drum 62. The amount of displacement is converted into the amount of positional deviation compared to the case where there is no twist at a predetermined point on the surface of the drum 62. Due to this difference in the amount of deformation of the drive member, when the load torque of cartridge B fluctuates, the change in the amount of deformation of the drive member is smaller in gear drive than in coupling drive. 62's rotational speed becomes smaller. In other words, the density unevenness of the image in the rotational direction of the drum 62 on the image when the load torque fluctuation of the cartridge B occurs (the sub-scanning direction between the scanning lines formed when scanning the surface of the drum 62 with the laser beam L) (occurring due to pitch variations (pitch unevenness)) can be suppressed to a low level. In this way, with the drive transmission configuration of the drive side flange 63 and the drive transmission gear 81 of the embodiment described above, it is possible to suppress a decrease in the rotation accuracy of the drum 62 due to load torque fluctuations, compared to the conventional coupling drive configuration. Can be done.

[0118] In addition, when compared with the conventional coupling drive from another point of view, in the case of the conventional coupling drive, a retraction mechanism is provided for moving the coupling 263a on the main body side back and forth in the direction of the rotation axis in order to install and remove the cartridge B. It is necessary to provide

[0119] Next, this evacuation mechanism will be explained using FIG. 28. FIG. 28(a) is a cross-sectional view of the drum 62 of the evacuation mechanism, taken along the axis of rotation. FIG. 28(b) is a schematic cross-sectional view of an image forming apparatus including a retraction mechanism. 28(c) and 28(d) are cross-sectional views of the drive transmission gear 281 and the retraction mechanism, and the cross sections include the rotational axis of the drive transmission gear 281.

[0120] The main body of the coupling-driven image forming apparatus is provided with a retraction mechanism consisting of a link 210, a cylindrical cam 212, and a compression spring 214. One end of the link 210 is connected to an opening / closing door 211 of the apparatus main body A. The other end of the link 210 is connected to a cylindrical cam 212 rotatably provided between the drive input member 281 and the side wall 213 on the same axis as the drive input member 281. Further, as shown in FIG. 28(a), the cylindrical cam 212 has an inclined surface 212d, a convex surface 212c, and a concave surface 212e having a height difference in the rotational direction on one end surface in the axial direction. Furthermore, the side wall 213 has a slope 213e, a convex surface 213f, and a concave surface 213g at locations facing the slope 212d, convex surface 212c, and concave surface 212e, respectively. Further, as shown in FIG. 28(d), the drive transmission gear 281 is urged toward the H direction by the compression spring 214.

[0121] As shown in FIG. 28(b), by opening the door 211, the cylindrical cam 212 is rotated in the I direction via the link 210, and the convex surfaces 212c and 213f provided on the cylindrical cam 212 and the side wall 213 come into contact with each other. to move the cylindrical cam 212 in the J direction. This movement of the cylindrical cam 212 in the J direction causes the cylindrical cam 212 to move the drive input member 281 in the J direction against the biasing force of the compression spring 214, as shown in FIG. 28(c). As a result, the drive input member 281 moves in a direction away from the drum flange 263 (see FIG. 26(a)) and releases the engagement between the coupling 281a and the coupling 263a (see FIG. 26(a)). As a result, cartridge B can be removed.

[0122] Further, as shown in FIG. 28(b), when the door 211 closes, the cylindrical cam 212 is moved through the link 210 while the slopes 212d and 213e provided on the cylindrical cam 212 and the side wall 213 are brought into contact with each other. Rotate in the opposite direction. During this rotation, the cylindrical cam 212, the side wall 213, and the drive input member 281 no longer come into contact with each other in the rotational axis direction, and as shown in FIG. 28(d), the drive input member 281 is moved in the H direction by the urging force of the compression spring 214. It is possible to move towards. As a result, the drive input member 281 moves in a direction approaching the drum flange 263 (see FIG. 26(a)), so that the coupling 281a and the coupling 263a (see FIG. 26(a)) can be engaged with each other.

[0123] In this way, in the case of the conventional coupling drive, a retracting mechanism is required as described above, and the apparatus main body may be increased in size or cost by the retracting mechanism. However, in the case of gear drive as in this embodiment, the cartridge B can be installed and removed without providing such a retraction mechanism.

[0124] <Modification example 1> Next, Modification 1 will be explained. In the embodiment described above, the first main body gear portion 81c and the second main body gear portion 81d of the drive transmission gear 81 have the same number of teeth, but they do not necessarily have to be the same. However, the reduction ratio between the first main body gear part 81c of the drive transmission gear 81 and the first gear part 63c of the drive side flange 63, the second main body gear part 81d of the drive transmission gear 81 and the second gear of the drive side flange 63, It is necessary to make the reduction ratio the same as that of the section 63d. For example, if the number of teeth of the first gear section 81d of the drive transmission gear is 20, the number of teeth of the first gear section of the drum gear is 30, and the reduction ratio is 2:3, the number of teeth of the second main gear section 81d of the drive transmission gear is 20. If the number of teeth is 40 and the number of teeth of the second gear portion 63d of the drive side flange 63 is 60, the reduction ratio will be the same, 2:3. In this case as well, the gear of the drive transmission gear 81 can be sandwiched between the first gear part 63c and the second gear part 63d of the drive side flange 63, so it is possible to create a backlash-free state in the rotation direction. It is.

[0125] <Variation 2> Next, modification 2 will be explained. In this modification, the first gear part 181c and the second gear part 181d of the drive transmission gear 181 have different numbers of teeth, and the number of teeth of one is not an integral multiple of the number of teeth of the other. The first gear portion 163c and the second gear portion 163d of the drive side flange 163 also have different numbers of teeth from each other, and the number of teeth of one is not an integral multiple of the number of teeth of the other. These points are the points in which this modification differs from the previously described embodiment, and other than these different points and the configurations associated therewith, the configuration of this modification is the same as that of the previously described embodiment, Explanation will be omitted.

[0126] In this modification, as in the previous embodiment, it is possible to create a backlash-free state in the rotational direction. However, due to the above-described setting of the number of teeth, this modification has a configuration in which the meshing phase of the gear of the drive side flange 163 with respect to the drive transmission gear 181 is not unique. In a configuration where the meshing phase is not unique, the axial position (balanced) position of the drive transmission gear 181 will be explained using FIG. 25. FIG. 25(a) is a schematic diagram of a drive transmission configuration using the drive transmission gear 81 of this embodiment described above. FIG. 25(b) is an explanatory diagram of a drive transmission section using a modified drive transmission gear 181 and a drive side flange 163. 25(c) and 25(d) show a state in which the drive transmission gear 181 is in the balanced position after the drive transmission gear 181 is driven.

[0127] Comparing FIG. 25(c) and FIG. 25(d), the drive transmission gear 181 and the drive side flange 163 are in mesh with each other in both cases, but the way in which they engage at the meshing portion is different from each other. Specifically, FIG. 25(c) shows the tooth crests of the first gear portion 181c and the tooth ridges of the second gear portion 181d of the drive transmission gear 181 at the meshing portion between the drive side flange 163 and the drive transmission gear 181. In this state, the teeth of the first gear portion 163c of the drive side flange 163 are in phase with the teeth of the second gear portion 163d. FIG. 25(d) shows that the tooth peaks of the first gear portion 181c and the second gear portion 181d of the drive transmission gear 181 in the meshing portion are in phase with each other, and the first gear portion of the drive side flange 163 is shown in FIG. This is a state in which the peaks of the teeth of the gear portion 163c and the valleys of the teeth of the second gear portion 163d are in phase.

[0128] If the number of teeth of the first gear section 181c and the second gear section 181d of the drive transmission gear 181 is different, the phase between the peaks of the teeth of the first gear section 181c and the second gear section 181d will change the rotation of the gear. Depends on the phase of the direction. For example, if there is a position Q1 where the phase of the tooth peak 181cs of the first gear part and the peak part 181ds of the second gear part match depending on the phase of the gear rotation direction, then the peak part 181cs of the first gear part and the peak part 181ds of the second gear part match. There is also a position Q2 where the phase matches the trough 181dv of the 2nd gear section. 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 shown in FIGS. 25(c) and 25(d), the driving force on the driving side flange 163 is determined by the initial meshing phase (before driving) in the rotational direction between the drive transmission gear 181 and the driving side flange 163. The axial balance position of the transmission gear 181 is different. Figure 25(c) shows the case where the balance position of the drive transmission gear 181 is the furthest downstream in the H direction, and Figure 25(d) shows the case where the balance position of the drive transmission gear 181 is the furthest downstream in the J direction. There is. The amount of change in the balance position is, for example, the first gear part 181c and the second gear part 181d of the drive transmission gear 181 based on the midline between the first gear part 163c and the second gear part 163d of the drive side flange 163. It is possible to express it by the amount of deviation of the boundary line. In other words, in the state of Fig. 25(c), the deviation amount LD is in the J direction, and in the state of Fig. 25(d), the deviation amount is LE in the H direction, so the sum of the deviation amount LD and deviation amount LE (LD + LE ) is the amount of change in the balance position in this modification.

[0129] If the first gear part 181c contacts the second gear part 163d or the second gear part 181d contacts the main body frame 184 before the drive transmission gear 181 reaches the balance position, or if the second gear part 181d If it comes into contact with the first gear portion 163c, the backlash-free state cannot be achieved even if it is driven. Therefore, in this modification, the distance LF (width of the cylindrical part 163e) between the first gear part 163c and the second gear part 163d of the drive side flange 163 and the A gap LG is set between the drive transmission gear 181 and the main body frame 184.

[0130] On the other hand, in the configuration of the above-described present embodiment shown in FIG. 25(a), the first main body gear section 81c and the second main body gear section 81d have the same number of teeth; The positional relationship between the peak portions 81cs and 81ds with respect to the main body gear portion 81d does not change depending on the phase in the rotation direction. Therefore, the balanced position in which the drive transmission gear 81 is positioned in the axial direction with respect to the drive side flange 63 does not change. In other words, there is no need to consider the amount of change in the balance position (LD+LE), which was necessary in the modified example. Therefore, in this embodiment, the gap between the first gear part 63c and the second gear part 63d of the drive side flange 63 (width of the cylindrical part 63e) can be designed to be smaller than in the modified example, and the cartridge B can be Can be made smaller. Furthermore, the device main body A of this embodiment can be designed to have a smaller gap between the drive transmission gear 81 and the main body frame 84 than in the modified example. As a result, it is possible to downsize the cartridge B and / or the device main body A.

[0131] <Other variations> Next, a modification example in which the main change is in a portion other than the drive transmission structure itself of the drive side flange 63 and the drive transmission gear 81 will be described.

[0132] <Application to cleanerless configuration> In the above embodiment, the cartridge B was described in which the toner remaining on the drum 62 without being transferred is scraped off by bringing the rubber blade 77a into contact with the drum 62 and stored in the waste toner chamber 71b (see FIG. (see 3). However, cartridge B may have a cleanerless configuration. In other words, the drive transmission configuration of the drive side flange 63 and the drive transmission gear 81 of the above-described embodiment may be applied to a cartridge with a cleanerless configuration.

[0133] FIG. 23 is a cross-sectional view of cartridge B having a cleanerless configuration. The cleaner-less cartridge B is configured and controlled so that the remaining toner on the drum 62 can be collected by the developing roller 32. Therefore, cartridge B does not have a rubber blade in contact with drum 62. Therefore, compared to a cartridge B with a cleanerless configuration in which the rubber blade 77a is in contact with the drum 62, the drum 62 is driven by the absence of the rubber blade 77a, which was a resistance when rotating the drum 62. The torque required for this is small. As a result, the rotational speed of the drum 62 tends to fluctuate due to the influence of impact and the like when the sheet material PA is conveyed. In other words, the rotation accuracy of the drum 62 may be reduced. By applying the drive transmission configuration of the drive side flange 63 and the drive transmission gear 81 of the embodiment described above, the drum 62 can be driven in a backlash-free state between the drive side flange 63 and the drive transmission gear 81. For this reason, compared to a configuration in which the drive side is driven in a state where there is backlash or play in the rotational direction between the drive side flange and the drive member on the main body side that transmits the drive to it, the rotation of the drum 62 due to the absence of the rubber blade is Decrease in accuracy can be suppressed.

[0134] <Application to configuration without magnet roller 34> Further, in the above-mentioned embodiments, a developer carrier in which a magnet roller 34 is provided inside the developing roller 32 has been described, but an elastic roller without a magnet roller provided therein may be used.

[0135] <Application to a configuration in which the developing roller gear 30 is engaged with the second gear portion 63d> Furthermore, in the above-mentioned embodiment, a configuration was described in which the developing roller gear 30 meshes with the first gear portion 63c of the drive side flange 63. However, the developing roller gear 30 may be configured to mesh with the second gear portion 63d. This case will be explained using FIG. 29. FIG. 29 is a schematic diagram showing the engagement between the drive side flange 63 and the developing roller gear 30. The developing roller gear 130 fixed to the end of the developing roller shaft 31 meshes with the second gear portion 63d. Since the second gear portion 63d has a larger helix angle than the first gear portion 63c, the meshing ratio also increases accordingly. Therefore, the tooth width of the developing roller gear 130 that meshes with the second gear portion 63d can be made smaller than that of the developing roller gear 30 that meshes with the first gear portion 63d.

[0136] <Application to drive transmission configuration from drive side flange to developing roller gear> Furthermore, a configuration similar to the configuration for transmitting the driving force from the drive-side flange 63 to the drive-side flange 63 may be further applied to the configuration for transmitting the driving force from the drive-side flange 63 to the developing roller gear 230. This case will be explained below using FIG. 30. FIG. 30 is a perspective view of cartridge B. The developing roller gear 230 is provided with a first developing gear section 230c and a second developing gear section 230d that mesh with the first gear section 63c and the second gear section 63d of the driving 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 based on the same principle as the drive transmission gear 81 moves in the direction of the rotation axis L1 and reaches the balance position in the previously described embodiment. direction and reach the equilibrium position. When the developing roller gear 230 is in the balanced position, the developing roller gear 230 is driven with no backlash against the drive side flange 63, which suppresses deterioration of rotational accuracy of the developing roller 32 due to misalignment or load fluctuations. can do.

[0137] <Application to a configuration in which the developing roller gear is driven without going through the drive side flange> Further, the driving force may be transmitted to the developing roller 532 without passing through the driving side flange 63. FIG. 44 is a partial perspective view of cartridge B showing the drive train to developing roller 532. Note that for the sake of explanation, a part of the frame of cartridge B is not shown.

[0138] As shown in FIG. 44, the developing roller 532 is not configured to receive the driving force from the drive side flange 63, but is configured to receive the driving force via another path. Specifically, the cartridge B has a developer coupling member 89 that can be engaged with a coupling member (not shown) for driving a developer roller of the apparatus main body A. Furthermore, the cartridge B is provided with idler gears 90 and 91 that mesh with the gear portion 89a of the developer coupling member 89, and has a developing roller gear 530 that meshes with the idler gear 91 at one end of the shaft of the developing roller 532. In this configuration, the developing roller 530 is driven by the driving force received by the developing coupling member 89 being transmitted via the idler gears 90, 91 and the developing roller gear 530. Therefore, it is possible to control the drive of the developer coupling member 89 separately from the drive of the drive-side flange 63, for example, by driving the developer coupling member 89 while driving the drive-side flange 63 is stopped.

[0139] <Application to drive transmission configuration to rotating bodies other than drums> The drive side flange 63 was attached to the end of the drum 62, but the developing roller gear 30 is provided with a first gear part 63c, a second gear part 63d, and a cylindrical part 63e, and the drive transmission gear 81 connects the developing roller 32. It is also possible to apply it to a driving configuration. Furthermore, the objects driven by the drive transmission gear 81 are not limited to developer carriers that carry toner (developer), such as the drum 62 and the developing roller 32. The object driven by the drive transmission gear 81 may be, for example, the conveying member (or stirring member) 43 that conveys (or stirs) toner, the charging roller 66, or the supplying member that supplies toner to the developing roller 32. . Further, when the object to be driven by the drive 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 have a photoreceptor such as the drum 62.

[0140] [Example 2] Next, Example 2 will be described below using FIG. 31. This embodiment differs from Embodiment 1 in the configurations of the first gear section and the second gear section provided on the drive side flange. The other points are the same as those in Example 1, so explanations will be omitted.

[0141] FIG. 31 is a sectional view of the meshing portion of the drive transmission gear 81 and the drive side flange 263, and the cross section is a surface in contact with the meshing pitch circle of these. The drive side flange 263 has 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 spur teeth (first protrusions) 263ct having a tooth width that can fit between the teeth of the first main body gear portion 81c. The second gear portion 263d includes a plurality of second spur teeth (second protrusions) 263dt having a tooth width that can fit between the teeth of the second main body gear portion 81d. Further, the width (tooth width) of the first spur tooth 263ct in the direction of the rotation axis L1 is larger than the width (tooth width) of the second spur tooth 263dt in the direction of the rotation axis L1. The plurality of first spur teeth and the plurality of second spur teeth are protrusions that protrude in the radial direction centered on the rotational axis L1, and are arranged at positions shifted in the circumferential direction centered on the rotational axis L1.

[0142] Even when such a drive side flange 263 is used, the rotation of the drive transmission gear 81 in the I direction causes the drive transmission gear 81 to move to the balanced position, resulting in a backlash-free state as in the first embodiment. That is, the first main body gear part 81c meshes with the first gear part 263c, and receives the reaction force of the driving force FD and the thrust force F209 in the J direction from the contact point (contact part) CP1 of the first gear part 263c. The second main body gear portion 81d meshes with the second gear portion 263d, and receives the reaction force of the regulating force FB and the thrust force F210 in the H direction from the contact point (contact portion) CP2 of the second gear portion 263d. Also in this case, the drive transmission gear 81 is sandwiched between the first gear part 263c and the second gear part 263d of the drive side flange 263 in the axial rotation direction, so that a backlash-free state is achieved as in the first embodiment. .

[0143] [Example 3] Next, Example 3 will be described below using FIG. 32. This embodiment differs from Embodiment 1 in the configurations of the first gear section and the second gear section provided on the drive side flange. The other points are the same as those in Example 1, so explanations will be omitted.

[0144] FIG. 32 is a diagram showing the drive side flange 363. The drive side flange 363 has a first gear portion 363c and a second gear 363d1. The first gear part (first unit side gear part) 363c includes a plurality of first helical gears (first protrusions) 363ct that are divided into a plurality of parts in the direction of the rotation axis L1. Although the plurality of first helical gears (protrusions) 363ct are divided in the direction of the rotation axis L1, with respect to the first main body gear portion 81c, they are essentially one diagonal gear extending in the direction of the rotation axis L1. Functions as teeth. Further, the tooth surfaces of the plurality of first helical gears (protrusions) 363ct are a plurality of force receiving portions that receive force from the first main body gear portion 81c. Therefore, it can be said that the plurality of force receiving parts that receive the force from the first main body gear part 81c are provided over the plurality of first helical gears (first protrusions) 363ct. The tooth surfaces of the plurality of first helical gears (protrusions) 363ct constitute a plurality of bevel tooth surfaces divided in the direction of the rotation axis L1, or are centered on the rotation axis L1 of the drive side flange 363. It can be said that this constitutes a bevel tooth surface divided into a plurality of parts in the circumferential direction. In this way, the plurality of helical tooth-shaped protrusions 363ct constitute one tooth of the helical gear corresponding to one tooth of the first main body gear portion 81c.

[0145] The tooth surfaces of the plurality of second helical gears (protrusions) 363dt are a plurality of force receiving portions that receive force from the second main body gear portion 81d. Therefore, it can be said that the plurality of force receiving parts that receive the force from the second main body gear part 81d are provided over the plurality of second helical gears (second protrusions) 363dt. The second gear part (second unit side gear part) 363d includes a plurality of second helical gears (protrusions) 363dt that are divided into a plurality of parts in the direction of the rotation axis L1. Although the plurality of second helical gears (second protrusions) 363dt are divided in the direction of the rotational axis L1, with respect to the second main body gear portion 81d, the plurality of second helical gears (second protrusions) 363dt substantially extend in the direction of the rotational axis L1. Functions as two oblique teeth. In addition, the tooth surfaces of the plurality of second helical gears (protrusions) 363dt constitute a bevel tooth surface divided into a plurality of parts in the direction of the rotation axis L1, or the tooth surfaces of the plurality of second helical gears (protrusions) 363dt are arranged around the rotation axis L1 of the drive side flange 363. It can be said that the bevel tooth surface is divided into a plurality of parts in the circumferential direction. In this way, the plurality of helical tooth-shaped protrusions 363dt constitute one tooth of the helical gear corresponding to one tooth of the second main body gear portion 81d.

[0146] Therefore, even when such a drive side flange 363 is used, when the drive transmission gear 81 rotates in the I direction, the drive transmission gear 81 moves to the balanced position, and as in the first embodiment, a backlash-free state is achieved. Become.

[0147] [Example 4] Next, Example 4 will be described below using FIG. 33. This embodiment differs from Embodiment 1 in the configurations of the first gear section and the second gear section provided on the drive side flange. The other points are the same as those in Example 1, so explanations will be omitted.

[0148] The drive side flange 463 has two gear parts (a first unit side gear part and a second unit side gear part) similarly to the first gear part 63c and the second gear part 63d of the drive side flange 63 in the first embodiment. ing. At least one of the two gear parts has a missing tooth part (a part where gear teeth are apparently thinned out) 463L. FIG. 33(a) is a cross-sectional view of the drive side flange 463 and the drive transmission gear 81 that are engaged with each other and is perpendicular to the rotation axis L1. FIG. 33(b) is a graph showing changes in the number of teeth of gears that mesh with each other. Assuming that the engagement ratio between each gear part of the drive side flange 463 and each gear part of the drive transmission gear 81 is N teeth rounded down to the decimal point, each gear part of the drive side flange 463 has a maximum of every N-1 teeth. It does not matter if it has a tooth portion 463L. By satisfying this condition, even if the toothless portion 463L is present, there is one or more teeth that mesh with the drive transmission gear 81 (the meshing ratio is 1 or more). With this configuration, when the drive transmission gear 81 rotates in the I direction, the drive transmission gear 81 moves to the balanced position, resulting in a backlash-free state as in the first embodiment. Note that, as shown in FIG. 33(b), the number of gear teeth of the drive side flange 463 that meshes with each gear portion of the drive transmission gear 81 changes during driving.

[0149] [Example 5] Next, Example 5 will be described below using FIG. 34. This embodiment differs from Embodiment 1 in the configurations of the first gear section and the second gear section provided on the drive side flange. The other points are the same as those in Example 1, so explanations will be omitted.

[0150] The drive side flange 563 has two gear parts (a first unit side gear part and a second unit side gear part) similarly to the first gear part 63c and the second gear part 63d of the drive side flange 63 in the first embodiment. ing. At least one of the two gear parts has a missing tooth part 563L. FIG. 34(a) is a cross-sectional view of the drive-side flange 563 and the drive transmission gear 81 that are engaged with each other and is perpendicular to the rotation axis L1. FIG. 34(b) is a diagram showing changes in the number of teeth of gears that mesh with each other. As shown in FIG. 34(a), unlike the drive side flange 463 of Example 4, the teeth of the drive side flange 563 are not arranged at equal pitches in the circumferential direction. In other words, it can be said that the circumferential size of the plurality of missing teeth 563 is not constant, or that the apparent thinning amount of all the missing teeth 563 is not the same. In other words, it is sufficient that they are arranged in the rotational direction at intervals LI and LJ that are a natural number (1, 2, ...) times the minimum pitch LH between adjacent teeth. Even if such a missing tooth portion 563 is provided, it is sufficient if there is at least one tooth that meshes with each other (the meshing ratio is 1 or more). With this configuration, when the drive transmission gear 81 rotates in the I direction, the drive transmission gear 81 moves to the balanced position, resulting in a backlash-free state as in the first embodiment. Note that, as shown in FIG. 34(b), the number of teeth of the gears of the drive side flange 463 that mesh with each gear portion of the drive transmission gear 81 changes.

[0151] [Example 6] Next, Example 6 will be described below using FIG. 35. This embodiment differs from Embodiment 1 in the configurations of the first gear section and the second gear section provided on the drive side flange. Specifically, the first gear part 63c and the second gear part 63d of Example 1 were provided with helical teeth having an involute tooth profile, but this embodiment differs in that they are provided with helical teeth that are not an involute tooth profile. The other points are the same as those in Example 1, so explanations will be omitted.

[0152] FIG. 35 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 centered on the rotation axis L1, and the cross-sectional shape in a cross section perpendicular to the rotation axis L1 is a trapezoid whose width becomes narrower toward the tip. . Further, the first protrusion 763ct and the second protrusion 763dt are oblique teeth arranged to be twisted with respect to the rotation axis L1. Even in this configuration, the first gear portion 763c and the second gear portion 763d function as helical gears when meshing with the drive transmission gear 81. Therefore, when the drive transmission gear 81 rotates in the I direction, the drive transmission gear 81 moves to the balanced position, and becomes in a backlash-free state as in the first embodiment.

[0153] Note that the cross-sectional shape of the first protrusion 763ct and the second protrusion 763dt is not limited to a trapezoid, but may be a rectangle, a triangle, a chevron formed by a curved line, or a shape with chamfered corners.

[0154] [Example 7] Next, Example 7 will be described below using FIG. 36. This embodiment differs from Embodiment 1 in the configurations of the first gear section and the second gear section provided on the drive side flange. Specifically, compared to the first gear portion 63c and the second gear portion 63d of Example 1, the twist direction is reversed. Accordingly, the twist directions of the first main body gear portion and the second main body gear portion of the drive transmission gear were also reversed compared to the first embodiment. The other points are the same as those in Example 1, so explanations will be omitted.

[0155] FIG. 36 is a schematic diagram showing the engagement between the drive transmission gear 881 and the drive side flange 863. As shown in FIG. 36, the torsional direction of the first gear part (first unit side gear part) 863c and second gear part (second unit side gear part) 863d of the drive side flange 863 changes toward the J direction. This is the direction in which it is twisted so that it deviates toward the I direction. The first gear portion 881c and second gear portion 881d of the drive transmission gear 881 twist in such a direction that the tooth surfaces shift toward the K direction as they move toward the J direction.

[0156] Since the twisting direction is reversed compared to the first embodiment, the direction of the thrust force F21 due to the engagement applied to the drive transmission gear 881 while driving the drive transmission gear 881 is also opposite to that of the first embodiment. Therefore, when moving to the balanced position in the axial direction, a space with a width LK is required for the drive transmission gear 881 to move in the H direction. For this reason, a compression spring 185 is provided to bias the drive transmission gear 881 in the J direction, and 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. ing.

[0157] Even with such a configuration, when the drive transmission gear 881 rotates in the I direction, the drive transmission gear 881 moves to the balanced position, resulting in a backlash-free state as in the first embodiment.

[0158] [Example 8] Next, Example 8 will be explained using FIG. 37. This embodiment differs from Embodiment 1 in the configuration in which the cartridge B is attached to the apparatus main body. The other points are the same as those in Example 1, so the explanation will be omitted.

[0159] FIG. 37 is a perspective view of image forming apparatus 800. In this image forming apparatus 800, the insertion direction in which the cartridge B is inserted into the apparatus main body A is parallel or substantially parallel to the rotational axis L1 of the drum 62. Even if cartridge B is inserted in the direction parallel to the rotation axis L1, there is a distance between the drive side flange 63 and the drive transmission gear (not shown) of the device body A in the direction perpendicular to the rotation axis L1. , can't mesh. Thereafter, by closing the door 211, a lift-up mechanism (not shown) provided in the device main body A connected to the door 211 displaces the cartridge B at least in the direction VD perpendicular to the rotational axis L1, causing the drive side flange 63 and the device main body to move. It meshes with the drive transmission gear (not shown) in A.

[0160] The driving operation after the drive-side flange 63 and the drive transmission gear (not shown) mesh is the same as in the first embodiment, and the drive transmission gear moves to the balanced position, resulting in a backlash-free state as in the first embodiment.

[0161] Note that when the lift-up mechanism displaces the cartridge B in at least the direction VD perpendicular to the rotation axis L1, the cartridge B may be displaced not only in the direction perpendicular to the rotation axis L1 but also in the direction of the rotation axis L1. Alternatively, a lift-up mechanism may be used to rotate the cartridge B around an axis perpendicular to the rotational axis L1 and displace the drive side flange 63 in the direction VD perpendicular to the rotational axis L1.

[0162] In addition, instead of closing the door 211 and operating the lift-up mechanism after the cartridge B is inserted into the device main body A, it is possible to move the cartridge B in at least a direction perpendicular to the rotation axis L1 during the process of inserting the cartridge B into the device main body A. It may be displaced to VD. Specifically, at the initial stage of the insertion process of the cartridge B into the apparatus main body A, the cartridge B is guided by a guide (not shown) so as to move the cartridge B in a direction parallel to the rotation axis L1. Then, at the final stage of the insertion stroke, the cartridge B is guided by a guide (not shown) so that the cartridge B is displaced at least in the direction VD perpendicular to the rotational axis L1. In this way, the moving direction (mounting direction) of the cartridge B may be changed during the insertion process.

[0163] [Example 9] Next, Example 9 will be described below using FIG. 38. This embodiment differs from Embodiment 1 in the configurations of the first gear section and the second gear section provided on the drive side flange. Specifically, in this embodiment, the arrangement of the first gear section 963c and the second gear section 963d with respect to the direction of the rotation axis L1 is reversed from the first gear section 63c and the second gear section 63d of the first embodiment. Accordingly, the positions of the first main body gear portion and the second main body gear portion of the drive transmission gear in the direction of the rotation axis L1 were also reversed compared to the first embodiment. The other points are the same as those in Example 1, so explanations will be omitted.

[0164] FIG. 38 is a schematic diagram showing the engagement between the drive transmission gear 981 and the drive side flange 963. The drive side flange 963 has a first gear portion (first unit side gear portion) 963c and a second gear portion (second unit side gear portion) 963d. The torsion angle of the second gear part 963d is larger than the torsion angle of the first gear part 963c. The first gear portion 963c is arranged on the downstream side (drive side) in the J direction than the second gear portion 963d. That is, the second gear portion 963d is disposed 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 that meshes with the first gear portion 963c, and a second gear portion 981d that meshes with the second gear portion 963d. The positions of these also in the direction of the rotational axis L1 have a relationship opposite to that of the first embodiment.

[0165] Even with such a configuration, when the drive transmission gear 981 is driven, the drive transmission gear 981 moves to the balanced position. During subsequent driving, the first gear section 963c receives the driving force FD (see FIG. 17(d)), and the second gear section 963d receives the regulating force FB (see FIG. 17(d)), as in the first embodiment. and the state becomes backlash-free.

[0166] Here, the drive side (downstream side in the J direction) end of the drum unit 969 in which the drive side flange 963 and the drum 62 are integrated is rotatably supported by a shaft member 86 (see also FIG. 4). Furthermore, the first gear portion 963c is located closer to the root of the shaft member 86 than the second gear portion 963d. Further, in the drive side flange 963, the force applied to the tooth surface of the first gear portion 963c receiving the driving force FD is greater than that of the second gear portion 963d receiving the regulating force FB. Therefore, the driving force FD acts to tilt the rotational axis L1 of the drum unit 969, and the drum 62 may be tilted with respect to the ideal rotational axis L1. However, as in this embodiment, by arranging the first gear portion 963c that receives the driving force FD at a position closer to the root of the shaft member 86 than the second gear portion 963d, the problem caused by receiving the driving force FD Axis inclination of the rotational axis L1 of the drum unit 969 can be suppressed.

[0167] [Example 10] Next, Example 10 will be described below using FIG. 39. This embodiment differs from Embodiment 1 in the configurations of the first gear section and the second gear section provided on the drive side flange. Specifically, the positions and widths of the teeth in the direction of the rotation axis L1 of the first gear part 63c and the second gear part 63d in Example 1 were the same, but in this example, the positions and widths of the teeth in the direction of the rotation axis L1 were the same. The difference is that the positions and widths are not aligned. The other points are the same as those in Example 1, so explanations will be omitted.

[0168] FIG. 39 is a cross-sectional view of the meshing portion between the drive transmission gear 81 and the drive side flange 1063, and the cross section is a surface in contact with their meshing pitch circle. 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 oblique teeth (first protrusions) 1063ct having different widths and positions in the direction of the rotation axis L1. The second gear portion 1063d includes a plurality of second oblique teeth (second protrusions) 1063dt having different widths and positions in the direction of the rotation axis L1.

[0169] In the case of this configuration, the engagement ratio is different from the case where the drive side flange 63 of Example 1 is used, but the first gear part 1063c and the second gear part 1063d are the first gear part 63c and the second gear part 63d, respectively. Functions as a similar helical gear. Therefore, when the drive transmission gear 81 rotates in the I direction, the drive transmission gear 81 moves to the balanced position, and becomes in a backlash-free state as in the first embodiment.

[0170] [Example 11] Next, Example 11 will be described below using FIG. 40. This example differs from Example 1 in the configuration of the second gear portion provided on the drive side flange. Specifically, the second gear portion 63d in Example 1 was a helical gear, but this example differs in that it is a spur gear. The other points are the same as those in Example 1, so explanations will be omitted.

[0171] FIG. 40 is a cross-sectional view of the meshing portion of the drive transmission gear 81 and the drive side flange 1163, and the cross section is a surface in contact with the meshing pitch circle of these. 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 the first embodiment. The second gear portion 1163d includes a plurality of second spur teeth (teeth, second protrusions) 1163dt. The plurality of second spur teeth 1163dt are spur teeth of a size and width and thickness that can be inserted between the teeth (trough portion) of the second main body gear portion 81d of the drive transmission gear 81. Therefore, the width (tooth width) of the second spur tooth (second protrusion) 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 spur teeth (second protrusions) that are narrower than the first oblique teeth that have the widest width (tooth width) in the direction of the rotation axis L1 of the first gear portion 1163c. It has 1163dt.

[0172] Further, the rotational direction (I direction) or circumferential width (length) of the second protrusion 1163dt is greater than the rotational direction (I direction) or circumferential width (length) of one tooth of the first gear portion 1163c. It's also small. In other words, the second gear portion 1163d is wider in the rotational direction (I direction) or in the circumferential direction than the first helical tooth of the first gear portion 1163c, which has the widest width (length) in the rotational direction (I direction) or circumferential direction. It has a second protrusion 1163dt with a narrow width in the direction.

[0173] Further, the second protrusion 1163dt has a contact portion CP2 that contacts the second main body gear portion 81d. As shown in FIG. 40, the contact portion CP2 is provided at the corner of the second protrusion 1163dt. The corner (contact point CP2) is provided so that the corner (contact point CP2) contacts one tooth of the second main body gear portion 81d at only one location in the direction of the rotation axis L1. The radius of curvature of this corner can be set to a desired value, and by making the radius of curvature smaller, the corner may have a sharper shape. A gentle corner may be formed by increasing the radius of curvature.

[0174] When the drive transmission gear 81 is driven, the drive transmission gear 81 receives the thrust force F1109 in the J direction and moves in the J direction as in the first embodiment. Then, the surface 81d2 on the upstream side in the I direction of the second main body gear portion 81d contacts the contact portion CP2 of the second spur tooth 1163dt of the second gear 1163d, and receives the thrust force F1110 in the H direction. Therefore, the drive transmission gear 81 is positioned at the balanced position using the same principle as in the first embodiment, resulting in a backlash-free state. Furthermore, in the backlash-less state, regarding drive in the rotational direction, the first gear portion 1163c receives the driving force FD, and the second gear portion 1163d receives the regulating force FB at the contact portion CP2 of the second spur tooth 1163dt.

[0175] [Example 12] Next, Example 12 will be described below using FIG. 41. This example differs from Example 1 in the configuration of the second gear portion provided on the drive side flange. Specifically, the torsion angle of the second gear part 63d in Example 1 was larger than the torsion angle of the first gear part 63c, but the difference is that the torsion angle of the second gear part 1263d in this example is not. . The other points are the same as those in Example 1, so explanations will be omitted.

[0176] FIG. 41 is a sectional view of the meshing portion of the drive transmission gear 81 and the drive side flange 1263, and the cross section is a surface in contact with the meshing pitch circle of these. 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 the first embodiment. The second gear portion 1263d includes a plurality of second oblique teeth (teeth, second protrusions) 1263dt. The helix angle of the plurality of second helical teeth 1263dt is the same as the helix angle of the helical teeth of the first gear portion 1263c. Further, similar to the plurality of second diagonal teeth 1163dt of the eleventh embodiment, the plurality of second diagonal teeth 1263dt are large enough to be inserted between the teeth (trough portion) of the second main body gear portion 81d of the drive transmission gear 81. It is a diagonal tooth with a width and a tooth thickness. Therefore, the width (tooth width) of the second oblique tooth (second protrusion) 1263dt in the direction of the rotation axis L1 is smaller than the width (tooth width) of the first gear portion 1263c in the direction of the rotation axis L1. In other words, the second gear portion 1263d has a second diagonal tooth (second protrusion) that is narrower than the first diagonal tooth of the first gear portion 1263c, which has the widest width (tooth width) in the direction of the rotation axis L1. It has 1263dt.

[0177] In addition, the rotational direction (I direction) or circumferential width (length) of the second protrusion 1263dt is greater than the rotational direction (I direction) or circumferential width (length) of one tooth of the first gear portion 1263c. It's also small. In other words, the second gear portion 1263d is wider in the rotational direction (I direction) or in the circumferential direction than the first helical tooth of the first gear portion 1263c, which has the widest width (length) in the rotational direction (I direction) or circumferential direction. It has a second protrusion 1263dt with a narrow width in the direction.

[0178] Further, the second protrusion 1263dt has a contact portion CP2 that contacts the second main body gear portion 81d. As shown in FIG. 40, the contact portion CP2 is provided at the corner of the second protrusion 1263dt. The corner (contact point CP2) is provided so that the corner (contact point CP2) contacts one tooth of the second main body gear portion 81d at only one location in the direction of the rotation axis L1. The radius of curvature of this corner can be set to a desired value, and by making the radius of curvature smaller, the corner may have a sharper shape. A gentle corner may be formed by increasing the radius of curvature.

[0179] When the drive transmission gear 81 is driven, the drive transmission gear 81 moves in the J direction in response to the thrust force F1209 in the J direction, as in the first embodiment. Then, the surface 81d2 on the upstream side in the I direction of the second main body gear portion 81d contacts the contact portion CP2 of the second helical tooth 1163dt of the second gear portion 1263d, and receives the thrust force F1210 in the H direction. Therefore, the drive transmission gear 81 is positioned at the balanced position based on the same principle as in the first embodiment, resulting in a backlash-free state. Furthermore, in the backlash-less state, regarding drive in the rotational direction, the first gear portion 1263c receives the driving force FD, and the second gear portion 1263d receives the regulating force FB at the contact portion CP2 of the second helical tooth 1263dt.

[0180] [Example 13] Next, Example 13 will be described below using FIG. 42. This embodiment differs from Embodiment 1 in the configuration of the portion corresponding to the second gear portion provided on the drive side flange. Specifically, the second gear portion 63d in Example 1 was a helical gear, but this example differs in that it is a plurality of cylindrical protrusions. The other points are the same as those in Example 1, so the explanation will be omitted.

[0181] FIG. 42(a) is a perspective view of the drive side flange 1363. FIG. 42(b) is a sectional view of the meshing portion of the drive transmission gear 81 and the drive side flange 1363, and the cross section is a surface in contact with the meshing pitch circle of these.

[0182] The drive 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 first embodiment.

[0183] The second gear portion 1363d includes a plurality of cylindrical second protrusions (teeth) 1363dt that protrude in the radial direction centered on the rotation axis L1 from a tooth bottom cylindrical portion (base cylindrical portion) 1363Bd extending along the rotation axis L1. including. The second gear section 1363d is a rotating section that rotates integrally with the first gear section 1363c. The plurality of second protrusions 1363dt are arranged at the same position in the direction of the rotation axis L1 (on the same plane orthogonal to the rotation axis L1).

[0184] Furthermore, when viewed along the rotation axis L1, the tips S of the plurality of second protrusions 1363dt are arranged on a predetermined circumference centered on the rotation axis L1, and are arranged at equal intervals in the circumferential direction. There is. The tip circle of the second gear portion 1363d is the tip that is farthest from the rotation axis (rotation axis L1) of the second gear portion 1363d among the tips S of the plurality of second protrusions 1363dt when the drive side flange 1363 rotates. S is a circle drawn as a rotation locus. In this embodiment, since all the second protrusions 1363dt have the same shape, the distances of the tips S of all the second protrusions 1363dt from the rotation axis L1 are the same, so all the tips S follow the same rotation locus. draw. Further, the diameter / radius of the circle of this rotation locus is defined as the tip circle diameter / tooth tip circle radius of the second gear portion 1363d.

[0185] The plurality of second protrusions 1363dt are protrusions with a width in the direction of the rotation axis L1 and a width in the rotation direction (I direction) that are large enough to be inserted between the teeth (trough portion) of the second main body gear portion 81d of the drive transmission gear 81. It is. Therefore, the width of the second protrusion 1363dt in the direction of the rotation axis L1 is smaller than the width (tooth width) of the first gear portion 1363c in the direction of the rotation axis L1. In other words, the second gear portion 1363d has a second projection having a narrower width in the direction of the rotation axis L1 than the first diagonal tooth of the first gear portion 1363c which has the widest width (tooth width) in the direction of the rotation axis L1. It has 1363dt. Further, the rotational direction (I direction) or circumferential width (length) of the second protrusion 1363dt is greater than the rotational direction (I direction) or circumferential width (length) of one tooth of the first gear portion 1363c. It's also small. In other words, the second gear portion 1363d is wider in the rotational direction (I direction) or circumferentially than the first bevel tooth of the first gear portion 1363c, which has the widest width (length) in the rotational direction (I direction) or circumferential direction. It has a second protrusion 1363dt with a narrow width in the direction.

[0186] Further, the second protrusion 1363dt has a contact portion CP2 that contacts the second main body gear portion 81d. As shown in FIG. 42(b), the contact portion CP2 is provided on a curved portion of the surface of the second protrusion 1363dt. The curved portion on the surface of this second protrusion 1363dt can be said to be a corner. The corner (contact point CP2) is provided so that the corner (contact point CP2) contacts one tooth of the second main body gear portion 81d at only one location in the direction of the rotation axis L1. The radius of curvature of this corner can be set to a desired value; by making the radius of curvature smaller, the corner can be made sharper, or by increasing the radius of curvature, it can be made to be a gentler corner. .

[0187] When the drive transmission gear 81 is driven, the drive transmission gear 81 receives a thrust force in the J direction and moves in the J direction, as in the first embodiment. Then, the surface 81d2 of the second main body gear portion 81d 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 the thrust force F1310 in the H direction. Therefore, the drive transmission gear 81 is positioned at the balanced position based on the same principle as in the first embodiment, resulting in a backlash-free state. Furthermore, in the backlash-less state, regarding drive in the rotational direction, the first gear portion 1363c receives the driving force FD, and the second gear portion 1363d receives the regulating force FB at the contact portion CP2 of the second protrusion 1363dt.

[0188] Note that the second gear part 1363d can receive rotational driving force and / or thrust force by meshing with other gears such as the second main body gear part 81d using the plurality of second protrusions 1363dt. In this respect, it can be considered a kind of gear.

[0189] Further, the plurality of second protrusions 1363dt are not limited to a cylindrical shape, but may have any shape as long as they protrude at least in the radial direction centered on the rotation axis L1, and may be, for example, a polygonal column shape. Further, all the plurality of second protrusions 1363dt may not have the same shape.

[0190] [Example 14] Next, Example 14 will be described below using FIG. 43. This embodiment differs from Embodiment 1 in the configuration of a portion corresponding to the second gear portion provided on the drive side flange. Specifically, the second gear portion 63d in Example 1 was a helical gear, but this example differs in that it is a plurality of cylindrical protrusions. The other points are the same as those in Example 1, so the explanation will be omitted. Furthermore, when comparing this example and Example 13, only the arrangement of the plurality of cylindrical protrusions is different.

[0191] FIG. 43(a) is a cross-sectional view of the teeth and protrusions of the drive side flange 1463, and the cross section is a surface in contact with a circle centered on the rotation axis L1. FIG. 43(b) is a cross-sectional view of the meshing portion of the drive transmission gear 81 and the drive side flange 1463, and the cross section is a surface in contact with the meshing pitch circle of these.

[0192] The drive 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 1463c is the same as the first gear portion 63c of the first embodiment.

[0193] The second gear 1463d includes a plurality of cylindrical second protrusions 1463dt that protrude in a radial direction centered on the rotation axis L1. The second gear section 1463d is a rotating section that rotates integrally with the first gear section 1463c. The plurality of second protrusions 1463dt are arranged at shifted positions with respect to the direction of the rotation axis L1.

[0194] Furthermore, when viewed along the rotation axis L1, the tips S (see FIG. 42(a)) of the plurality of second protrusions 1463dt are arranged on a predetermined circumference centered on the rotation axis L1. The plurality of second protrusions 1463dt are protrusions with a width in the direction of the rotation axis L1 and a width in the rotation direction (I direction) that are large enough to be inserted between the teeth (trough portion) of the second main body gear portion 81d of the drive transmission gear 81. It is. Further, the plurality of second protrusions 1463dt are inserted between the teeth (trough portion) of the second main body gear portion 81d of the drive transmission gear 81, and receive the regulating force FB from the second main body gear portion 81d in a backlash-less state. It is placed in such a position that it can be Specifically, as shown in FIG. 43(a), a plurality of virtual torsion lines ( Draw a spiral line) L9 at a predetermined pitch P9. This pitch P9 is the same as the pitch of the plurality of second oblique teeth 81dt of the second body gear portion 81d of the drive transmission gear 81 in the direction perpendicular to the tooth surface. Then, the plurality of second protrusions 1463dt are arranged so as to satisfy the following conditions in relation to the plurality of twisted lines L9. The conditions are such that some of the plurality of twisted lines L9 touch some of the plurality of second protrusions 1463dt, and none of the plurality of twisted lines L9 passes within the cross section of the plurality of second protrusions 1463dt. , the condition is that a plurality of twisted lines L9 can be arranged. By arranging the plurality of second protrusions 1463dt so as to satisfy such conditions, the plurality of second protrusions 1463dt receive the regulating force FB from the second main body gear portion 81d in a backlash-less state. can perform the same function as the plurality of second protrusions 1363dt. In addition, as in the thirteenth embodiment, the corner (contact point CP2) of the second protrusion 1463dt is located at only one corner (contact point CP2) with respect to one tooth of the second main body gear portion 81d in the direction of the rotation axis L1. The contact points CP2) are arranged so that they touch each other.

[0195] When the drive transmission gear 81 is driven, as shown in FIG. 43(b), the drive transmission gear 81 receives the thrust force F1409 and moves in the J direction, as in the first embodiment. Then, the surface 81d2 on the upstream side in the I direction of the second main body gear portion 81d contacts the contact portion CP of the second protrusion 1463dt of the second gear portion 1463d, and receives the thrust force F1410 in the H direction. Therefore, the drive transmission gear 81 is positioned at the balanced position based on the same principle as in the first embodiment, resulting in a backlash-free state. Furthermore, in the backlash-less state, regarding drive in the rotational direction, the first gear portion 1463c receives the driving force FD, and the second gear portion 1463d receives the regulating force FB at the contact portion CP2 of the second protrusion 1463dt.

[0196] Note that the second gear portion 1463d can receive rotational driving force and / or thrust force by meshing with other gears such as the second main body gear portion 81d using the plurality of second protrusions 1463dt. In this respect, it can be considered a kind of gear.

[0197] Further, the plurality of second protrusions 1463dt are not limited to a cylindrical shape, but may have any shape as long as they protrude at least in the radial direction centered on the rotation axis L1, and all the plurality of second protrusions 1463dt do not have to have the same shape. good.

[0198] [Example 15] Next, Example 15 will be described using FIG. 45. The drive transmission structure within cartridge B is different from that of the first embodiment. FIG. 45(a) is a partial sectional view of the cartridge B near the drum 62 at a cross section including the rotational axis L1. FIG. 45(b) is a view of the drum 62 and the developing roller 632 of the cartridge B as viewed in a direction perpendicular to the rotational axis L1.

[0199] The gear that meshes with the drive transmission gear 81 does not need to be integrally fixed to the end of the drum 62. As shown in FIG. 45(a), a driven gear 1563 that meshes with the drive transmission gear 81 is rotatably supported at both ends by a shaft 1578 fixed to one end of a cleaning frame 1571. In other words, the shaft 1578 supports the driven gear 1563 while passing through the driven gear 1563. The driven gear 1563 includes a first gear part (first unit It has a side gear part) 1563c, and a second gear part (second unit side gear part) 1563d, which is a helical gear with a helical angle α2. Furthermore, a developing roller gear 630 that meshes with the second gear portion 1563d of the driven gear 1563 is integrally provided at one end of the developing roller 632, and a drum driving gear 92 is provided at the other end of the developing roller 632. It is integrated with the Further, a drum gear 93 that meshes with a drum drive gear 92 is integrally attached to one end of the drum 62 by caulking or the like, and is rotatably supported by a drum shaft. Further, a drum flange 1564 is attached to the other end of the drum by caulking or the like, and is rotatably supported by a shaft 1578. With this configuration, 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 driving gear 92, and the drum gear 93.

[0200] [Example 16] Next, Example 15 will be described below using FIG. 48. This example differs from Example 1 in the configuration of the portions corresponding to the first gear portion and the second gear portion provided on the drive side flange. Specifically, the first gear part 63c and the second gear part 63d in Example 1 were helical gears, but in this example, each gear part was formed with a plurality of protrusions (the gear part 63c and the second gear part 63d were formed with a plurality of protrusions). The difference is in the structure of each tooth of the part. The other points are the same as those in Example 1, so explanations will be omitted.

[0201] FIG. 48(a) is a cross-sectional view of the teeth and protrusions of the drive side flange 1663, and the cross section is a surface in contact with a circle centered on the rotation axis L1. FIG. 48(b) is a cross-sectional view of the meshing portion of the drive transmission gear 81 and the drive side flange 1663, and the cross section is a surface in contact with the meshing pitch circle of these.

[0202] The first gear part (first unit side gear part, first unit side helical gear part) 1663c has a radius centered on the rotation axis L1 from the bottom cylindrical part (base cylinder part) extending along the rotation axis L1. It includes a plurality of cylindrical first protrusions 1663ct that protrude in the direction. The plurality of first protrusions 1663ct are arranged at the same position and at shifted positions with respect to the direction of the rotation axis L1.

[0203] Furthermore, when viewed along the rotation axis L1, the tips S (see FIG. 42(a)) of the plurality of first protrusions 1663ct are arranged on a predetermined circumference centered on the rotation axis L1. The plurality of first protrusions 1663ct are protrusions with a width in the direction of the rotational axis L1 and a width in the rotational direction (I direction) that are large enough to be inserted between the teeth (trough portion) of the first main body gear portion 81c of the drive transmission gear 81. It is. Further, the plurality of first protrusions 1663dt are inserted between the teeth (trough portion) of the first main body gear portion 81c of the drive transmission gear 81, and receive the driving force FD from the first main body gear portion 81c in a backlash-less state. It is placed in such a position that it can be Specifically, as shown in FIG. 48(a), a plurality of virtual torsion lines ( Draw a spiral line) L15 at a predetermined pitch P11. This pitch P11 is the same as the pitch of the plurality of first oblique teeth 81ct of the first body gear portion 81c of the drive transmission gear 81 in the direction perpendicular to the tooth surface. Then, the plurality of first protrusions 1663dt are arranged so as to satisfy the following conditions in relation to the plurality of twist lines L5. The conditions are such that some of the plurality of twisted lines L15 touch some of the plurality of first protrusions 1663ct, and none of the plurality of twisted lines L11 passes within the cross section of the plurality of first protrusions 1663ct. , the condition is that a plurality of twisted lines L11 can be arranged. By arranging the plurality of first protrusions 1663ct to satisfy such conditions, the plurality of first protrusions 1663dt mesh with the first main body gear part 81c in a backlash-less state, rotate, and receive the driving force FD. It can perform this function.

[0204] 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 in a radial direction centered on the rotation axis L1. The second gear section 1663d is a rotating section that rotates integrally with the first gear section 1663c. The plurality of second protrusions 1663dt are arranged at shifted positions with respect to the direction of the rotation axis L1.

[0205] Furthermore, when viewed along the rotation axis L1, the tips S (see FIG. 42(a)) of the plurality of second protrusions 1663dt are arranged on a predetermined circumference centered on the rotation axis L1. The plurality of second protrusions 1663dt are protrusions with a width in the direction of the rotational axis L1 and a width in the rotational direction (I direction) that are large enough to be inserted between the teeth (trough portion) of the second main body gear portion 81d of the drive transmission gear 81. It is. Further, the plurality of second protrusions 1663dt are inserted between the teeth (trough portion) of the second main body gear portion 81d of the drive transmission gear 81, and receive the regulating force FB from the second main body gear portion 81d in a backlash-less state. It is placed in such a position that it can be Specifically, as shown in FIG. 48(a), a plurality of virtual torsion lines ( Draw a spiral line) L14 at a predetermined pitch P10. This pitch P10 is the same as the pitch of the plurality of second oblique teeth 81dt of the second main body gear portion 81d of the drive transmission gear 81 in the direction perpendicular to the tooth surface. Then, the plurality of second protrusions 1663dt are arranged so as to satisfy the following conditions in relation to the plurality of twisted lines L14. The conditions are such that some of the plurality of twisted lines L14 touch some of the plurality of second protrusions 1663dt, and none of the plurality of twisted lines L14 passes within the cross section of the plurality of second protrusions 1663dt. , the condition is that a plurality of twisted lines L14 can be arranged. By arranging the plurality of second protrusions 1663dt to satisfy such conditions, the plurality of second protrusions 1663dt mesh with and rotate with the second main body gear part 81d in a backlash-less state and receive the regulating force FB. , can perform the same function as the plurality of second protrusions 1363dt of the thirteenth embodiment.

[0206] As shown in FIG. 48(b), when the drive transmission gear 81 is driven, the drive transmission gear 81 moves in the J direction as in the first embodiment. This is because the first main body gear portion 81c contacts the plurality of first protrusions 1663ct and receives thrust force in the J direction. The drive transmission gear 81 that has moved in the J direction finally makes contact with the contact portion CP2 of the second protrusion 1663dt of the second gear portion 1663d with the upstream surface 81d2 of the second main body gear portion 81d in the I direction, and the drive transmission gear 81 moves in the H direction. Receives thrust force F1610. Further, the downstream side surface 81c1 in the I direction of the first main body gear portion 81c contacts the contact portion CP1 of the first protrusion 1663ct of the first gear portion 1663c, and receives thrust force F1609 in the J direction. Therefore, the drive transmission gear 81 is positioned at the balanced position based on the same principle as in the first embodiment, resulting in a backlash-free state. In addition, in the backlash-less state, regarding drive in the rotational direction, the first gear portion 1663c receives the driving force FD, and the second gear portion 1663d receives the regulating force FB at the contact portion CP of the second protrusion 1463dt.

[0207] Note that the first gear portion 1663c can receive rotational driving force and / or thrust force by meshing with other gears such as the first main body gear portion 81d using the plurality of first protrusions 1663ct. In this respect, it can be regarded as a type of gear (slanted gear). In other words, the surfaces of the plurality of first protrusions 1663ct (the plurality of contact parts CP1) constitute a beveled tooth surface divided into a plurality of parts in the direction of the rotation axis L1, or the surfaces of the plurality of first protrusions 1663ct are centered on the rotation axis L1 of the drive side flange 1663. It can be said that the bevel tooth surface is divided into a plurality of parts in the circumferential direction.

[0208] Therefore, by connecting the plurality of contact parts CP1, a twisted line L15 can be defined. The plurality of first protrusions 1663ct are arranged so that they can each contact one tooth of the first main body gear portion 81c at a plurality of locations spaced apart in the direction of the rotation axis L1. It can also be said that a plurality of contact parts CP1 that can simultaneously contact one tooth of the first main body gear part 81c are provided at positions separated from each other in the direction of the rotation axis L1. In this way, it can be said that the plurality of first protrusions 1663ct arranged separately in the direction of the rotation axis L1 constitute one tooth (oblique tooth) that meshes with one tooth of the first main body gear portion 81c. Therefore, the plurality of first protrusions 1663ct function as a helical gear, and the first gear portion 1663c is a first helical gear portion.

[0209] In addition, the circle drawn as a rotation locus when the tip (point) farthest from the rotation axis L1 among the tips of the plurality of first protrusions 1663ct rotates is the tip circle of the first gear portion 1663c, and the diameter of that circle is The diameter of the tip of the tooth.

[0210] Similarly, the second gear part 1663d can receive rotational driving force and / or thrust force by meshing with other gears such as the second main body gear part 81d using the plurality of second protrusions 1663dt. , in this respect it can be considered a kind of gear. In other words, the surfaces of the plurality of second protrusions 1663dt (the plurality of contact parts CP2) constitute a beveled tooth surface divided into a plurality of parts in the direction of the rotation axis L1, or the surfaces of the plurality of second protrusions 1663dt form a bevel tooth surface divided into a plurality of parts in the direction of the rotation axis L1, or It can be said that the bevel tooth surface is divided into a plurality of parts in the circumferential direction.

[0211] Therefore, by connecting the plurality of contact parts CP2, a twisted line L14 can be defined. The plurality of second protrusions 1663dt are arranged so that they can each contact one tooth of the second main body gear portion 81d at a plurality of locations spaced apart in the direction of the rotation axis L1. It can also be said that a plurality of contact parts CP2 that can simultaneously contact one tooth of the second main body gear part 81d are provided at positions separated from each other in the direction of the rotation axis L1. In this way, it can be said that the plurality of second protrusions 1663dt arranged separately in the direction of the rotation axis L1 constitute one tooth (oblique tooth) that meshes with one tooth of the second main body gear portion 81d. Therefore, the plurality of second protrusions 1663dt function as a helical gear, and the second gear portion 1663d is a second helical gear portion.

[0212] In addition, the circle drawn as a rotation locus when the tip (point) farthest from the rotation axis L1 among the tips of the plurality of second projections 1663dt rotates is the tip circle of the second gear portion 1663d, and the diameter of the circle is The diameter of the tip of the tooth.

[0213] Furthermore, each of the plurality of first protrusions 1663ct and the plurality of second protrusions 1663dt is not limited to a cylindrical shape, but may have any shape as long as it protrudes at least in the radial direction centering on the rotation axis L1. Further, the plurality of first protrusions 1663ct may not be a plurality of completely separated protrusions, although they include a plurality of contact portions CP1. For example, a cross-sectional shape in a tangential direction perpendicular to the radial direction centering on the rotation axis L1 may have a step-like shape in which some parts are connected. The same applies to the plurality of second protrusions 1663dt. Moreover, all the plurality of first protrusions 1663ct do not have to have the same shape, and all the plurality of second protrusions 1663dt do not have to have the same shape either.

[0214] [Example 17] Example 17 differs from Example 1 in the following points. First, the layout of each component within the apparatus main body A into which the cartridge B is installed is different. As a result, the posture of the cartridge B within the apparatus main body A is different. Further, the support configuration of the drive side flange 1763 and the engagement configuration between the drive transmission gear 1781 and the idler gear 1780 are different. Further, the configuration for transmitting the drive to the developing roller 1732 is the same as in <Other modifications> of the first embodiment. Further, the positional relationship in the axial direction of the first gear section receiving the driving force FD and the second gear section receiving the regulating force FB is the same as in the ninth embodiment. Other points are the same as in Example 1, and detailed explanation will be omitted. Furthermore, among the elements in this example, the elements (e.g. drum 1762) that correspond to the elements of example 1 (e.g. drum 62) are associated with the corresponding elements of example 1. (e.g. "1762" which corresponds to "62"). Items that are not specifically explained regarding these elements are the same as the corresponding elements of Example 1.

[0215] <Device main body configuration> FIG. 50 is a cross-sectional view (the cross section is perpendicular to the rotational axis L1) of the apparatus main body A in which the cartridge B is installed. The apparatus main body A of the image forming apparatus 17100 includes an exposure device (laser scanner unit) 1703 and a sheet tray 1704 that stores the sheet material PA. Further, the apparatus main body A includes a pickup roller (not shown), a pair of conveyance rollers 1705b, a transfer guide 1706, a transfer roller 1707, a conveyance guide 1708, a fixing device 1709, a pair of discharge rollers 1710, It has an ejection tray 1711.

[0216] <Position of cartridge B inside device body A> As shown in FIG. 50, the cartridge B is positioned in the apparatus main body A with the cleaning unit 1760 and the developing unit 1720 arranged substantially horizontally. At this time, a transfer roller 1707 is placed below the drum 1762.

[0217] <Support structure of drum unit 1769 by cleaning unit 1760> Next, regarding the support structure of the drum unit 1769 by the cleaning unit 1760, FIG. 51(a), FIG. 51(b), FIG. 52(a), FIG. 52(b), FIG. This will be explained using

[0218] FIG. 51(a) is an exploded perspective view of the cleaning unit 1760, showing the cleaning unit 1760 viewed from the developing unit side so that the inside of the drum bearing member 1773 is visible. FIG. 51(b) is an exploded perspective view of the cleaning unit 1760, showing the cleaning unit 1760 viewed from the developing unit side so that the outside of the drum bearing member 1773 is visible. FIG. 52(a) is a perspective view of the drum bearing member 1773 viewed from inside. FIG. 52(b) is a cross-sectional view of the guided portion 1773g of the drum bearing member 1773 that supports the drive side flange 1763 taken along a cross section orthogonal to the rotational axis L1. However, this cross-sectional view shows a state in which the cross section is viewed from inside the drum bearing member 1773. FIG. 52(c) shows the vicinity of the drive-side flange 1763 of cartridge B installed in apparatus main body A, which includes the rotation axis L1 and is orthogonal to the mounting direction M of cartridge B into apparatus main body A (see FIG. 57). FIG. 3 is a sectional view taken along a cross section. FIG. 58 is a diagram showing a cross section of the cleaning unit 1760 and the drive transmission gear 1781 viewed from outside the drum bearing member 1773, and the cross section is a hole 1773d of the drum bearing member 1773 that supports the drive side flange 1763. This is a cross section that passes through and is orthogonal to the rotational axis L1. FIG. 59 is a partial perspective view of the vicinity of the drive side flange 1763 of the cartridge B.

[0219] As shown in FIGS. 51(a) and 51(b), the cleaning unit 1760 includes a frame member 1771 and a drum bearing member 1773 fixed to the frame member 1771, which is a drum frame supporting a drum 1762. be. The drive side flange 1763 is provided on the outside (downstream side in the J direction) of the end surface of the first gear part 1763c with respect to the rotational axis L1 so as to protrude from the end of the drive side flange 1763 toward the downstream side in the J direction. It also includes a cylindrical protrusion (supported part) 1763g centered on the rotation axis L1. The drum bearing 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 FIGS. 52(a) and 52(b), the inner peripheral surface of the hole 1773d has two flat surfaces 1773e, 1773f and two circumferential surfaces 1773h, 1773i, each parallel to the rotation axis L1. Further, the two planes 1773e and 1773f are not parallel to each other, but are arranged so as to have a substantially V-shaped concave shape when viewed from the direction of the rotation axis L1. The plane 1773e and the plane 1773f are support surfaces (support portions) having support points that contact and support the protrusion 1763g. As shown in FIG. 58, the approximately V-shaped concave shape composed of two planes 1773e and 1773f is caused by the meshing force on the tooth surfaces of the gears when driving force is transmitted from the drive transmission gear 1781 to the drive side flange 1763. In order to receive the force of FG, it is provided in the direction opposite to the force FH, which is parallel to the force FG starting from the rotational axis L1. Specifically, it is provided so that the force FH is substantially parallel to the bisector of the angle formed by the extension line of the plane 1773e and the extension line of the plane 1773f when viewed along the rotation axis L1. There is. Note that the directions of the two planes 1773e and 1773f are not limited to this, and may be set by comprehensively considering various forces that apply loads to the drive side flange 1763.

[0220] After the drum unit 1769 is assembled inside the frame member 1771, the drum bearing member 1773 is attached and fixed to the frame member 1771, so that the protrusion 1763g of the drive side flange 1763 fits inside the hole 1773d of the drum bearing member 1773. . Thereby, the drum unit 1769 is rotatably supported by the frame member 1771 and the drum bearing member 1773. In addition, as shown in FIG. 59 and FIG. 114(b), in the completed state of cartridge B, part of the drive side flange 1763 (part of the first gear part 1363c and second gear part 1363d) and the drum 1762 A portion is not covered by the drum frame (drum bearing member 1773 and frame member 1771) and is exposed to the outside of cartridge B. In other words, the drum frame has an opening to expose a portion of the drive side flange 1763 (a portion of the first gear portion 1363c, a portion of the second gear portion 1363d, etc.) and a portion of the drum 1762 to the outside. It can also be said that it has a part.

[0221] As shown in FIG. 52(c), when the cartridge B is installed in the apparatus main body A, the circular arc surface of the guided part 1773g is aligned with the two positioning parts 1715a of the first drive-side side plate 1715 of the apparatus main body A. The position of the rotational axis L1 of the cartridge B with respect to the apparatus main body A is determined with respect to the two directions (mounting direction M and orthogonal direction MP perpendicular to the mounting direction M) that are in contact and perpendicular to the rotational axis L1 (see FIG. 57). The guided portion 1773g is a protruding portion that protrudes outward (in the J direction) in the direction of the rotation axis L1, and the above-described hole 1773d is provided inside the guided portion 1773g. Note that the apparatus main body A is provided with a pressing member (not shown) that presses the cartridge B so as to press the guided portion 1773g toward the two positioning portions 1715a. Further, the meshing force FG on the tooth surfaces of the gears when the driving force is transmitted from the drive transmission gear 1781 to the drive side flange 1763 also acts to press the guided portion 1773g toward the two positioning portions 1715a. . Further, the force with which the transfer roller 1707 (see FIG. 50) as a transfer section presses the drum 1762 also acts to press the guided section 1773g toward the positioning section 1715a in the orthogonal direction MP.

[0222] 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 at 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 plane portions 1773f and 1773e, and at least a portion of the protrusion 1763g are arranged on a certain plane orthogonal to the rotation axis L1. This arrangement can suppress deformation of the drum bearing 1773 such that it is inclined with respect to the rotational axis L1, and it is possible to suppress inclination (fall) of the drive side flange 1763 with respect to the rotational axis L1. As a result, deterioration in the meshing accuracy between the drive side flange 1763 and the drive transmission gear 1781 can be suppressed. In addition, by abutting the protrusion 1763g against the two plane parts 1773f and 1773e, the play in the fitting can be reduced in one direction (the extension line of the plane 1773e and the extension line of the plane 1773f when viewed along the rotational axis L1). The positional accuracy of the drive side flange 1763 in the direction orthogonal to the rotation axis L1 is improved, and deterioration of the meshing accuracy with the drive transmission gear 1781 can be suppressed. can.

[0223] In this embodiment, the protrusion 1763g is formed integrally with the drive-side flange 1763, but the protrusion 1763g may be made of a separate component such as metal and press-fitted into the drive-side flange 1763.

[0224] Next, positioning of the drive side flange 1763 in the axial direction will be explained. As shown in FIGS. 51(a) and 51(b), the first gear portion 1763c of the drive side flange 1763 has a protruding portion 1763c1 that slightly protrudes in the H direction on the end face on the downstream side in the H direction, and A protruding portion 1763f that slightly protrudes in the J direction is provided on the end face on the downstream side (upstream side in the H direction). Further, the frame member 1771 includes a rib 1771p and a side wall 1771m provided to extend in a direction perpendicular to the rotation axis L1. The protrusion 1763c1 can contact the side surface of the rib 1771p, and the protrusion 1763f can contact the side surface of the side wall 1771m. The drive side flange 1763 is fitted and held with a clearance fit between the rib 1771p and the side wall 1771m so as to be slidable in the direction of the rotation axis L1. As a result, the drive side flange 1763 is positioned on the frame member 1771 with respect to the direction of the rotation axis L1, and as a result, the position of the drum unit 1769 within the frame member 1771 is determined.

[0225] <Attachment and removal of cartridge B to and from device body A, and positioning within device body A> Figure 113(a) is a diagram of the cartridge B installed in the device main body A installed on a horizontal installation surface, viewed in the direction along the rotation axis L1 (K direction), where the horizontal direction is HD and the vertical direction is is shown as VD. Note that the plane perpendicular to the rotation axis L1 is parallel to the vertical direction VD. FIG. 113(b) is a diagram of the cartridge B viewed along the HD1 direction parallel to the horizontal direction HD shown in FIG. 113(a). FIG. 114(a) is a diagram of cartridge B viewed along the VD1 direction parallel to the vertical direction VD shown in FIG. 113(a). FIG. 114(b) is a view of cartridge B viewed along the VD2 direction parallel to the vertical direction VD shown in FIG. 113(a). Note that when viewed along the direction of the rotation axis L1, as can be seen from FIG. 50, the mounting direction M is approximately 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). be. Therefore, the mounting direction M in the following description can be read as a direction that is perpendicular to the rotation axis L1 and parallel to a straight line connecting the rotation center of the developing roller 1732 and the rotation center (rotation axis L1) of the photosensitive drum 1762.

[0226] As in Example 1, the mounting direction M of the cartridge B into the apparatus main body A and the direction of removing it from the apparatus main body A (opposite direction to the mounting direction M) are directions substantially perpendicular to the rotational axis L1. Further, the direction in which the drum unit 69 is attached to the apparatus main body A and the direction in which it is removed from the apparatus main body A are the same as the direction M in which the cartridge B is attached to the apparatus main body A and the direction in which it is removed from the apparatus main body A, respectively.

[0227] As shown in FIG. 113(a), the drum bearing member 1773 is provided with a guided portion 1773s1, a guided portion 1773s2, and a guided portion 1773s3 in addition to the guided portion 1773g described above. These guided portions are protruding portions that protrude from the main body portion of the drum bearing member 1773 in the direction of the rotation axis L1. When the cartridge B is installed in the apparatus main body A and when it is taken out from the apparatus main body A, it comes into contact with a guide section (not shown) provided on the apparatus main body A and is guided. Note that, as shown in other figures, the guided portion 1773s1 may be omitted. The guided portion 1773s3 may also be omitted in consideration of necessity. However, installing and removing the cartridge B is more stable when the guided portion 1773s1 and the guided portion 1773s3 are provided. The guided portion 1773s1 is elongated in the mounting direction M (or along a direction perpendicular to the rotation axis L1 and parallel to a straight line connecting the rotation center of the developing roller 1732 and the rotation center of the photosensitive drum 1762 (rotation axis L1). It is a long protrusion. The rigidity of the drum bearing member 1773 is increased by forming the guided portion 1773s1 as an elongated protrusion in this manner. Further, although the guided portion 1773s1 and the guided portion 1773g are provided as one connected protrusion, they may be provided as separate protrusions. However, the rigidity of the drum bearing member 1773 increases when it is provided as one continuous protrusion.

[0228] Furthermore, as mentioned earlier, when the cartridge B is installed in the apparatus main body A, the guided part 1773g contacts the two positioning parts 1715a of the apparatus main body A, and the guided part 1773g contacts the two positioning parts 1715a of the apparatus main body A, and The position of the rotational axis L1 of the cartridge B with respect to the apparatus main body A is determined with respect to the direction MP orthogonal to M (see FIGS. 52(c) and 57). Furthermore, the guided portion 1773s2 comes into contact with a positioning portion of the device main body A (not shown), thereby determining the position (posture) of the cartridge B with respect to the device main body A with respect to the rotational direction about the rotation axis L1.

[0229] Further, the positioning of the cartridge B with respect to the apparatus main body A in the direction of the rotation axis L1 is the same as in the first embodiment. Specifically, as shown in FIGS. 113(b) and 114(a), the drum bearing member 1773 has a concave fitting portion 1773h recessed along the mounting direction M, and the device body is inserted here. A convex fitting portion protruding along a mounting direction M (not shown) of A is fitted, and the position of the cartridge B with respect to the apparatus main body A in the direction of the rotation axis L1 is determined.

[0230] Further, as shown in FIG. 113(a), the drum bearing member 1773 has a developing unit support portion 1773b having a substantially cylindrical surface shape extending in the direction of the rotation axis L1. The developing unit support section 1773b rotates (swings) the cylindrical section 1721a, which is arranged to surround the developing coupling member 1789 and the coupling section 1789a of the frame 1721 of the developing unit 1720, around the rotation axis DA. support possible. The rotation axis DA is coaxial with the rotation axis of the developer coupling member 1789 and parallel to the rotation axis L1. The developing unit 1720 receives force from a force applying section (not shown) of the apparatus main body A at the force receiving section 1721b of the frame 1721 of the developing unit 1720, and thereby rotates the DS about the rotation axis DA relative to the cleaning unit 1760. It is possible to rotate (swing) in the direction. This rotation allows the developing roller 1732 to be separated from the drum 1762.

[0231] Furthermore, as shown in FIG. 113(a), when looking at the cartridge B from the direction of the rotation axis L1, the guided portion 1773s2 is arranged on the straight line LT passing through the rotation axis L1 and the rotation axis DA. In the parallel direction, the developing unit support portion 1773b and the rotation axis DA are arranged between the rotation axis L1 and the guided portion 1773s2. Therefore, the cleaning unit 1760 can firmly support the relatively heavy developing unit 1760. Therefore, the mounting direction M (or the longitudinal direction of the guided part 1773s1), the orthogonal direction MP perpendicular to the mounting direction M (or the direction perpendicular to the longitudinal direction of the guided part 1773s1), the horizontal direction HD, and the vertical direction VD. In any direction, it can be said that the developing unit support portion 1773b and the rotation axis DA are arranged between the rotation axis L1 and the guided portion 1773s2.

[0232] Furthermore, when looking at cartridge B from the direction of rotation axis L1, if we divide the areas by straight line LT, guided part 1773s1 is placed in one area and guided part 1773s3 is placed in the other area, so cartridge B The posture of cartridge B is stabilized during installation and removal.

[0233] Furthermore, as shown in FIGS. 113(b), 114(a), and 114(b), the drum frame of the cleaning unit 1760 includes the drum bearing member (first bearing member) 1773 and the frame member 1711. In addition, it has a non-drive side drum bearing member (second bearing member) 1712 attached to the frame member 1711. As described above, in the drum unit 1769, the drive side flange 1763 (first flange member) is rotatably supported by the drum bearing member 1773. On the other hand, a non-drive side flange (second flange member) 1764 of the drum unit 1769 is rotatably supported by a non-drive side drum bearing member 1712. Note that the non-drive side flange 1764 is a member fixed to the downstream end of the drum 1762 in the H direction. That is, the drum bearing member (first bearing member) 1773 is arranged at the first end of the drum frame in the direction of the rotation axis L1, and the second end of the frame opposite to the first end of the frame A non-drive side drum bearing member (second bearing member) 1712 is arranged at the end. Of the two ends of the drum 62 in the direction of the rotational axis L1, the first end of the photoreceptor is located closer to the first end of the frame than the second end of the frame. The second end of the photoreceptor opposite to the first end of the body is located closer to the second end of the frame than the first end of the frame. As can be seen from FIGS. 114(a) and (b), it has a protruding shaped portion 1712a that protrudes downstream in the mounting direction M of the non-drive side drum bearing member 1712. Here, when viewed along the direction of the rotation axis L1, as can be seen from FIG. 50, the mounting direction M is approximately parallel. Therefore, the protruding shaped portion 1712a is attached to the drum bearing member 1773 or the drum 1762 with respect to the direction perpendicular to the rotation axis L1 and from the rotation center of the developing roller 1732 to the rotation center of the photosensitive drum 1762 (direction substantially parallel to the mounting direction M). It has a shape that protrudes further downstream. A memory board 1740 on which a nonvolatile memory chip is mounted is attached to the protruding portion 1712a. The memory board 1740 has an electrode part (electrode surface) 1740a, which is a surface that is electrically connected to the nonvolatile memory chip and can be electrically connected by contacting a main body side electrode part (not shown) of the device main body A. Be prepared. The electrode portion 1740a is located on the opposite side (non-drive side) from the end (first frame end) on the side where the drum bearing member 1773 and the drive-side flange 1763 are arranged (drive side) with respect to the direction of the rotation axis L1. The frame is located near the end of the frame (the end of the second frame body). Specifically, with respect to the direction of the rotation axis L1, the area where the electrode portion 1740a is arranged is an area including the position of the downstream end of the drum 1762 in the H direction (the second end of the photoreceptor). However, with respect to the direction of the rotation axis L1, the area where the electrode part 1740a is arranged is outside the drum frame (or the cartridge B It may be placed at a position close to (outside of) (a position on the downstream side in the H direction). Furthermore, with respect to the direction of the rotation axis L1, the region where the electrode portion 1740a is arranged and the region where the non-drive side flange 1764 is arranged are at least partially in the same position (at least partially overlap). However, with respect to the direction of the rotation axis L1, the area where the electrode part 1740a is placed is located 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 placed (in the H direction). (downstream position). Further, the electrode portion 1740a is arranged downstream of the rotation axis L1 and the photosensitive drum 1762 in the mounting direction M. Further, the electrode portion 1740 is arranged from the rotation axis L1 or the photosensitive drum 1762 in a direction perpendicular to the rotation axis L1 and 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). is also located downstream. Furthermore, the memory board 1740 is supported by the cleaning unit 1760 in a posture such that the electrode portion (electrode surface) 1740a is oriented perpendicular to the mounting direction M.

[0234] <Drive side flange 1763> Next, the drive side flange 1763 will be explained using FIG. 54(b) and FIG. 60. FIG. 54(b) is a schematic cross-sectional view of the gear portion of the drive side flange 1763. Its cross section is in contact with the meshing pitch circle when meshing with the drive transmission gear 1781. 60(a) and (b) are cross-sectional views of the vicinity of the drive-side flange 1763 of the drum unit 1769, and the cross-section includes the rotation axis L1.

[0235] The drive side flange 1763 has a first gear part (first unit side gear part, first unit side helical gear part) 1763c as a helical gear part and a second gear part (second unit side gear part, second unit Equipped with a coaxial side diagonal tooth gear part) 1763d. The first gear portion 1763c is arranged upstream in the H direction (downstream in the J direction) than the second gear portion 1763d. That is, the second gear section 1763d is arranged between the first gear section 1763c and the drum 1762 in the direction of the rotation axis L1. The first gear part 1763c includes a plurality of first oblique teeth (teeth, first protrusions) 1763ct arranged at different positions in the circumferential direction around the rotation axis L1, and the second gear part 1763d has the center around the rotation axis L1. It includes a plurality of second oblique teeth (teeth, second protrusions) 1763dt arranged at different positions in the circumferential direction. Note that the first oblique tooth 1763ct and the second oblique tooth 1763dt are both involute teeth and protrusions that protrude in the radial direction centered on the rotation axis L1. The first gear portion 1763c and the second gear portion 1763d are integrally molded with resin and rotate integrally. Therefore, the first gear portion 1763c and the second gear portion 1763d are the first rotating portion that rotates integrally with each other. , it can also be seen as the second rotating section. The first gear portion 1763c meshes with the first main body gear portion 1781c of the drive transmission gear 1781, and the second gear portion 1763d meshes with the second main body gear portion 1781d of the drive transmission gear 1781.

[0236] The first gear portion 1763c and the second gear portion 1763d of the drive side flange 1763 twist in the same direction, and are twisted so that the tooth surfaces shift toward the K direction as they move toward the J direction. Note that the twisting direction of the first gear portion 1763c and the second gear portion 1763d is opposite to the twisting direction of the first main body gear portion 1781c and the second main body gear portion 1781d of the drive transmission gear 1781. Further, similar to the first embodiment, the torsion angle of the second gear portion 1763d is larger than the torsion angle of the first gear portion 1763c. The torsion angle of the first gear part 1763c is the same as the torsion angle of the first main body gear part 1781c, which will be described later, and the torsion angle of the second gear part 1763d is the same as the torsion angle of the second main body gear part 1781d, which will be described later. be. Further, the first gear portion 1763c and the second gear portion 1763d of the drive side flange 1763 have the same number of teeth.

[0237] In addition, as shown in Fig. 60(a), the width (tooth width) Wc of the first oblique tooth (teeth, first protrusion) 1763ct in the direction of the rotation axis L1 is the same as that of the second oblique tooth (teeth, second protrusion) It is larger than the width (tooth width) Wd in the direction of the rotation axis L1 of 1763dt. In other words, the first gear part 1763c and the second gear part 1763d each have a width Wc of the first diagonal tooth (teeth, first protrusion) 1763ct and a width Wc of the second diagonal tooth (teeth, second protrusion) in the direction of the rotation axis L1. )1763dt and has at least one tooth whose face width Wd satisfies the following formula A1. Wc>Wd...(Formula A1)

[0238] While the drive side flange 1763 is being 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 regulating force FB received by the second gear portion 1763d. It is preferable to have such a relationship.

[0239] In addition, the width (meshing width) of the rotation axis L1 of the part where the first gear part 1763c meshes (contacts) with the first main body gear part 1781c, and the meshing of the second helical gear part 1763c with the second main body gear part 1781d. The larger the width, the better the drive transmission accuracy. However, if the engagement width is set larger than necessary, the width of the first gear section 1763c and the second gear section 1763c in the direction of the rotation axis L1 becomes large, which affects the driving side flange 1763, drum unit 1769, cartridge B, and eventually the apparatus main body A. becomes large. Therefore, the tooth width Wc1 of the first diagonal tooth (teeth) 1763ct having the widest tooth width in the first gear portion 1763c and the tooth width Wc1 of the second diagonal tooth (teeth) 1763dt having the widest tooth width in the second gear portion 1763d. It is preferable that the face width Wd1 satisfies the following formula A2, more preferably formula A3. Wd1≦(4 / 5)·Wc1···(Formula A2) Wd1≦(3 / 4)·Wc1···(Formula A3)

[0240] Furthermore, from the viewpoint of the strength of the second diagonal tooth (teeth) 1763dt of the second gear portion 1763d, it is preferable that the second diagonal tooth (teeth) 1763dt have a tooth width of a certain degree or more, and the tooth width Wc1 and the tooth width It is preferable that Wd1 satisfies the following formula A4. Wd1≧(1 / 10)·Wc1···(Formula A4)

[0241] Furthermore, the width (length) We of the cylindrical portion 1763e (or gap g) in the direction of the rotational axis L1 is calculated by the following formulas B1, B2, And, it is set to satisfy formula B3. Note that when the tooth width Wc of the first gear portion 1763c is not constant, the tooth width Wc1 of the tooth with the widest tooth width is assumed to be the tooth width Wc. We≧Wc / 5...(Formula B1) We≦Wc...(Formula B2) We≦Wd...(Formula B3)

[0242] In this embodiment, the tooth width of each tooth of the first gear part 1763c is all the same, and the tooth width of each tooth of the second gear part 1763c is all the same, and the tooth width Wc is 8.2 mm and the tooth width Wd is 5.2 mm. It is set to . Also, the width We is set to 3.1mm.

[0243] Furthermore, as shown in FIG. 60(b), the meshing pitch circle diameters D63c and D63d of the first gear part 1763c and the second gear part 1763d in the meshing between the drive side flange 1763 and the drive transmission gear 1781 are almost the same. It is set as follows. Similarly, the meshing pitch circle diameters of the first main body gear portion 1781c and the second main body gear portion 1781d are set to be approximately the same. As a result, the meshing between the first gear portion 1763c and the first main body gear portion 1781c and the meshing between the second gear portion 1763d and the second main body gear portion 1781d can be properly meshed without contacting the tooth tips. can.

[0244] In addition, as in the first embodiment, the tooth tip circle diameter of the first gear portion 1763c is adjusted so that the meshing with the first main body gear portion 1781c and the second main body gear portion 1781d is appropriate without contacting the tooth tips. Dt63c and the root diameter Db63d of the second gear portion 1763d are set to be approximately the same.

[0245] Specifically, the size of the tip diameter Dt63c of the first gear portion 1763c is larger than the root diameter Db63d of the second gear portion 1763d, or the tip diameter Dt63d of the second gear portion 1763d. It is preferable to set the value to a value larger than 0.8 times (more preferably 0.9 times). Further, the size of the tip diameter Dt63c of the first gear portion 1763c is preferably set to a value smaller than 1.1 times the tip diameter Dt63d of the second gear portion 1763d.

[0246] Furthermore, it is preferable that the size of the root diameter Db63c of the first gear portion 1763c is set to a smaller value than the tip diameter Dt63d of the second gear portion 1763d. Further, it is preferable that the size of the tooth bottom circle diameter Db63c of the first gear portion 1763c is set to a value larger than 0.9 times the tooth root circle diameter Db63d of the second gear portion 1763d.

[0247] Further, the size of the tip diameter Dt63d of the second gear portion 1763d is a value larger than the root diameter Db63c of the first gear portion 1763c, or 0.8 times the tip diameter Dt63c of the first gear portion 1763c ( It is preferable to set the value to be larger than (more preferably 0.9 times). Further, the size of the tip diameter Dt63d of the second gear portion 1763d is preferably set to a value smaller than 1.1 times the tip diameter Dt63c of the first gear portion 1763c.

[0248] Furthermore, it is preferable that the size of the root diameter Db63d of the second gear portion 1763d is set to a smaller value than the tip diameter Dt63c of the first gear portion 1763c. Further, it is preferable that the size of the tooth bottom circle diameter Db63d of the second gear portion 1763d is set to a value larger than 0.9 times the tooth root circle diameter Db63c of the first gear portion 1763c.

[0249] In this example, the tip diameter Dt63c, pitch diameter D63c, and bottom diameter Db63c of the first gear portion 1763c were set to 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 were set to 22.1 mm, 21.1 mm, and 19.8 mm, respectively. Further, the diameter of the cylindrical portion 1763e was set to 17.5 mm.

[0250] In addition, the module is arranged between the first gear part 1763c and the second gear part 1763d so that the meshing pitch circle diameters D63c and D63d are the same while the helix angles of the first gear part 1763c and the second gear part 1763d are different. They are made different, and the amount of metastasis is changed. Note that for the drive transmission gear 1781, the modules are similarly made different between the first main body gear section 1781c and the second main body gear section 1781d, and the amount of displacement is changed.

[0251] Further, the drive side flange 1763 includes a cylindrical portion (intermediate portion, small diameter portion, shaft portion) 1763e between the first gear portion 1763c and the second gear portion 63d in the direction of the rotation axis L1. The maximum diameter D63e of the cylindrical portion 1763e centered on the rotational axis L1 is smaller than the tip diameter Dt63c of the first gear portion 1763c and the tip diameter Dt63d of the second gear portion 1763d. Further, in this embodiment, the maximum diameter D63e of the cylindrical portion 1763e centered on the rotation axis L1 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, the maximum diameter D63e of the cylindrical portion 1763e centered on the rotational axis L1 is not limited to the above unless the drive side flange 1763 comes into contact with the drive transmission gear 1781 while being driven by the drive transmission gear 1781. Note that, as will be explained later in Examples 22 and 23, the distance from the rotation axis L1 to the outer diameter of the cylindrical portion 1763e is such that the drive side flange 1763 and the drive transmission gear 1781 can mesh with each other and transmit the driving force. The distance (radius) R63e may be configured to be smaller than the tip circle radius Rt63ct of the first gear portion 1763c or the tip circle radius Rt63d of the second gear portion 1763d, at least temporarily.

[0252] It is obvious that the relationship between the dimensions of the first gear portion 1763c, the second gear portion 1763d, and the cylindrical portion 1763e is expressed using various diameters, and the relationship is the same even if the diameter is replaced with a radius.

[0253] <Drive transmission gear 1781> Next, the drive transmission gear 1781 of the device main body A that meshes with the drive side flange 1763 will be explained using FIG. 53 and FIG. 54(a). 53(a) and (b) are exploded perspective views of the drive transmission gear 1781 and surrounding portion of the device main body A, with (a) being viewed from the second drive side plate 1783 side, and (b) being the main frame body. Shown is the state seen from the 1784 side. FIG. 54(a) is a schematic cross-sectional view of the gear portion of the drive transmission gear 1781. The cross section is a cross section that is in contact with the meshing pitch circle when meshing with the driving side flange 1763.

[0254] The drive transmission gear 1781 includes a first main body gear part (first main body helical gear part) 1781c and a second main body gear part (second main body helical gear part) 1781d coaxially as a helical gear part. The first main body gear section 1781c is disposed on the upstream side in the H direction (downstream in the J direction) with respect to the second main body gear section 1781d. The first main body gear portion 1781c includes a plurality of first main body bevel teeth 1781ct, and the second main body gear portion 1781d includes a plurality of second main body bevel teeth 1781dt. Note that the first main body bevel teeth 1781ct and the second main body bevel teeth 1781dt are both involute teeth. The first main body gear portion 1781c and the second main body gear portion 1781d are integrally molded with resin and rotate integrally. Further, the twisting directions of the first main body gear portion 81c and the second main body gear portion 81d are the same direction, and the tooth surfaces are twisted in such a manner that the tooth surfaces shift toward the I direction as they move toward the J direction. Further, as in Example 1, the torsion angle of the second body gear portion 1781d is larger than the torsion angle of the first body gear portion 1781c. Further, the first main body gear portion 81c and the second main body gear portion 81d have the same number of teeth. With the cartridge B attached to the apparatus main body A, the first gear part 1763c meshes with the first main body gear part 1781c, and the second gear part 1763c meshes with the second main body gear part 1781d.

[0255] Note that FIG. 112 is a perspective view of another configuration example of the drive transmission gear 1781. As shown in FIG. 112, with respect to the direction of the rotational axis L2, a rib-shaped portion (a protruding portion, A radially protruding main portion) 1781p may be provided. Depending on the manufacturing method of the drive transmission gear 1781, providing the rib-shaped portion 1781p may improve molding accuracy, suppress deterioration, or reduce manufacturing costs. There is. The diameter of the rib-shaped portion 1781p is approximately the same as the tip circle diameter of the first main body gear portion 1781c and the tooth tip circle diameter of the second main body gear portion 1781d. The rib-shaped portion 1781p may be provided over the entire circumference in the circumferential direction centering on the rotation axis L2, or may be provided only on a part of the circumference. Here, since the drive side flange 1763 is provided with the cylindrical part 1763e, there is a gap g between the first gear part 1763c and the second gear part 1763d in the direction of the rotation axis L1 (see FIG. 60, etc.) is formed. Because of this gap g, even if the drive transmission gear 1781 has the rib shaped part 1781p, contact between the rib shaped part 1781p and the drive side flange 1763 is avoided, and the drive transmission gear 1781 and the drive side flange 1763 are prevented from coming into contact with each other. The gear parts of the two can mesh properly with each other. At this time, the rib-shaped portion 1781p is inserted (entered) into the gap g between the first gear portion 1763c and the second gear portion 1763d.

[0256] As shown in FIGS. 53(a) and (b), the device main body A includes a motor (not shown), an idler gear 1780, a drive transmission gear 1781, a second drive side plate 1783, a main frame 1784, a drive shaft 1782, and reinforcement. It has a member 1798 and a compression spring 1785. The second drive-side side plate 1783 is a member corresponding to the second drive-side side plate 83 of the first embodiment. The driving force from the motor is transmitted to the drive transmission gear 1781 via the idler gear 1780. The idler gear 1780, the drive transmission gear 1781, and the reinforcing member 1798 are rotatable coaxially about the rotation axis L2, and are supported by a fixed drive shaft 1782 so as to be movable in the direction of the rotation axis L2. . The drive shaft 1782 has one end fixed to the second drive side plate 1783, and the other end 1782b fitted into a hole 1784a of the main frame 1784 and supported. The drive shaft 1782 is provided so that the rotation axis L2 of the drive transmission gear 1781 is parallel to the rotation axis L1 of the drum 62 when the cartridge B is attached to the apparatus main body A.

[0257] A compression spring 1785 is provided between the other end 1780b of the idler gear 1780 and the second drive side plate 1783, and the idler gear 1780 is biased toward the main frame 1784 (in the H direction) in the direction of the rotation axis L2. There is. A recess 1780a recessed in the direction of the rotation axis L2 is provided at the end of the idler gear 1780 facing the drive transmission gear 1781, and a protrusion (driving force transmission portion) 1780a1 is provided inside the recess 1780a.

[0258] At the end of the drive transmission gear 1781 that faces the idler gear 1780, a protrusion 1781a1 that protrudes in the direction of the rotation axis L2 is provided at a location that faces the recess 1780a1 of the idler gear 1780. The protrusion 1781a1 has a surface 1781e at the upstream end in the rotation direction I, and a slope 1781h at the downstream end. The surface 1781e is perpendicular to the surface perpendicular to the rotation axis L2, and the slope 1781h is inclined to the surface perpendicular to the rotation axis L2. When the protrusion 1780a1 of the idler gear 1780 and the surface 1781e of the protrusion 1781a1 engage with each other, driving force is transmitted from the idler gear 1780 to the drive transmission gear 1781, which rotates integrally in the rotation direction I.

[0259] On the other hand, when the drive transmission gear 1781 rotates in the rotation direction I relative to the idler gear 1780, the slope 1781h of the projection 1781a1 of the drive transmission gear 1781 comes into contact with the projection 1780a1 of the idler gear 1780. As a result, a force is applied to the idler gear 1780 and the drive transmission gear 1781 in the direction of separating them from each other 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, so that the protrusion 1780a1 becomes the protrusion. 1781a1, and the driving force in the rotational direction I is not transmitted from the drive transmission gear 1781 to the idler gear 1780. In the process of attaching cartridge B to apparatus main body A, drive transmission gear 1781 may engage drive side flange 1763 and rotate in rotational direction I. At this time, due to the above-mentioned configuration, drive transmission gear 1781 is connected to idler gear. The driving force in rotational direction I is not transmitted to 1780. Therefore, when the user installs cartridge B, there is no need to rotate the motor that drives the idler gear 1780 or rotate the photosensitive drum 1762, so there is no need to rotate the motor that drives the idler gear 1780 or rotate the photosensitive drum 1762. can be reduced.

[0260] Further, the drive transmission gear 1781 has a hole 1781f, and an engaging portion 1781g configured with a plurality of concave and convex shapes is provided on the inner peripheral portion of the hole 1781f. The reinforcing member 1798 is provided with an engaging portion 1798b having a plurality of concave and convex shapes on its outer circumference, and is inserted into the hole 1781f. An engaging portion 1781g of the drive transmission gear 1781 and an engaging portion 1798b of the reinforcing member 1798 are 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 via the reinforcing member 1798. However, the drive transmission gear 1781 may be configured to be directly supported by the drive shaft 1782.

[0261] However, when manufacturing a relatively large-diameter drive transmission gear 1781 by resin molding as in this embodiment, it is better to support the drive shaft 1782 via the reinforcing member 1798 as shown in this example. This is advantageous in terms of achieving both molding precision and strength. When a gear with a relatively large radial wall thickness (radial distance from the inner peripheral surface of the hole through which the shaft passes to the bottom circle of the gear) is constructed from a single resin molded member, resin sinks, etc. This is because it is necessary to provide a hollowed-out shape in order to avoid deterioration of gear molding accuracy due to the above. If a hollow shape is provided, the strength of the gear may be reduced. Therefore, as in this embodiment, the drive transmission gear 1781 is not directly supported by the drive shaft 1782, but is provided with a separate reinforcing member 1798 molded with resin. While suppressing deterioration of molding accuracy, it is also possible to suppress a decrease in strength.

[0262] <Drive transmission operation> Next, the meshing operation between the drive transmission gear 1781 and the drive side flange 1763 will be explained using FIGS. 54 and 55. 54(c), FIG. 54(d), FIG. 55(a), FIG. 55(b), and FIG. 55(c) show the meshing portion of the gear portion of the drive transmission gear 1781 and the gear portion of the drive-side drum flange 1763. FIG. Note that the cross section is a cross section that is in contact with the meshing pitch circle between the drive transmission gear 1781 and the drive side flange 1763. 54(c), FIG. 54(d), FIG. 55(a), FIG. 55(b), and FIG. 55(c) all show the state after the drive transmission gear 1781 starts to be driven, in this order. Shown in chronological order.

[0263] First, when the cartridge B is not attached to the main body A, the drive transmission gear 1781 is urged in the H direction by the compression spring 1785 and abuts against the main frame 1784, as shown in FIG. 54(a).

[0264] <Operation after start of drive> After the cartridge B is attached to the main body A, the drive transmission gear 1781 is driven by the motor (not shown) of the apparatus main body A via the idler gear 1780 (see FIG. 53), and rotates in the I direction. The drive side flange 1763 receives a driving force from the drive transmission gear 1781 that rotates in the I direction and rotates in the K direction.

[0265] Immediately after the drive transmission gear 1781 starts rotating in the I direction, as shown in FIG. 54(c), the second body gear portion 1781d of the drive transmission gear 1781 first meshes with the second gear portion 1763d of the drive side flange 1763 and is driven. The case where force FD is transmitted will be explained. The second main body gear portion 1781d generates a thrust force that presses 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 FIG. 51(a)), and receives a reaction force in the J direction corresponding to the thrust force in the H direction. Therefore, the second body gear portion 1781d receives thrust force F5 in the J direction due to the reaction force received from the second gear portion 1763d. This thrust force F5 causes the drive transmission gear 1781 to move in the J direction.

[0266] As the rotation continues and the drive transmission gear 1781 moves in the J direction, the first gear part 1763c also meshes with the first main body gear part 1781c, transmitting the driving force FD, as shown in FIG. 54(d). At the same time, thrust force F6 is generated in the first main body gear portion 1781c. The thrust force F6 is a thrust force in the J direction that is the same as the thrust force F5 that the second main body gear portion 1781d previously received by meshing with the second gear portion 1763d. As a result, the drive transmission gear 1781 further moves in the J direction.

[0267] When the drive transmission gear 1781 rotates further and moves in the J direction, the second main body gear portion 1781d eventually ceases to mesh with the second gear portion 1763d, as shown in FIG. 55(a). On the other hand, the first gear portion 1781c and the first gear portion 1763c maintain meshing, and a thrust force F8 acts on the first gear portion 1781c in the J direction. At this time, the drive transmission gear 81 transmits the driving force FD only by meshing the first main body gear part 1781c and the first gear part 1763c, and rotates the drive side flange 1763.

[0268] When the rotation continues and the drive transmission gear 1781 moves in the J direction, the second main body gear part 1781d finally moves in the I direction of the second gear part 1763d, as shown in FIGS. 55(b) and (c). It contacts the downstream tooth surface (contact part) 1763d2. Note that the surface 1781c1 of the first main body gear portion 1781c and the surface 1763c1 of the first gear portion 1763c maintain contact. That is, the teeth of the first gear part 1763c are in contact with the first main body gear part 1781c disposed on the upstream side in the I direction, and the teeth of the second gear part 1763d are in contact with the second main body gear part 1781c disposed on the downstream side in the I direction. In contact with section 1781d. Moreover, since the first gear part 1763c and the second gear part 1763d are integrally molded with resin, the teeth of the first gear part 1763c move in the I direction relative to the teeth of the second gear part 1763d ( The teeth of the second gear part 1763d are fixed so that they cannot move (rotate) in the direction opposite to the I direction relative to the teeth of the first gear part 1763c. Therefore, in this state, the first main body gear portion 1781c of the drive transmission gear 1781 presses the tooth surface (contact portion) 1763c1 with the tooth surface 1781c1 to rotate the drive side flange 1763, and the second main body gear of the drive transmission gear 1781 The tooth surface 1781d2 of the portion 1781d comes into contact with the tooth surface 1763d2, thereby being sandwiched between the driving side flange 1763. Then, the movement of the drive transmission gear 1781 in the direction of the rotation axis L1 is stopped. The position of the drive transmission gear 1781 in the direction of the rotational axis L1 at this time is defined as the balance position.

[0269] In the balanced state, as shown in FIG. 55(b), force F9, force F10, and force F1 are applied to drive transmission gear 1781 in the direction of rotation axis L1. Force F9 is the thrust force in the J direction that the first main body gear portion 1781c receives due to the meshing force with the first gear portion 1763c, and force F10 is the H thrust force that the second main body gear portion 1781d receives due to the meshing force with the second gear portion 6173d. The thrust force in the direction, force F1, is the biasing force of the compression spring 1785 received via the idler gear 1780. Further, the drive side flange 1763 receives a force from the drive transmission gear 1781, contacts the rib 1771p or the side wall 1771m, and is positioned in the direction of the rotation axis L1, and is positioned in the direction of the rotation axis L1 that balances the thrust force received from the drive transmission gear 1781. A reaction force F11 is generated. FIG. 55(b) shows a case where the drive side flange 1763 is positioned by contacting the rib 1771p. In the balanced state, if friction is ignored in the direction of the rotation axis L1, force F9, force F10, force F1, and force F11 are balanced, and the drive transmission gear 1781 and the drive side flange 1763 are moved in the direction of the rotation axis L1, respectively. It is in a state where it is positioned in the direction.

[0270] In addition, in the balanced state, as shown in FIG. 55(c), the drive side flange 1763 is sandwiched between the first main body gear part 1781c and the second main body gear part 1781d of the drive transmission gear 1781 in the K direction (rotation direction). It is in a state where it receives the following force (by contacting it). In other words, the tooth surface (contact portion) 1763c1 of the first gear portion 1763c contacts the first main body gear portion 1781c disposed on the upstream side in the K direction (first circumferential direction), thereby moving the drive side flange 1763 to the K direction. It receives a driving force FD as a force component in the direction of rotation (predetermined direction). At the same time, the tooth surface (contact part) 1763d2 of the second gear part 1763d comes into contact with the second main body gear part 1781d disposed downstream in the K direction (first circumferential direction), thereby causing the K It receives a regulating force (braking force) FB as a component force in the direction that suppresses (regulates) rotation in the direction. Therefore, it can be said that the first gear part 1763c is a driving force receiving part that receives the driving force FD, and the second gear part 1763d is a regulating force receiving part that receives the regulating force FB. Note that FIG. 55(b) shows the reaction force FF of the driving force FD received by the first main body gear portion 1781c and the reaction force FE of the regulating force FB received by the second main body gear portion 1781d.

[0271] Further, immediately after the drive transmission gear 1781 starts rotating in the I direction, if the first main body 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, The state shown in FIG. 54(d) or FIG. 55(a) is reached. After that, in the same way as described above, the drive transmission gear 1781 moves in the J direction toward the drive side while transmitting the driving force FD to the first gear part 1763c, and FIGS. 55(b) and 55(c) ) transitions to the balanced state shown in ).

[0272] In this way, also in this embodiment, when the first gear section 1763c receives the driving force FD and the second gear section 1763d receives the regulating force FB, the rotation occurs between the drive side flange 1763 and the drive transmission gear 1781. This is a state in which there is no play (backlash) in the direction (I direction), that is, a backlash-free state. In this way, the drive side flange 1763 is rotationally driven in the K direction while maintaining the backlash-free state. While meshing and transmitting drive in a backlash-free state, drive transmission with high rotational accuracy is possible.

[0273] Further, in the direction of the rotation axis L1, the first gear portion 1763c is located closer to the protrusion 1763g, which is a supported portion supported by the plane 1773e and the plane 1773f, than the second gear portion 1763d. In the drive side flange 1763, the force applied to the tooth surface of the first gear portion 1763c receiving the driving force FD is greater than that of the second gear portion 1763d receiving the regulating force FB. Therefore, the driving force FD acts to tilt the rotational axis L1 of the drum unit 1769, and the drum 1762 may be tilted with respect to the ideal rotational axis L1. However, as in this embodiment, by arranging the first gear portion 1763c that receives the driving force FD at a position closer to the protrusion 1763g that is the supported portion than the second gear portion 1763d, it is possible to receive the driving force FD. It is possible to suppress the axis tilting of the rotation axis L1 of the drum unit 1769 caused by this.

[0274] <Drive transmission configuration to developing roller 1732> Further, the configuration for transmitting the driving force to the developing roller 1732 in this embodiment engages with the coupling member of the apparatus main body A described in <Other Modifications> of Embodiment 1 with reference to FIG. This configuration is similar to the configuration in which driving force is transmitted to the developing roller 532 via the inputted developing coupling member 89.

[0275] The specific configuration will be explained using FIGS. 56 and 57. FIG. 56(a) is a perspective view of a drive train that drives the developing roller 1732 of the developing unit 1720. FIG. 56(b) is a partial perspective view of the vicinity of the coupling member 1789 of the developing unit 1720. FIG. 56(c) is a perspective view of cartridge B. FIG. 57 is a partial perspective view of the main body A of the main body side coupling member 1799 and its vicinity.

[0276] The developing unit 1720 includes a developing coupling member 1789 including a coupling portion 1789a and a gear portion 1789b, which constitute a developing drive train that drives the developing roller 1732, an idler gear 1790 that meshes with the gear portion 1789b, an idler gear 1791 that meshes with the idler gear 1790, and , has a developing roller gear 1730 fixed to one end of the shaft portion of the developing roller 1732 and meshing with an idler gear 1791.

[0277] In the apparatus main body A, a main body side coupling member 1799 driven by a motor (not shown) is supported by a first driving side plate 1715. The main body side coupling member 1799 is provided so as to be movable in the direction of the rotation axis. When the main body side coupling member 1799 and the coupling portion 1789a of the developer coupling member 1789 are engaged and rotate together, driving force is transmitted from the main body side coupling member 1799 to the developer coupling member 1789. be done. The driving force is then transmitted from the developer coupling member 1789 to the idler gears 1790, 1791, and the developer roller gear 1730 in this order to the developer roller 1732.

[0278] Further, the developing unit 1720 is provided with a toner moving member (stirring member) (not shown) that stirs or transports the toner in the toner storage container, and the driving force received by the developing coupling member 1789 is transmitted through another gear. The power is transmitted to the toner moving member of the lever to drive the toner moving member.

[0279] Note that the member driven by the driving force from the developer coupling member 89 is not limited to the above-mentioned developer roller 1732 and the toner moving member (not shown), but also any member other than the drum unit 1769 included in the cartridge B (for example, a charging member, a seal). members, cleaning members, etc.). In this way, the member to which the driving force is transmitted from the developing coupling member 1789 (the member connected to the developing coupling member 1789 so that driving force can be transmitted) is not limited to the developing roller 1732.

[0280] In this way, the apparatus main body A includes two systems of driving force output means, the drive transmission gear 1781 and the main body side coupling member 1799, as a driving force output means to the cartridge B. This allows control such as driving one of the drive transmission gear 1781 and the main body side coupling member 1799 while stopping the drive of the other. As a specific example, the developing roller 1732 can be controlled to be driven while the drum 1762 is stopped.

[0281] Further, in the cartridge B, the drive side flange 1763 is not included in a member that is connected to the developer drive train that drives the developer roller 1732 or the developer coupling member 1789 so that driving force can be transmitted. Therefore, even if the user rotates the drum 1762 in a state where the cartridge B is removed from the apparatus main body A, the member connected to the developing roller 1732 or the developing coupling member 1789 so as to be able to transmit a driving force will not rotate the drum 1762. It is suppressed from being driven in accordance with the rotation. Therefore, it is possible to reduce the possibility that a member connected to the developing roller 1732 or the developing coupling member 1789 so as to be able to transmit driving force will be driven unnecessarily, resulting in toner leakage or the like.

[0282] As described above, in this embodiment, the developing roller 1732 is driven by the driving force input to the developing coupling member 1789, but as in the first embodiment, the driving force is applied from the driving side flange 1763 to the developing roller gear 1730. A configuration may also be adopted in which the developing roller 1732 is driven by transmission.

[0283] As explained above, according to this embodiment, the same effects as in the first embodiment can be obtained. Further, the elements of each embodiment described above can be applied to the configuration of this embodiment. In particular, the configurations of the first oblique tooth (first protrusion) 1763ct of the first gear portion 1763c of the drive side flange 1763 and the second oblique tooth (second protrusion) 1763dt of the second gear portion 1763d are modified in Examples 2, 3, and 4. , 5, 6, 10, 11, 12, 13, 14, 16 may be used instead.

[0284] [Example 18] This example differs from Example 17 in that a ring-shaped elastic member is provided to cover the drive side flange 1763. Other points are the same as in Example 17, and detailed explanation will be omitted. Furthermore, among the elements in this example, the elements corresponding to the elements in Example 1 are given the reference numerals associated with the corresponding elements in Example 1. Items that are not specifically explained regarding these elements are the same as the corresponding elements of Example 1.

[0285] FIG. 61 is a partial perspective view of the vicinity of the drive side flange 1863 of the drum unit 1869. FIG. 62 is a cross-sectional view of the second gear portion 1863d and the second main body gear portion 1881d, and the cross section is perpendicular to the rotation axis L1.

[0286] The drive side flange 1863 has the same shape as the drive side flange 1763 of the seventeenth embodiment. In this embodiment, an elastic ring 1801, which is a ring-shaped elastic member that can be elastically deformed, is provided to cover the entire or part of the outer periphery of the second gear portion (second unit side gear portion) 1863d.

[0287] The elastic ring 1801 is made of a thin film of rubber or sponge, and the thickness is desirably about 0.01 to 1 mm if it is made of rubber, such as nitrile rubber, or about 1 to 6 mm if it is made of sponge. Furthermore, it is desirable that the inner diameter of the elastic ring before being attached to the drive side flange 1863 is approximately 0.5 to 0.9 times the outer diameter of the second gear portion 1863d. In this example, the outer diameter of the second gear portion 1863d was 20 mm, and the inner diameter of the elastic ring 1801 was 14 mm. When the outer diameter of the second gear portion 1863d is Φ20 mm, the inner diameter of the elastic ring 1801 is desirably selected appropriately within the range of Φ10 mm to 18 mm, which is slightly smaller than the Φ20 mm. If it is larger than Φ18 mm, it may come off from the second gear part 1863d, and if it is smaller than Φ10 mm, the force that tightens the second gear part 1863d is strong, and the second gear part 1863d may be deformed.

[0288] As shown in FIG. 62, when the cartridge B is attached to the main body A of the apparatus, the elastic ring 1801 is elastically deformed, and the second helical tooth 1863dt of the second gear portion 1863d and the second helical tooth 1781dt of the drive transmission gear 81 are connected to each other. The second gear portion 1863d and the second main body gear portion 1781d are in mesh with each other via the elastic ring 1801. Further, the first gear portion (first unit side gear portion) 1863c meshes with the first main body gear portion 1781c.

[0289] When the drive transmission gear 1781 rotates in the direction of arrow I, force is transmitted from the second main body gear section 1781d to the second gear section 1863d via the elastic ring 1801. Therefore, the second gear section 1863d exhibits the same function as the second gear section 1763d of the seventeenth embodiment. Therefore, when the drive transmission gear 1781 rotates in the direction of arrow I, there is no play (backlash) in the rotational direction (direction I) between the drive side flange 1863 and the drive transmission gear 1781, as in the 17th embodiment, that is, backlash is generated. It becomes a rushless state.

[0290] In addition, in a state where the elastic ring 1801 is not in contact with the drive transmission gear 1781, such as before installing the cartridge B in the apparatus main body A, the elastic ring 1801 closes the plurality of gaps 1863ds between the plurality of second oblique teeth 1863dt of the second gear portion 1863d. The inner circumferential portion may have a plurality of convex portions protruding in the direction toward the rotation axis L1 of the drive side flange 1863 so as to fill the inner peripheral portion.

[0291] Further, in this embodiment, the elastic ring 1801 is provided on the outer periphery of the second gear portion 1863d, but the elastic ring 1801 is provided on the entire or part of the outer periphery of the first gear portion 1863c, or the elastic ring 1801 is provided on the outer periphery of the second gear portion 1863d. Elastic rings 1801 may be provided on the entire or part of both outer peripheries of the first gear portion 1863c. Even in these cases, force is transmitted between the tooth surfaces of the respective gears via the elastic ring 1801. Therefore, the first gear section 1863c and the second gear section 1863d exhibit the same functions as the first gear section 1763c and the second gear section 1763d of the seventeenth embodiment. Therefore, when the drive transmission gear 1781 rotates in the direction of arrow I, there is no play (backlash) in the rotational direction (direction I) between the drive side flange 1863 and the drive transmission gear 1781, that is, there is no backlash.

[0292] Further, the drive side flange 1863 has the same shape as the drive side flange 1763 of the seventeenth embodiment, but the shape of the tip of the gear and the size of the gear may be changed as appropriate in consideration of the thickness of the elastic ring 1801, etc.

[0293] As explained above, according to this embodiment, the same effects as in the 17th embodiment can be obtained. Further, the elements of each embodiment described above can be applied to the configuration of this embodiment. In particular, the configurations of the first oblique tooth (first protrusion) 1863ct of the first gear portion 1863c of the drive side flange 1863 and the second oblique tooth (second protrusion) 1863dt of the second gear portion 1863d are modified in Examples 2, 3, and 4. , 5, 6, 10, 11, 12, 13, 14, 16 may be used instead.

[0294] [Example 19] In this example, compared to Example 17, the rotational axis (L19, etc.) of the first gear portion (external gear portion 1902b, etc.) receiving the driving force FD and the rotation axis (L19, etc.) of the second gear portion (1963d) receiving the regulating force FB. The difference is that the axis of rotation (L1) is not coaxial but parallel. Other points are the same as in Example 17, and detailed explanation will be omitted. Furthermore, among the elements in this example, the elements corresponding to the elements in Example 1 are given the reference numerals associated with the corresponding elements in Example 1. Items that are not specifically explained regarding these elements are the same as the corresponding elements of Example 1. <Drum unit 1969>

[0295] FIG. 63 is a partial perspective view of the drum unit 1969. As shown in FIG. 63, the drive side flange 1963 of the drum unit 1969 includes an internal gear portion 1963f, a second gear portion 1963d, a protrusion 1963g, a small diameter portion 1963e, and a flange portion 1963h centered around the drum rotation axis L1. Internal gear portion 1963f is a spur gear. The drum unit 1969 further includes a gear 1902, which will be described in detail later (see FIG. 65, etc.). The gear 1902 includes an external gear section 1902b serving as a first gear section and an internal gear section 1902a that meshes with an internal gear section 1963f.

[0296] The protrusion 1963g has a substantially cylindrical shape and is provided to protrude from the internal gear portion 1963f in a direction opposite to the drum 1962 side (downstream in the J direction) along the drum rotation axis L1. The small diameter portion (cylindrical portion) 1963e has a substantially cylindrical shape and is provided so as to protrude from the internal gear portion 1963f toward the drum 1962 (downstream in the H direction) along the drum rotation axis L1. The second gear portion 1963d is a diagonal tooth with a helix angle α2, similar to the seventeenth embodiment, and is provided on the drum 1962 side (downstream side in the H direction) of the small diameter portion 1963e. The flange portion 1963h has a thin disk shape with a diameter equal to or larger than the diameter of the drum 1962, and is provided on the drum 1962 side (downstream side in the H direction) of the second gear portion 1963d.

[0297] <Support structure of drum unit 1969> Next, a configuration for supporting the drum unit 1969 will be explained using FIGS. 64, 65, 66, and 67.

[0298] FIG. 64 is a side view (viewed from a direction perpendicular to the rotational axis L1) of the cleaning unit 1960 to which the drum unit 1969 is attached. FIG. 65 is an exploded perspective view of the drive side portion of the cleaning unit 1960. FIG. 66 is a partial cross-sectional view of the vicinity of the drive side flange 1963 of the cleaning unit 1960, and the cross section includes the rotation axis L1. FIG. 67 is a partial cross-sectional view of the cleaning unit 1960, and is a cross-sectional view of a cross section that is perpendicular to the rotational axis L1 and passes through the internal gear portion 1963f, as seen along the J direction.

[0299] As shown in FIG. 64, a cleaning frame 1960a of the cleaning unit 1960 supports a drum unit 1969. The cleaning frame 1960a of the cleaning unit 1960 is composed of a frame member 1971 and a drum bearing member 1973. The cleaning frame 1971 is provided with a drum sliding portion 1971g.

[0300] The drive side flange 1963 is rotatably supported by a drum bearing 1973 in the same manner as in the seventeenth embodiment. As described in the 17th embodiment, after the drive side flange 1963 of the drum unit 1969 engages with the drive transmission gear 1781, when the drive transmission gear 1781 rotates in a predetermined direction, the drive side While the flange 1963 rotates, a thrust force in the H direction is generated in the drum unit 1969, as described above. This thrust force brings the non-drive side flange 1964 into contact with the drum sliding portion 1971g, thereby restricting movement of the drum unit 1969 in the H direction.

[0301] As shown in FIG. 65, the bearing member 1973 is supported by the frame member 1971. A cylindrical portion 19710b, which is a positioning portion with respect to the bearing member 1973, is provided on the frame member 1971 so as to protrude toward the drum unit 1969 side. A cylindrical portion 19730r, which is a positioning portion with respect to the frame member 1971, is installed on the bearing member 1973 so as to protrude toward the drum unit 1969 side.

[0302] The inner circumferential surface 19710d of the cylindrical portion 19710b is formed in an arc shape, and the center of the arc is located at a position that coincides with the drum rotation axis L1. Further, the outer circumferential surface 19730b of the cylindrical portion 19730r is formed in a circular arc shape, and the center of the circular arc is provided at a position that coincides with the drum rotation axis L1. On the other hand, the outer peripheral surface 19710c of the cylindrical portion 19710b is formed in an arcuate shape, but the center axis L19 of the arcuate surface (coaxial with the rotational axis L19 of the gear 1902) is parallel to and coaxial with the drum rotational axis L1. provided. In other words, the outer circumferential surface 19710c of the cylindrical portion 19710b is provided at an eccentric position with respect to the inner circumferential surface 19710d.

[0303] The outer circumferential surface 19710c of the cylindrical portion 19710b supports the gear 1902 so as to be rotatable about the rotation axis L19. The gear 1902 has a substantially cylindrical shape, and has an internal gear part 1902a on the inner periphery and an external gear part 1902b as a first gear part (first unit side gear part) on the outer periphery, with the rotation axis L19 of the cylinder as the center. is installed. The internal gear portion 1902a has spur teeth, and the external gear portion 1902b has oblique teeth with a helix angle α1, which is 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 installed on one end side of the gear 1902, and a cylindrical portion 1902d is installed on the other end side. The support portion 1902c has a substantially cylindrical shape and is provided so as to protrude from the external gear portion 1902b and the internal gear portion 1902a in a direction opposite to the drum 1962 (downstream in the J direction) along the rotation axis L19. The cylindrical portion 1902d has a substantially cylindrical shape and is provided so as to protrude toward the drum 1962 side (downstream in the H direction) from the external gear portion 1902b and the internal gear portion 1902a along the rotation axis L19.

[0304] As shown in FIG. 66, the inner peripheral surface (supported part) of the support part 1902c engages with the outer peripheral surface 19710c of the cylindrical part 19710b, and the gear 1902 is rotatable about the rotation axis L19 on the frame member 1971. Supported by Further, the outer circumferential surface 19730b of the cylindrical portion 19730r engages with the inner circumferential surface 19710d of the cylindrical portion 19710b, and the bearing member 1973 is positioned and supported by the frame member 1971. The drive side flange 1963 passes through the inner peripheral portion of the gear 1902 and is installed on the cleaning frame 1960a. As in the seventeenth embodiment, the drive side flange 1963 has a projection 1963g supported by a bearing member 1973 so as to be rotatable about the rotation axis L1.

[0305] Further, as shown in FIG. 67, the internal gear portion 1963f of the drive side flange 1963 has spur teeth, and has the same number of teeth as the internal gear portion 1902a of the gear 1902. The gear 1902 and the internal gear part 1902a are installed so as to be fitted into the internal gear part 1963f, and the tooth surfaces of the internal gear part 1902a and the internal gear part 1963f engage with each other in the rotational direction. In other words, the internal gear portion 1902a and the internal gear portion 1963f mesh to be able to transmit rotational driving force.

[0306] As described above, the outer circumferential surface 19710c of the cylindrical portion 19710b of the frame member 1971 is provided at an eccentric position with respect to the inner circumferential surface 19710d. Therefore, the gear 1902 supported by the outer peripheral surface 19710c engages with the drive side flange 1963 supported by the inner peripheral surface 19710d via the bearing member 1973 at an eccentric position. In other words, the gear 1902 and the drive-side flange 1963 are rotatably arranged with their rotation axes L19 and L1 parallel to each other and non-coaxial, and can transmit rotational driving force to each other. In FIG. 67, the positions of the rotational axis L19 and the rotational axis L1 are indicated by the intersections of the horizontal dashed-dot line extending left and right and the vertical dashed-dotted line extending vertically, and the horizontal dashed-dotted line corresponding to the rotational axis L19 The deviation of the horizontal dash-dotted line corresponding to the rotation axis L1 can be confirmed. Further, the gear 1902 can also be referred to as a non-coaxial rotating member connected to the drive side flange 1963 so as to be able to transmit driving force.

[0307] <Transmission of driving force to drum unit 1969> Next, the transmission of driving force to the drum unit 1969 will be explained using FIGS. 68 and 69. FIG. 68 is a cross-sectional view showing the engaged state of the drum unit 1969 and the drive transmission gear 1781, and the cross section includes the rotation axis L1. FIG. 69 is a cross-sectional view showing the engaged state of the drum unit 1969 and the drive transmission gear 1781, and is a cross-sectional view taken along the J direction of a cross section that is perpendicular to the rotational axis L1 and passes through the internal gear portion 1963f.

[0308] As shown in FIG. 68, similarly to the seventeenth embodiment, the second main body gear portion 81d of the drive transmission gear 1781 meshes with the second gear portion 1963d of the drive side flange 1963. Further, the first main body gear portion 1781c of the drive transmission gear 1781 meshes with the external gear portion (first gear portion) 1902b of the gear 1902, and the internal gear portion 1902a of the gear 1902 meshes with the internal gear portion 1963f of the drive side flange 1963. meshes with

[0309] As shown in FIG. 69, when the drive transmission gear 1781 rotates in the direction of the arrow I, the gear 1902 receives a driving force from the engagement between the external gear portion 1902b and the first main body gear portion 1781c, and the gear 1902 rotates along the rotation axis L19. Rotate around the center in the direction of arrow KW. At this time, the internal gear portion 1902a engages with the internal gear portion 1963f of the drive side flange 1963 in the rotational direction, and transmits the driving force to the drive side flange 1963. As a result, the drive side flange 1963 rotates in the direction of arrow K around the rotation axis L1.

[0310] As the drive transmission gear 1781 rotates in the direction of the arrow I, the external gear portion 1902b receives a thrust force in the direction of the arrow H (see FIG. 68) due to engagement with the first main body gear portion 1781c. Therefore, as shown in FIG. 68, the gear 1902 moves in the direction of the arrow H, and the cylindrical part 1902d comes into contact with the end surface of the second gear part 1963d of the drive side flange 1963, causing the gear 1902 to move in the direction of the arrow H. be regulated (stopped).

[0311] On the other hand, the drive transmission gear 1781 moves in the direction of arrow J under the thrust force due to engagement with the external gear portion 1902b. Then, as in the seventeenth embodiment, the second main body gear portion 1781d moves to a balanced position where it engages with the second gear portion 1963d of the drive side flange 1963, and stops moving in the direction of the rotation axis L1.

[0312] In this balanced state, the external gear section (first gear section) 1902b receives the driving force FD from the first main body gear section 1781c. Since the gear 1902 can be regarded as a rigid body, this driving force FD is transmitted to the drive side flange 1963 due to the meshing (engagement) between the internal gear part 1902a and the internal gear part 1963f. That is, the driving side flange 1963 is in a state where it receives the driving force FD via the gear 1902. Furthermore, the drive side flange 1963 is in a state where the second gear portion 1963d receives the regulating force (braking force) FB from the second main body gear portion 1781d. The teeth of the second gear section 1963d are fixed so that they cannot move (rotate) in the direction opposite to the I direction relative to the teeth of the first gear section 1902b. Therefore, the drum unit 1969 (drum 1962, drive side flange 1963, and gear 1902) is driven without backlash. Therefore, even if the configuration of this embodiment is used, the same effects as in the 17th embodiment can be obtained.

[0313] Immediately after the drive transmission gear 1781 starts rotating, the drive side flange 1963 rotates in the K direction due to the engagement between the second gear section 1963d and the second main body gear section 1781d, and the gear 1902 engages with the internal gear section 1902a. It may also be rotated in the KW direction due to the engagement of the internal gear portion 1963f. In this case as well, as the drive transmission gear 1781 moves in the J direction, the first main body gear portion 1781c meshes with the external gear portion 1902b, and finally shifts to the balanced state described above.

[0314] Thus, in this embodiment, the rotational axis L19 of the external gear portion 1902b (first gear portion) and the rotational axis L1 of the second gear portion 1963d are not coaxial but parallel. In the balanced state, gear 1902 has the following parts (i) to (iii). (i) Input part: A part of the external gear part 1902b that meshes with at least the drive transmission gear 1781 (at least a part of the first gear part), (ii) Transmission part: Transmits driving force to the drive side flange 1963 The part of the internal gear part 1902a that meshes with the internal gear part 1963f, (iii) Output part: the part between (i) the input part and (ii) the output part. Since the parts (i) to (iii) of the gear 1902 are substantially rigid in the K direction, they move integrally along the K direction. Therefore, in the balanced state, the parts (i) to (iii) of the gear 1902 and the second gear part 1963d of the drive side flange 1963 are integral with each other in the K direction (rotation direction around the rotation axis L1). move in a specific manner. Therefore, a force corresponding to the driving force FD and a regulating force FB act on the driving side flange 1963, realizing driving in a backlash-free state and obtaining the same effects as in the seventeenth driving example. Additionally, this means that the first gear section that receives the driving force FD and the second gear section that receives the rotational axis and the regulating force FB need only be configured so that they can move integrally in the K direction in a balanced state. This shows that the first gear part and the second gear part do not have to be always integrally fixed to the drive side flange 1963 as in Examples 1 to 18.

[0315] Further, in this embodiment, an example of a configuration is shown in which the rotational axis of the first gear section receiving the driving force FD and the rotational axis of the second gear section receiving the regulating force FB are not coaxial. In other words, the axis of rotation of the second gear part (1963d) that receives the regulating force FB is coaxial with the axis of rotation (L1) of the drive side flange (1963), and the axis of rotation of the first gear part (1902b) that receives the driving force FD. is not coaxial with the rotation axis (L1) of the drive side flange (1963). Specifically, a first gear portion (1902b) is provided in the gear 1902 as a non-coaxial rotating member connected to the drive side flange 1963 so as to be able to transmit driving force. However, the structure in which the rotational axis of the first gear section receiving the driving force FD and the rotational axis of the second gear section receiving the regulating force FB are not coaxial is not limited to such a structure.

[0316] For example, as another example, the rotation axis of the first gear section receiving the driving force FD is coaxial with the rotation axis of the drive side flange, and the rotation axis of the second gear section receiving the regulating force FB is the rotation axis of the drive side flange. It is also possible to have a configuration that is not coaxial. In this configuration, specifically, the first gear portion is provided on the drive side flange, and the second gear portion is provided on the non-coaxial rotating member connected to the drive side flange so that driving force can be transmitted. As an example of a more specific configuration, in the drive side flange 1763 of Example 17, the first gear portion 1763c is left as is, and the gear 1902 having the second gear portion at the position of the second gear portion 1763d is changed as in the present example. The configuration may be such that it is placed in

[0317] As yet another example, the rotational axis of the first gear section receiving the driving force FD, the rotational axis of the second gear section receiving the regulating force FB, and the rotational axis of the drive side flange may be configured not to be coaxial with each other. In the case of this configuration, specifically, the first gear portion is provided in the first non-coaxial rotating member that is connected to the drive side flange so that the driving force can be transmitted, and the first gear part is connected to the drive side flange so that the driving force can be transmitted, A second gear portion is provided in a second non-coaxial rotating member that rotates non-coaxially with the first non-coaxial rotating member. As an example of a more specific configuration, in the drive side flange 1763 of Example 17, a gear 1902 having a first gear part is arranged at the position of the first gear part 1763c in the same manner as in this example, The gear 1902 including the second gear portion may be arranged in the same manner as in this embodiment.

[0318] Note that the connection configuration between the drive side flange 1963 and the non-coaxial rotating member (gear 1902) that allows driving force to be transmitted is not limited to the meshing configuration of spur gears such as the internal gear portion 1902a and the internal gear portion 1963f. For example, a connection configuration may be used in which driving force can be transmitted using a helical gear or a plurality of protrusions arranged in the circumferential direction. Furthermore, a non-coaxial driving force transmission joint such as an Oldham joint (detailed in Modification 2 of Embodiment 19) may be configured to connect the drive side flange 1963 and the non-coaxial rotating member (gear 1902) so that the driving force can be transmitted. .

[0319] <Modification 1 of Example 19> In the above-mentioned embodiment 19, the internal gear part 1963f of the drive side flange 1963 and the internal gear part 1902a of the gear 1902 have the same number of teeth and rotate as one body. However, in this modification, the drive side flange 1963 A configuration in which the rotation speed of the gear 1902 and the rotation speed of the gear 1902 are different will be explained. FIG. 70 is an exploded perspective view of the drive side portion of the cleaning unit 1960. FIG. 71 is a cross-sectional view showing the engaged state of the drum unit 1969 and the drive transmission gear 1781, and is a cross-sectional view of a cross section that is perpendicular to the rotational axis L1 and passes through the internal gear portion 1963f, taken along the J direction.

[0320] A gear 1903 is installed as a non-coaxial rotating member in place of the gear 1902 configured as described above, and a drive side flange 1963 is installed in place of the drive side flange 1963. Similar to the configuration described above, the gear 1903 is rotatably supported by the outer peripheral surface 1971c of the cylindrical portion 1971b of the cleaning frame 1971, and the drive side flange 1963 is rotatably supported by the bearing member 1973 through the gear 1903. ing.

[0321] As shown in FIG. 71, the internal gear portion 1903a of the gear 1903 is configured to be larger than the first gear portion 1963c of the drive side flange 1963, and is even more eccentric than the configuration described above. Note that in FIG. 71, the positions of the rotational axis L19 and the rotational axis L1 are indicated by the intersections of horizontal dashed-dot lines extending left and right and vertical dashed-dot lines extending vertically.

[0322] In the balanced state, at least the portion of the external gear portion 1903b that meshes with the drive transmission gear 1781 (at least a portion of the first gear portion) and the second gear portion 1963d are centered on the rotation axis L1. It moves integrally in the direction of rotation. Therefore, the same effects as in the 19th embodiment described above can be obtained.

[0323] In this embodiment, the first gear portion 1963c of the drive side flange 1963 and the internal gear portion 1903a of the gear 1903 are constructed of spur gears, but if the configuration allows mutual eccentricity, they may be helical gears. It may be composed of

[0324] <Modification 2 of Example 19> A configuration using an Oldham joint as a driving force transmission configuration between the non-coaxial rotating member and the drive side flange 1963 will be described. FIG. 72 is a partial perspective view of the drum unit 1969. As shown in FIG. 72, the drive flange 1963 includes a gear portion 1963d, a protrusion 1963g, a small diameter portion 1963e, and a flange portion 1963h centered around the drum rotation axis L1.

[0325] The small diameter portion 1963e has a substantially cylindrical shape, and is provided so as to protrude from the gear portion 1963c to the side opposite to the drum 1962 (downstream in the J direction) along the drum rotation axis L1. The small diameter portion 1963e is provided with a recessed portion 1963r that is recessed toward the drum 1962 side (downstream side in the H direction). The side surfaces 1963s of the recessed portion 1963r have a planar shape parallel to the direction of the drum rotation axis L1, and are arranged at equally spaced positions across the drum rotation axis L1. Further, the recessed portions 1963r are provided at two symmetrical positions across the small diameter portion 1963g in a direction perpendicular to the drum rotation axis L1.

[0326] The protrusion 1963g has a cylindrical shape and is provided to protrude from the small diameter portion 1963e in a direction opposite to the drum 1962 (downstream in the J direction) along the drum rotation axis L1.

[0327] The flange portion 1963h has a thin disk shape with a diameter equal to or larger than the diameter of the drum 1962, and is provided on the drum 1962 side (downstream side in the H direction) of the 1963 gear portion 1963d. The gear portion 1963d is a diagonal tooth with a helix angle α2, similar to the seventeenth embodiment. The drum unit 1969 also includes a gear 1904 including a gear portion 1904c as a first gear portion, which will be described in detail later, and a driven coupling 1905.

[0328] Next, the configuration of the cleaning unit will be explained using FIG. 73. Figure 73 is an exploded perspective view of the drive side of the cleaning unit, (a) is a view seen from the drive side towards the non-drive side, and (b) is a view seen from the non-drive side towards the drive side. be. As shown in FIGS. 73(a) and 73(b), the bearing member 1973 is supported by the frame member 1971. A hole 1971d is provided on the side surface of the frame member 1971 as a positioning portion with respect to the bearing member 1973, and the hole 1971d is formed in an arc shape, and is provided at a position where the center of the arc coincides with the drum rotation axis L1. ing. Further, a cylindrical portion 1971b is installed on the frame member 1971 so as to protrude downstream in the H direction. The inner circumferential surface 1971c of the cylindrical portion 1971b has an arcuate surface shape, and the centerline L19 of the arcuate surface is provided at a position parallel to, but not coaxial with, the drum rotation axis L1. In other words, the hole 1971d is provided at a position eccentric to the inner peripheral surface 1971c.

[0329] A gear 1904 as a non-coaxial rotating member is rotatably supported on the inner circumferential surface 1971c of the cylindrical portion 1971b. The gear 1904 has a substantially cylindrical shape and includes a through hole 1904a, a gear portion 1904c as a first gear portion on the outer periphery, and a cylindrical portion 1904d coaxially centered on the axis of the cylinder. The gear portion 1904c is a diagonal tooth with a helix angle α1. A convex portion 1904b is installed from the side surface of the gear 1904 to protrude downstream in the H direction.

[0330] When the rotational axis of the gear 1904 is the gear rotational axis L19, the side portions 1904e and 1904f of the convex portion 1904b have a planar shape parallel to the gear rotational axis L19 direction, and are arranged at equal intervals across the gear rotational axis L19. Each is placed. Further, the convex portion 1904b has an arcuate shape that does not protrude from the tooth bottom of the gear portion 1904c in the radial direction centered on the rotation axis L1. Further, the convex portions 1904b are provided at two symmetrical positions across the through hole 1904a in a direction perpendicular to the gear rotation axis 1901. The cylindrical portion 1904d protrudes downstream in the J direction. The cylindrical portion 1904d fits into the inner peripheral surface 1971c of the cylindrical portion 1971b of the frame member 1971, so that the gear 1904 is rotatably supported by the frame member 1971.

[0331] A driven coupling 1905 is installed downstream of the gear 1904 in the H direction. The driven coupling 1905 has a substantially cylindrical shape and includes a through hole 1905a and a cylindrical portion 1905d coaxially centered around the axis of the cylindrical shape. A convex portion 1905b is installed on the downstream side of the cylindrical portion 1905d in the H direction so as to protrude downstream in the H direction. Further, a recessed portion 1905c is provided on the downstream side of the cylindrical portion 1905d in the J direction, and is recessed downstream in the H direction. The convex portion 1905b has parallel surfaces that are equally spaced from the side surface portions 1963s of the concave portion 1963r around the cylindrical axis, and the concave portion 1905c has side surfaces 1904e and 1904f of the convex portion 1904b centered on the cylindrical axis. The convex portion 1905b and the concave portion 1905c are arranged in orthogonal directions centering on the axis of the cylindrical shape.

[0332] The protrusion 1904b of the gear 1904 fits into the recess 1905c of the driven coupling 1905 in the direction of the rotational axis L1 of the cylinder, and the protrusion 1904b moves (slides) in the 190Y direction (see Figure 73(b)) within the recess 1905c. It is possible. The 190Y direction is a direction parallel to a plane orthogonal to the rotation axis L1. Further, the convex portion 1904b is capable of transmitting a driving force for rotating the driven coupling 1905 around the rotation axis L1 to the concave portion 1905c.

[0333] Further, the projection 1963g of the drive flange 1963 passes through the through hole 1905a of the driven coupling 1905 and the through hole 1904a of the gear 1904. Here, the radial size of the through hole 1905a and the through hole 1904a is set to be sufficiently larger than the outer diameter of the protrusion 1963g.

[0334] Further, the protrusion 1905b of the driven coupling 1905 fits into the recess 1963r of the drive flange 1963 in the direction of the rotation axis L1, and the protrusion 1905b can move (slide) in the 190X direction within the recess 1963r. The 190X direction is a direction parallel to a plane orthogonal to the rotation axis L1, and is a direction orthogonal to the 190Y direction when viewed along the rotation axis L1. Further, the convex portion 1905b can transmit the driving force for rotating the drive flange 1963 around the rotation axis L1 to the concave portion 1963r. The tip of the projection 1963g is rotatably supported by a drum bearing member 1973, as in the seventeenth embodiment.

[0335] As described above, the inner circumferential surface 1971c of the cylindrical portion 1971b of the frame member 1971 is eccentrically arranged with respect to the hole 1971d. Therefore, the gear 1904 supported by the inner circumferential surface 1971c and the drive side flange 1963 supported coaxially with the hole 1971d are each rotatably supported at eccentric positions.

[0336] Next, the engagement with the drive transmission gear 1781 will be explained using FIGS. 74 and 75. FIG. 74 is a diagram showing the drum unit 1969 that meshes with the drive transmission gear 1781, as viewed from a direction perpendicular to the rotation axis L1. 75(a) to (e) are cross-sectional views showing the engaged state of the drum unit 1969 and the drive transmission gear 178, in which a cross section passing through the convex portion 1904b of the gear 1904, which is perpendicular to the rotational axis L1, is taken along the H direction. It is a sectional view. In addition, in FIG. 75, the position of the rotation axis L19 is shown by the intersection of the horizontal dash-dot line extending left and right and the vertical dash-dot line extending up and down, while the position of the rotation axis L1 is indicated by a circle. Since it is the center of the protrusion 1963g, its description has been omitted to simplify the diagram. Furthermore, the black circle shown on the driven coupling 1905 in FIG. 75 is a mark pointing to a specific part of the driven coupling 1905, and is written to make it easier to understand the rotational phase of the driven coupling 1905.

[0337] As shown in FIG. 74, the second body gear portion 1781d of the drive transmission gear 1781 engages with the second gear portion 1963d of the drive side flange 1963, and the first body gear portion 81c engages with the gear 1904 (first gear portion). engage with.

[0338] As shown in FIGS. 75(a) to (e), when the drive transmission gear 1781 rotates in the I direction, the driving force is transmitted from the drive transmission gear 1781 to the gear section 1904c (first gear section), and the drive force is transmitted to the gear section 1904c (first gear section). rotates in the KW direction around the gear rotation axis L19. The driving force of the drive transmission gear 1781 is transmitted to the drive flange 1963 via the driven coupling 1905 that engages with the gear 1904, and moves the drive flange 1963 in the K direction (see FIG. 72) around the rotation axis L1. Rotate.

[0339] As the gear 1904 and drum unit 1969 rotate, the driven coupling 1905 moves in the 190X direction with respect to the drive flange 1963 because the protrusion 1905b (see Figure 74) moves within the recess 1963r of the drive side flange 1963. Moving. Further, the gear 1904 moves in the 190Y direction with respect to the driven coupling 1905 as the convex portion 1904b moves within the concave portion 1905c. As a result, gear 1904 (rotation axis L19) and drive side flange 1963 (rotation axis L1) rotate between gear 1904 and drive side flange 1963 while maintaining their eccentric position (non-coaxial and parallel state). It is possible to transmit the driving force for

[0340] Then, by the same action as in the nineteenth embodiment, the drive transmission gear 1781 moves to the balanced position and enters the balanced state. In the balanced state, the drive transmission gear 1781 receives the regulating force FB at the second gear portion 1963d, and transmits a force corresponding to the driving force FD received by the gear portion 1904c (first gear portion) of the gear 1904 to the driven coupling 1905. Receive at the side part 1963s through. The teeth of the second gear section 1963d are fixed so that they cannot move (rotate) in the direction opposite to the I direction relative to the teeth of the first gear section 1904c. Therefore, a backlash-free state is achieved, and the same effects as in Example 17 can be obtained.

[0341] As described above, according to Example 19, Modification 1 of Example 19, and Modification 2 of Example 19, effects similar to those of Example 17 can be obtained. Further, the elements of each embodiment described above can be applied to the configuration of this embodiment. In particular, the configurations of the first oblique teeth (first protrusion) of the first gear part and the second oblique teeth (second protrusion) of the second gear part were changed to Examples 2, 3, 4, 5, 6, 10, 11, It may be changed to oblique teeth, spur teeth, protrusions, etc. shown in 12, 13, 14, and 16.

[0342] [Example 20] Next, Example 20 will be described below using FIGS. 76, 77, 78, and 79. In this example, compared to Example 17, the first gear portion (external tooth portion 2002b) receiving the driving force FD rotates only in a certain region of the second gear portion (2063d) receiving the regulating force FB. The difference is that it rotates coaxially with the axis (L1). Alternatively, it can be said that in this example, compared to Example 17, the movement of the first gear portion (external tooth portion 2002b) does not consist only of rotation about one rotation axis (L1). Other points are the same as in Example 17, and detailed explanation will be omitted. Furthermore, among the elements in this example, the elements corresponding to the elements in Example 1 are given the reference numerals associated with the corresponding elements in Example 1. Items that are not specifically explained regarding these elements are the same as the corresponding elements of Example 1.

[0343] <Drum unit 2069> FIG. 76 is a partial perspective view of the drum unit 2069. FIG. 77 is an exploded perspective view of the driving side of the cleaning unit 2060 and drum unit 2069. FIG. 78 is a cross-sectional view of the drive side flange 2063 of the cleaning unit 2060 at the gear portion 2063f.

[0344] As shown in FIG. 76, the drive side flange 2063 has a gear portion 2063f, a second gear portion (second unit side gear portion) 2063d, a protrusion 2063g, a small diameter portion 2063e, and a flange portion 2063h around the drum rotation axis L1. We are prepared. The gear portion 2063f has a pulley shape corresponding to a toothed belt.

[0345] The protrusion 2063g has a substantially cylindrical shape and is provided to protrude from the gear portion 2063f in a direction opposite to the drum 2062 side (downstream side in the J direction) along the drum rotation axis L1. The small diameter portion 2063e has a substantially cylindrical shape with a diameter greater than or equal to the diameter of the gear portion 2063f and less than a diameter of the second gear portion 2063d, and is located closer to the drum 2062 than the gear portion 2063f (downstream in the H direction) along the drum rotation axis L1. established in The second gear portion 2063d is a diagonal tooth with a helix angle α2, similar to the seventeenth embodiment, and is provided on the drum 2062 side (downstream side in the H direction) of the small diameter portion 2063e. The flange portion 2063h has a thin disk shape with a diameter equal to or larger than the diameter of the drum 2062, and is provided on the drum 2062 side (downstream side in the H direction) of the second gear portion 2063d.

[0346] As shown in FIG. 77, the drum unit 2069 further includes a belt 2002 (see FIG. 77, etc.). The belt 2002 includes an outer toothed portion 2002b serving as a first gear portion (first unit side gear portion) on the outer circumference, and an inner toothed portion 2002a that meshes with the gear portion 2063f on the inner circumference. The belt 2002 is an elastic belt-like member. The external tooth portion 2002b is a diagonal tooth with a helix angle α1.

[0347] Next, the configuration of the drive-side cleaning unit 2060 will be explained using FIGS. 77 and 78. As shown in FIG. 77, the bearing member 2073 is supported by the frame member 2071. The frame member 2071 is provided with a substantially cylindrical hole 20710a. The bearing member 2073 is provided with a substantially cylindrical hole 20730a facing the hole 20710a at a position facing the hole 20710a. A pulley 2001 is installed between hole 20710a and hole 20730a. The pulley 2001 has a substantially cylindrical shape extending in the direction of an axis parallel to the rotation axis L1. The pulley 2001 has supported parts 2001a and 2001b, which are approximately cylindrical protrusions, at both ends in a direction parallel to the rotation axis L1, and has a pulley shape corresponding to the internal teeth part 2002a of the belt 2002 on the peripheral surface of the central part. A certain tooth portion 2001c is provided. Further, the pulley 2001 includes a flange portion 2001d having a larger diameter than the tooth portion 2001c between the supported portion 2001a and the tooth portion 2001c. The supported parts 2001a and 2001b are rotatably supported by the holes 20710a and 20730a, respectively, so that the pulley 2001 can rotate about a rotation axis parallel to the rotation axis L1.

[0348] <Support structure of drum unit 2069> The support structure of the drive-side flange 2062 of the drum unit 2069 and the drum 2062 by the bearing member 2073 and the frame member 2071 is the same as in the nineteenth embodiment, and therefore the explanation will be omitted. On the other hand, as shown in FIG. 78, the belt 2002 of the drum unit 2069 is connected to the pulley 2001 and the gear portion, with the internal tooth portion 2002a meshing with the gear portion 2063f of the drive side flange 2063 and the tooth portion 2001c of the pulley 2001. Supported by 2063f. Further, the belt 2002 is supported by the drive side flange 2063 and the pulley 2001 with an appropriate tension so that the portion not in contact with either the drive side flange 2063 or the pulley 2001 does not bend significantly. . Further, the belt 2002 can be circulated by rotation of the drive side flange 2063 (gear portion 2063f) and pulley 2001 (teeth portion 2001c).

[0349] <Transmission of driving force to drum unit 2069> Next, the state of engagement with the drive transmission gear 1781 will be explained using FIGS. 79 and 80. FIG. 79 is a cross-sectional view showing the engaged state of the drum unit 2069 and the drive transmission gear 1781, and a cross-sectional view of the cross section passing through the belt 2002 perpendicular to the rotational axis L1 as seen along the J direction. FIG. 17 is a cross-sectional view showing an engaged state of transmission gear 1781, and the cross section includes the rotation axis L1. FIG.

[0350] As shown in FIG. 79, when the drive transmission gear 1781 rotates in the direction of the arrow I, the external toothed portion 2002b of the belt 2002 engages with the first main body gear portion 1781c, and circulates in the direction of the arrow KC, which is the cyclic movement direction. Moving. As the belt 2002 circulates, the gear portion 2063f of the drive side flange 2063 that engages with the internal tooth portion 2002a of the belt 2002 rotates in the direction of arrow K. At this time, if the portion of the belt 2002 that engages with the internal toothed portion 2002a is a rotating portion 2002R, the rotating portion 2002R rotates in the K direction about the rotation axis L1. Therefore, the circulating movement direction KC of the rotating portion 2002R of the belt 2002 coincides with the K direction. Therefore, if a portion of the external toothed portion 2002b serving as the first gear portion that is included in the rotating portion 2002R is the rotating gear portion 2002bR, the rotating gear portion 2002bR includes the drive side flange 2063 and the It rotates coaxially and integrally with the 2nd gear part 2063d. Further, as the belt 2002 circulates in the KC direction, the pulley 2001 rotates in the direction of arrow V20.

[0351] When the drive transmission gear 1781 rotates in the direction of the arrow I, the external gear portion 2002b receives a thrust force in the direction of the arrow H due to engagement with the first main body gear portion 1781c, and the belt 2002 attempts to move in the direction of the arrow H. do. However, as shown in FIG. 80, since the diameter of the small diameter portion 2063e of the drive side flange 2063 is larger than the diameter of the gear portion 2063f, the end surface 2002E of the belt 2002 comes into contact with the end surface 2063eE of the small diameter portion 2063e, and the arrow on the belt 2002 Movement in the H direction is restricted (stopped).

[0352] On the other hand, drive transmission gear 1781 moves in the direction of arrow J in response to thrust force due to engagement with external tooth portion 2002b. Then, as in the seventeenth embodiment, the second main body gear portion 1781d moves to a balanced position where it engages with the second gear portion 2063d of the drive side flange 1963, and stops moving in the direction of the rotation axis L1. The operations and functions of the first gear portion (external tooth portion 2002b) and 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 in the nineteenth embodiment. The same is true.

[0353] In this balanced state, the rotating gear section 2002bR of the external tooth section (first gear section) 2002b receives the driving force FD from the first main body gear section 1781c. Since the rotating portion 2002R of the belt 2002 can be regarded as a rigid body, this driving force FD is transmitted to the drive side flange 2063 due to the meshing (engagement) between the internal tooth portion 2002a and the gear portion 2063f. That is, the driving side flange 2063 is in a state where it receives the driving force FD via the rotating portion 2002R of the belt 2002. Further, the drive side flange 2063 is in a state where the second gear portion 2063d receives the regulating force (braking force) FB from the second main body gear portion 1781d. The teeth of the second gear section 2063d are fixed so that they cannot move (rotate) in the direction opposite to the I direction relative to the teeth of the first gear section 2002b. Therefore, the drum unit 2069 (drum 2062, drive side flange 2063, and belt 2002) is driven without backlash. Therefore, even if the configuration of this embodiment is used, the same effects as in the 17th embodiment can be obtained.

[0354] In addition, although this embodiment shows a configuration in which the belt 2002 is provided with the first gear portion that receives the driving force FD in the balanced state, the second gear portion that receives the regulating force FB in the balanced state is supported in the same way as the belt 2002. It may also be configured to be provided on a belt that is Alternatively, a configuration may be adopted in which the first gear portion receiving the driving force FD is provided on the belt 2002 and the second gear portion receiving the regulating force FB is provided on another belt.

[0355] Further, in this embodiment, a configuration is shown in which the belt 2002 has an internal toothed portion 2002a and an external toothed portion 2002b as a first gear portion, but this is not the case. For example, the belt may be a belt that deforms into a shape that follows the shape of the gear of the drive side flange 2063 and the gear of the drive transmission gear 1781, such as the elastic ring 1801 shown in Example 18. In this case, the gear portion 2063f of the drive side flange 2063 has a shape corresponding to the first main body gear portion 1781c of the drive transmission gear 1781, and the gear portion 2063f is configured to mesh with the first main body gear portion 1781c via a belt. In this case, the gear section 2063f can also be regarded as a first gear section that receives the driving force FD. If the belt covers the second gear part 2063d of the drive side flange 2063 and is provided so as to follow the gear shape of the second gear part 2063d, the second gear part 2063d is replaced with the second gear part 2063d that receives the regulating force FB. It can be considered as a department.

[0356] As explained above, according to this embodiment, the same effects as in the 17th embodiment can be obtained. Further, the elements of each embodiment described above can be applied to the configuration of this embodiment. In particular, the configurations of the first oblique tooth (first protrusion) of the first gear part and the second oblique tooth (second protrusion) of the second gear part were changed to Examples 2, 3, 4, 5, 6, 10, 11, It may be changed to oblique teeth, spur teeth, protrusions, etc. shown in 12, 13, 14, and 16.

[0357] [Example 21] Next, Example 21 will be described below using FIGS. 81 and 82. This example differs from Example 17 in the direction in which the teeth of the gear portion protrude. That is, in Example 17, the protruding direction of the teeth of each gear part (first gear part, second gear part) was the radial direction centered on the rotation axis L1, but in this embodiment, the protruding direction of the teeth was rotational. The direction has a directional component parallel to the axis L1. Other points are the same as in Example 17, and detailed explanation will be omitted. Furthermore, among the elements in this example, the elements corresponding to the elements in Example 1 are given the reference numerals associated with the corresponding elements in Example 1. Regarding these elements, items without special explanation are the same as the corresponding elements of Example 1.

[0358] <Drive side flange 2163> FIG. 81 is a partial perspective view of the drive side portion of the drum unit 2169. FIG. 82 is a partial perspective view of the drum unit 2169 in which the drive side flange 2163 is cut along a cross section that is perpendicular to the rotational axis L1 and passes through the protrusion 2163d. As shown in FIG. 81, the drive side flange 2163 has a first gear portion (first unit side gear portion) 2163c, a protrusion portion as a second gear portion (second unit side gear portion), centered around the rotation axis L1. 2163d, a projection (supported part) 2163g, a small diameter part 2163e, and a flange part 2163h.

[0359] The first gear portion 2163c is a diagonal tooth with a helix angle α1, and has substantially the same shape as the first gear portion 1763c of the seventeenth embodiment. The protrusion (supported part) 2163g has a substantially cylindrical shape centered on the rotation axis L1, and protrudes from the first gear part 2163c in a direction opposite to the drum 2162 (downstream in the J direction) along the rotation axis L1. provided. The protrusion 2163g has substantially the same shape as the protrusion 1763g of Example 17.

[0360] The small diameter portion 2163e has a substantially cylindrical shape, and is provided to protrude from the first gear portion 2163c toward the drum 2162 side (downstream side in the H direction) along the rotation axis L1. The flange portion 2163h has a thin disk shape with a diameter equal to or larger than the diameter of the drum 2162, and is provided on the drum 62 side (downstream side in the H direction) of the small diameter portion 2163e.

[0361] The protrusion 2163d serving as the second gear portion is composed of a plurality of protrusions (teeth) 2163dt. The plurality of protrusions 2163dt are provided in the same number as the number of teeth of the first gear part 2163c, and are formed in a shape that can be engaged with the second main body gear part 1781d of the drive transmission gear 1781. Further, the plurality of protrusions (teeth) 2163dt protrude from the flange portion 2163h so as to extend in the J direction toward the side opposite to the drum 2162 along the rotation axis L1, and further extend around the rotation axis L1 as they go in the J direction. It is a spiral protrusion twisted at a twist angle α2 toward the downstream side in the K direction (rotation direction K of the drive side flange 2163), which is the circumferential direction of the drive side flange 2163. That is, the protrusion direction PD of the protrusion (teeth) 2163dt from the flange portion 2163h is a direction having at least an H-direction component parallel to the rotation axis L1 and a K-direction component that is a circumferential direction centered on the rotation axis L1. The torsion angle of the plurality of protrusions 2163dt is torsion angle α2. Note that when the protrusion 2163dt is configured to have a spur tooth shape rather than a diagonal tooth shape, the protrusion direction PD has an H direction component parallel to the rotation axis L1, but does not have a circumferential direction (K direction) component.

[0362] Further, the plurality of protrusions 2163dt are involute tooth-shaped teeth having involute surface portions on the side surfaces, and have substantially the same shape as the second oblique teeth (second...

Claims

1. A photosensitive unit detachable from the main body of an image forming device, comprising a first main body side helical gear portion and a second main body side helical gear portion which rotate on the same axis, the twist direction of the teeth of the second main body side helical gear portion being the same as the twist direction of the teeth of the first main body side helical gear portion, and the twist angle of the teeth of the second main body side helical gear portion being greater than the twist angle of the teeth of the first main body side helical gear portion, A photoconductor rotatable about a rotation axis; a first unit side gear portion for meshing with the first main body side helical gear portion; a second unit side gear portion having a plurality of teeth for meshing with the second main body side helical gear portion; having the first unit side gear portion is a helical gear portion having helical teeth twisted in a first circumferential direction about the rotation axis of the photosensitive member as the first unit side gear portion moves away from the photosensitive member along the rotation axis of the photosensitive member, the second unit side gear portion is disposed between the first unit side gear portion and the photosensitive body with respect to a direction of a rotation axis of the photosensitive body, a gap is provided between the first unit side gear portion and the second unit side gear portion in a direction of a rotation axis of the photosensitive member, the plurality of teeth of the second unit side gear portion include teeth including: (i) a first protrusion portion extending at least in a direction of a rotation axis of the photosensitive body; and (ii) a second protrusion portion disposed downstream in the first circumferential direction of at least a portion of the first protrusion portion and closer to the first unit side gear portion in the direction of the rotation axis of the photosensitive body than at least a portion of the first protrusion portion, the first unit side gear portion and the second unit side gear portion are rotatable in a state in which the first unit side gear portion meshes with the first main body side helical gear portion and the second protrusion portion of the second unit side gear portion meshes with the second main body side helical gear portion; The photoconductor unit is characterized by the above.

2. At least a part of the first protrusion is disposed between the second protrusion and the photoconductor with respect to a direction of a rotation axis of the photoconductor.

2. The photoconductor unit according to claim 1.

3. the second protrusion is disposed at a position farthest from the photosensitive member among the teeth of the second unit side gear portion in relation to the direction of the rotation axis of the photosensitive member; 3. The photoconductor unit according to claim 2.

4. the first protrusion portion includes a twisted protrusion portion that is twisted in the first circumferential direction about the rotation axis of the photoconductor as it moves away from the photoconductor along the rotation axis of the photoconductor, 4. The photoconductor unit according to claim 1, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

5. a helix angle of the helical protrusion is equal to or smaller than a helix angle of the helical teeth of the first unit side gear portion; 5. The photoconductor unit according to claim 4.

6. With respect to the direction of the rotation axis of the photosensitive member, the tooth width Wc of the first unit side gear portion and the tooth width Wd of the second unit side gear portion are expressed by the following formula: Wc≦Wd Fulfilling 6. The photoconductor unit according to claim 1, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

7. With respect to the direction of the rotation axis of the photosensitive member, the tooth width Wc of the first unit side gear portion and the width We of the gap are expressed by the following formula: Wc≦We Fulfilling 7. The photoconductor unit according to claim 1, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

8. With respect to the direction of the rotation axis of the photosensitive member, the width We of the gap and the tooth width Wd of the second unit side gear portion are expressed by the following formula: Wd≦We Fulfilling 8. The photoconductor unit according to claim 1, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

9. The twist angle of the teeth of the first unit side gear portion is 15° or more and 40° or less.

9. The photoconductor unit according to claim 1, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

10. The twist angle of the teeth of the first unit side gear portion is equal to or greater than 20° and equal to or less than 35°.

10. The photoconductor unit according to claim 1, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

11. the helical teeth of the first unit side gear portion are teeth formed by a plurality of first protrusions arranged separately with respect to a direction of a rotation axis of the photosensitive body or a rotation direction of the first unit side gear portion, 11. The photoconductor unit according to claim 1,

12. the first protrusion portion is a tooth constituted by a plurality of second protrusions arranged separately with respect to a direction of a rotation axis of the photosensitive body or a rotation direction of the second unit side gear portion, 12. The photoconductor unit according to claim 1, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

13. The first unit side gear portion and the second unit side gear portion are rotatable coaxially.

13. The photoconductor unit according to claim 1, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

14. a rotation axis of the first unit side gear portion and a rotation axis of the second unit side gear portion are coaxial with a rotation axis of the photosensitive body; The photoconductor unit according to claim 13 .

15. The first unit side gear portion and the second unit side gear portion are integrally molded.

15. The photoconductor unit according to claim 1,

16. a flange attached to an end of the photoreceptor with respect to a rotation axis direction of the photoreceptor; the first unit side gear portion and the second unit side gear portion are provided on the flange, 16. The photoconductor unit according to claim 1, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

17. an intermediate member that is provided between the first unit side gear portion and the second unit side gear portion with respect to a direction of a rotation axis of the photosensitive member and is capable of filling the gap; 17. The photoconductor unit according to claim 1,

18. A photoconductor unit detachably attached to a main body of an image forming apparatus, the photoconductor unit having a first main body side helical gear portion and a second main body side helical gear portion which rotate on the same shaft, A photoconductor rotatable about a rotation axis; a first unit side gear portion for meshing with the first main body side helical gear portion; a second unit side gear portion having a plurality of teeth for meshing with the second main body side helical gear portion; having the first unit side gear portion is a helical gear portion having helical teeth twisted in a first circumferential direction about the rotation axis of the photosensitive member as the first unit side gear portion moves away from the photosensitive member along the rotation axis of the photosensitive member, the second unit side gear portion is disposed between the first unit side gear portion and the photosensitive body with respect to a direction of a rotation axis of the photosensitive body, a gap is provided between the first unit side gear portion and the second unit side gear portion in a direction of a rotation axis of the photosensitive member, the plurality of teeth of the second unit side gear portion include teeth including: (i) a first protrusion portion extending at least in a direction of a rotation axis of the photosensitive body; and (ii) a second protrusion portion disposed downstream in the first circumferential direction of at least a portion of the first protrusion portion and closer to the first unit side gear portion in the direction of the rotation axis of the photosensitive body than at least a portion of the first protrusion portion, while the first unit side gear portion and the second unit side gear portion rotate in a predetermined direction due to rotation of the first body side helical gear portion and the second body side helical gear portion, the teeth of the first unit side gear portion come into contact with the teeth of the first body side helical gear portion arranged upstream in the first circumferential direction, and the second protrusion portion of the second unit side gear portion comes into contact with the teeth of the second body side helical gear portion arranged downstream in the first circumferential direction. The photoconductor unit is characterized by the above.

19. At least a portion of the first protrusion is disposed between the second protrusion and the photosensitive body with respect to the direction of the rotation axis of the photosensitive body.

20. The photoconductor unit according to claim 18,

20. The second protrusion is disposed at a position farthest from the photosensitive body among the teeth of the second unit side gear part with respect to the direction of the rotation axis of the photosensitive body.

20. The photoconductor unit according to claim 19.

21. The first protrusion portion has a twisted protrusion portion that twists in the first circumferential direction around the rotation axis of the photoconductor as it moves away from the photoconductor along the rotation axis of the photoconductor.

21. The photoconductor unit according to claim 18, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

22. A twist angle of the twisted protrusion is equal to or smaller than a twist angle of the helical teeth of the first unit side gear part.

22. The photoconductor unit according to claim 21.

23. With respect to the direction of the rotation axis of the photosensitive member, the tooth width Wc of the first unit side gear portion and the tooth width Wd of the second unit side gear portion are expressed by the following formula: Wc≦Wd Fulfilling 23. The photoconductor unit according to claim 18, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

24. With respect to the direction of the rotation axis of the photosensitive member, the tooth width Wc of the first unit side gear portion and the width We of the gap are expressed by the following formula: Wc≦We Fulfilling 24. The photoconductor unit according to claim 18, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

25. With respect to the direction of the rotation axis of the photosensitive member, the width We of the gap and the tooth width Wd of the second unit side gear portion are expressed by the following formula. Wd≦We Fulfilling 25. The photoconductor unit according to claim 18, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

26. The twist angle of the teeth of the first unit side gear portion is greater than or equal to 15° and less than or equal to 40°.

26. The photoconductor unit according to claim 18, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

27. ​​The twist angle of the teeth of the first unit side gear portion is greater than or equal to 20° and less than or equal to 35°.

27. The photoconductor unit according to claim 18,

28. The inclined teeth of the first unit side gear part are teeth formed by a plurality of first protrusions arranged separately with respect to the direction of the rotation axis of the photosensitive body or the rotation direction of the first unit side gear part.

28. The photoconductor unit according to claim 18, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

29. The first protrusion portion is a tooth formed by a plurality of second protrusions arranged separately with respect to the direction of the rotation axis of the photosensitive body or the rotation direction of the second unit side gear portion.

29. The photoconductor unit according to claim 18, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

30. The first unit side gear portion and the second unit side gear portion are rotatable coaxially.

30. The photoconductor unit according to claim 18, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

31. The rotation axis of the first unit side gear part and the rotation axis of the second unit side gear part are coaxial with the rotation axis of the photosensitive body.

31. The photoconductor unit according to claim 30.

32. The first unit side gear portion and the second unit side gear portion are integrally molded.

32. The photoconductor unit according to claim 18, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

33. A flange is attached to an end of the photoreceptor relative to the direction of the rotation axis of the photoreceptor, the first unit side gear portion and the second unit side gear portion are provided on the flange, 33. The photoconductor unit according to claim 18, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

34. An intermediate member is provided between the first unit side gear portion and the second unit side gear portion with respect to the direction of the rotation axis of the photosensitive body, and is capable of filling the gap.

34. The photoconductor unit according to claim 18, wherein the photoconductor unit is a photoconductor having a first surface and a second surface.

Images