WO2013032721A1 - Rotating drive shaft coupling - Google Patents
Rotating drive shaft coupling Download PDFInfo
- Publication number
- WO2013032721A1 WO2013032721A1 PCT/US2012/051072 US2012051072W WO2013032721A1 WO 2013032721 A1 WO2013032721 A1 WO 2013032721A1 US 2012051072 W US2012051072 W US 2012051072W WO 2013032721 A1 WO2013032721 A1 WO 2013032721A1
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- WIPO (PCT)
- Prior art keywords
- recess
- drive coupling
- projection
- teeth
- tooth
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/02—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for connecting two abutting shafts or the like
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
- F16D1/101—Quick-acting couplings in which the parts are connected by simply bringing them together axially without axial retaining means rotating with the coupling
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- G—PHYSICS
- G03—PHOTOGRAPHY; CINEMATOGRAPHY; ANALOGOUS TECHNIQUES USING WAVES OTHER THAN OPTICAL WAVES; ELECTROGRAPHY; HOLOGRAPHY
- G03G—ELECTROGRAPHY; ELECTROPHOTOGRAPHY; MAGNETOGRAPHY
- G03G21/00—Arrangements not provided for by groups G03G13/00 - G03G19/00, e.g. cleaning, elimination of residual charge
- G03G21/16—Mechanical means for facilitating the maintenance of the apparatus, e.g. modular arrangements
- G03G21/18—Mechanical means for facilitating the maintenance of the apparatus, e.g. modular arrangements using a processing cartridge, whereby the process cartridge comprises at least two image processing means in a single unit
- G03G21/1839—Means for handling the process cartridge in the apparatus body
- G03G21/1857—Means for handling the process cartridge in the apparatus body for transmitting mechanical drive power to the process cartridge, drive mechanisms, gears, couplings, braking mechanisms
- G03G21/186—Axial couplings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
- F16D2001/102—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via polygon shaped connections
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- G—PHYSICS
- G03—PHOTOGRAPHY; CINEMATOGRAPHY; ANALOGOUS TECHNIQUES USING WAVES OTHER THAN OPTICAL WAVES; ELECTROGRAPHY; HOLOGRAPHY
- G03G—ELECTROGRAPHY; ELECTROPHOTOGRAPHY; MAGNETOGRAPHY
- G03G2221/00—Processes not provided for by group G03G2215/00, e.g. cleaning or residual charge elimination
- G03G2221/16—Mechanical means for facilitating the maintenance of the apparatus, e.g. modular arrangements and complete machine concepts
- G03G2221/1651—Mechanical means for facilitating the maintenance of the apparatus, e.g. modular arrangements and complete machine concepts for connecting the different parts
- G03G2221/1657—Mechanical means for facilitating the maintenance of the apparatus, e.g. modular arrangements and complete machine concepts for connecting the different parts transmitting mechanical drive power
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T403/00—Joints and connections
- Y10T403/70—Interfitted members
- Y10T403/7005—Lugged member, rotary engagement
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T403/00—Joints and connections
- Y10T403/70—Interfitted members
- Y10T403/7098—Non-circular rod section is joint component
Definitions
- This invention relates to the field of mechanically transmitting rotational force from a drive mechanism that is coupled to another rotational device.
- the invention can be used in general situations when a drive shaft is coupled to a driven apparatus.
- the preferred embodiment of the invention is used in the field of electrostatographic image forming devices such as copiers, facsimile machines, electrophotography printers, and replaceable or changeable cartridges for these devices, such as a toner cartridge for a laser printer.
- a detachable developer cylinder that contains a photosensitive member.
- the cylinder is also known as a cartridge or developer cartridge, and it is detachably mounted to the complete copier or printer. This construction enables users to maintain the printing capability of the device without the aid of a serviceman.
- the developer cylinder must be coupled to a drive mechanism that rotates the cartridge. Typically this is accomplished by a driving member with a hole or recess that couples with a projecting end in the driven member, which includes the cartridge.
- U.S. Patent No. 5,987,287 to Huang which is incorporated by reference into this disclosure, is a typical attempt to address the problems of connecting the developer cylinder.
- FIG. 1 of Huang depicts a typical prior art coupling and is the reference on which the following description is based.
- the drive coupling includes a drive shaft B that is centered in drive gear A that, in turn, drives developer cylinder E.
- the end of developer cylinder E has a fixedly mounted a flange that includes a transmission gear F and triangular coupling block D that fits in coupling recess C, which is disposed at the end of drive shaft B.
- Recess C is a twisted triangular hole
- coupling block D is a twisted triangle that is engageable with recess C.
- the driven end of the cylinder is typically made of plastic.
- many prior art couplings including those in commercial use, include some form of pin and hole that assist the coaxial alignment of the driving and driven portions of the coupling. Because the torque on twisted coupling block D of Huang is concentric to its three pointed vertices, the driven cylinder flange with its projection and the driving mechanism both encounter high stresses.
- a triangular projection fits in a larger triangular recess without the two pieces engaging.
- FIG. 18b depicts the relative rotation of the two pieces such that they engage where the tips of the smaller triangle meet the flat sides of the larger recess.
- the relative sizes of the projection and recess, and the lack of precise engagement, occur because replacing the developer cartridge requires some dimensional tolerance.
- Many existing machines use a triangular or twisted triangular recess as the driving mechanism and some form of triangular driven mechanism.
- Karz uses a triangular recess that engages with three skewed blades mounted on a rod.
- Cho uses a tapered recess with spiral protrusions that engages with a tapered shaft that has spiral sloping ribs.
- Wang et al describes a triangular recess coupling with a shaft that has a plurality of teeth spaced spirally around the shaft. Wang has circular spiral teeth, not the more adaptable and effective helical involute teeth of the present invention.
- Jin emphasizes the tradeoffs between accuracy and wear, highlighting that his invention involves point rather than surface contact. According to Jin, that arrangement - point contact - makes torque transmission more mechanically reliable, which in turn makes the printing more accurate.
- the point contact hastens the wear of the driving and driven mechanisms because of the stress concentration at the point. Jin is also more likely to damage the recess of the driving mechanism, which affects the coaxial alignment of the driving and driven mechanisms and thus causes the print quality to deteriorate as the coupling wears. If the wear to the recess of the driving mechanism is too great, the driving mechanism could require replacement. This part of the device is much more difficult to remove and repair than simply replacing a plastic cartridge that contains a developer cylinder with ink or toner. During the life of a device such as a printer or facsimile, the developer cartridge may be replaced many times, depending on the design of the device and the user's printing needs.
- a successful mechanical coupling must be designed in a way to 1) maximize the torque that can be transferred from the driving mechanism to the driven mechanism and the developer cylinder; 2) maintain the coaxial alignment of the driving and driven mechanism, which also maintains the accuracy of the printing process; 3) minimize the wear on the driving and driven mechanisms, which in turn maintains the accuracy and reduces the maintenance cost of the machine; 4) maintain the coupling's dimensional tolerances to facilitate easy replacement of the cartridge with the developer cylinder; and, 5) render a low manufacture cost.
- the present invention is a substantial improvement to the mechanical coupling, because manufacture and maintenance costs can be reduced without sacrificing printing accuracy.
- the stress transferred from the torque generated between the driving mechanism and the driven mechanism is reduced while the coaxial alignment of the driving and driven portions of the coupling is maintained.
- more powerful torque may be transferred with the same size coupling or, alternatively, materials of less strength (and less cost) may be used in fabricating the coupling.
- the invention includes a plurality of helical involute teeth projecting from a cylinder, as shown in FIG. 1.
- the teeth engage with a twisted, preferably petaline recess or coupling hole in the drive shaft, as shown in FIGS. 2 and 3.
- the invention permits the involute teeth and petaline recess to engage each other so that a curved surface of the gear and a curved surface of the recess engage in three locations. Moreover, this engagement minimizes the shear stress, maximizes the compression force, and distributes the compression force over a greater surface area on the tooth and on the side of the recess. Greater shear means more wear, less printing accuracy, and a greater chance of failure. In testing, these ends of the developer cylinder have outlasted the prior art coupling ends. This endurance, which results from emphasizing the compression force over the shear and spreading it out over a larger area, ultimately means less part wear, less maintenance cost, and greater printing accuracy.
- One embodiment of the invention includes a driving member having an end portion; a driven member having an end portion that is engageable with the driving member; a petaline recess defined by petaline sides and disposed in the end portion of the driving member; a projection disposed on the end portion of the driven member that is coaxially and rotationally engageable with the petaline recess, the projection comprising a plurality of teeth constructed on a base cylinder; and, wherein rotation of the driving member causes the sides of the petaline recess to drivably engage with the teeth.
- the diameter of a base circle defines the shape and the placement of the helical involute teeth, is approximately 0.25 to 0.57 of the side of a triangle defined by vertices in the recess, although the invention is not limited by that ratio. Ratios on the order of 1/6 to 3/4, i.e., about 0.16 to 0.75, are acceptable limits of the invention.
- the helix angle the angle between a helix tooth and the axial line on its cylinder, is approximately 0 to 40 degrees.
- the teeth can be comprised of twisted or helical cycloid curves.
- Other embodiments are also contemplated, such as three helical involute teeth that are not connected by a center cylinder.
- FIG. 1 is a perspective view of the invention's helical involute teeth and recess;
- FIG. 2 is a cross-sectional view along the line A-A in FIG. 1 after the projection is inserted into the twisted petaline recess but has not yet engaged with the helical involute teeth;
- FIG. 3 is a cross-sectional view similar to FIG. 2 with the twisted petaline recess engaged with the helical involute teeth;
- FIG. 4 is a perspective view of another embodiment of the twisted involute coupling in which the helical involute teeth are not connected to a center cylinder;
- FIG. 5 is a cross-sectional view of along the line B-B in FIG. 4 after the projection is inserted into the recess but is not yet engaged with the helical involute teeth;
- FIG. 6 is a cross-sectional view similar to FIG. 5 in which the recess is engaged with the helical involute teeth;
- FIG. 7 is a cross-sectional view similar to FIG. 2 illustrating an alternative recess.
- FIG. 8 is a cross-sectional view similar to FIG. 3 illustrating the alternative recess of FIG.
- FIGS. 1-3 depict a preferred embodiment of the present invention.
- Drive gear 101 includes a gear shaft 103 at its center and an outside edge 102 having gear teeth.
- Gear shaft 103 has a front surface 104, which includes a twisted petaline recess 105 having defined vertices 106a, 106b, 106c formed therein.
- the twisted petaline recess 105 is engageable with the plurality of helical involute teeth 116a, 116b, 116c.
- Driven coupling 110 is attached to photosensitive drum 118 of a replaceable or changeable developer cylinder and has geared driven shaft cylinder 112 that includes shaft cylinder flange 111.
- Concentric shaft 113 extends longitudinally outwardly from shaft cylinder flange 111.
- Concentric shaft 113 includes a front surface 114 from which extends an engagement projection 115 that has a plurality of helical involute teeth 116 extending radially outward from the centerline of rotation of driven shaft cylinder 112, concentric shaft 113, and engagement projection 115.
- the plurality of helical involute teeth 116a, 116b, 116c are adapted to fit within twisted petaline recess 105 shown in driving shaft 103 of driving coupling member 100.
- the helical involute teeth 116 are constructed on a helical petaline cylinder along the axis of rotation AR of the driven coupling 110.
- FIG. 2 depicts the initial, non-rotational engagement of the driving and driven couplings 100, 110 shown in FIG. 1.
- Recess 105 in gear shaft 103 is petaline (or petaloid) shaped, with three petal tips 106a, 106b, 106c. In the preferred embodiment the three petal tips are pointed.
- the three tips 106 define an equilateral triangle with center C2 and side length T.
- FIG. 2 also depicts engagement projection 115 that includes three helical involute teeth 116a, 116b, 116c that preferably have flattened tips 117a, 117b, 117c.
- Engagement projection 115 is preferably symmetrical and has a center CI .
- centers CI and C2 do not coincide.
- driving shaft 103 rotates in the direction of arrow A
- the surface areas near or adjacent the flattened tips 117a, 117b, 117c of teeth 116a, 116b, 116c eventually contact the sides 105a, 105b, 105c of recess 105.
- centers CI and C2 become concentric, which places driving coupling 100 and driven coupling 110 in coaxial alignment. From this single center there is the Base Circle BC of diameter D, as shown in FIG. 3.
- the profile of teeth 116a, 116b, 116c is the involute of the Base Circle.
- the involute curves of teeth 116a, 116b, 116c engage recess 105 at the rounded sides 105a, 105b, 105c.
- Hole or recess 119 in projection 115 is adapted to receive a pin (not shown) in recess 105 to facilitate co-axial alignment.
- Various pin-and-hole arrangements are known in the prior art and are currently used in commercial applications.
- the invention's configuration distributes the shear and compressive forces far better than if the teeth were simply a twisted triangle or circular segments like those of Wang et al.
- the projection 115 has larger surface areas that contact with recess 105 and in turn permit any compressive force to be distributed over more area, thus lessening the stress. A greater area also improves the frictional engagement that develops from the shear stresses.
- the maximum radius of each tooth is between approximately 50% to 75% the radius of each petal tip.
- the coupling can substantially increase the torque transmission from the driving to the driven mechanism.
- the configuration of a helical involute tooth depends on several parameters, including the helix angle of the tooth and the radius of the base cylinder to which the tooth is attached.
- the preferable range for the helix angle of the tooth is approximately 15 to 30 degrees.
- the helix angle is measured between a helix tooth and the axial line on the base cylinder of the tooth.
- the radius of base circle BC is ordinarily not the same as the radius of the base cylinder 120 of the helical involute tooth.
- diameter D of the base circle BC is less than the diameter of the base cylinder 120 to which teeth 116a, 116b, 116c is attached.
- the base cylinder 120 has center CI and the edge of the base cylinder 120 is a circle defined by points 116m, 116n, 116o.
- the coupling should not be limited in use to electrophotographic, xerographic, or other copying, printing, and document production devices. It could, for example, find use in the automobile industry, in which sp lined shaft and sleeve couplings have been used in transmissions.
- the petaline projection may be part of a conical or cylindrical structure.
- the drive mechanism and driven mechanism could switch functions. In other words, drive coupling 100 and driven coupling 110 would retain the same or similar structure, but drive coupling 100 would be the driven coupling and driven coupling 110 would become the drive coupling.
- diameter D should not be limited to the preferred range. Depending upon its application, the invention may require, say, larger forces for which smaller tolerances are a necessary
- FIGS. 4-6 depict an alternate embodiment, with the numerals generally corresponding to the numerals in FIGS. 1-3. When engaged, as depicted in FIG. 6, driving member 200 in FIG.
- teeth 216a, 216b, 216c are separate structures, whereas in FIGS. 1-3 teeth 116a, 116b, 116c are part of a unitary helical involute projection 115 that has a cylindrical center. In FIGS. 5-6, a cylinder of material has been removed from the projection.
- sides 216x, 216y, 216z could be circular arcs.
- the sides could be flat.
- circle BC with diameter D' can be an imaginary construct that facilitates designing the relationship between teeth 216a,b,c and recess 205.
- the petaline recess 205 could be designed to that tips 206a, 206b, 206c, which define triangle T ' , exist inside the empty space of recess 205 or within the material of gear shaft 203.
- FIG. 2 the three petals are depicted as part of the projection 115.
- FIG. 3 the three petals are depicted as separate teeth 116a, 116b, 116c.
- Some in the art would refer to projection as a single helical involute gear or a portion of such gear.
- Other uses and variations of the invention will become apparent to those skilled in the art. Therefore, it is intended that the invention not be limited to the particular embodiments or uses described here, but that the invention will include all embodiments falling within the scope of the claims.
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Abstract
A rotatable coupling is used with a replaceable developer cartridge and electrostatographic image devices. The coupling has a driven portion and a driving portion. The driven portion has a shaft with a connecting portion that has a plurality of helical involute teeth extending outwardly. The driving portion has an end with a gear shaft and a twisted petaline recess in the gear shaft. The sides of the recess are engageable with the helical involute teeth so that the driving portion drives the driven portion and transmit torque.
Description
ROTATING DRIVE SHAFT COUPLING
Field of the Invention
This invention relates to the field of mechanically transmitting rotational force from a drive mechanism that is coupled to another rotational device. The invention can be used in general situations when a drive shaft is coupled to a driven apparatus. The preferred embodiment of the invention is used in the field of electrostatographic image forming devices such as copiers, facsimile machines, electrophotography printers, and replaceable or changeable cartridges for these devices, such as a toner cartridge for a laser printer.
Background of the Invention
Many electrophotographic machines, such as photocopiers or laser printers, use a detachable developer cylinder that contains a photosensitive member. The cylinder is also known as a cartridge or developer cartridge, and it is detachably mounted to the complete copier or printer. This construction enables users to maintain the printing capability of the device without the aid of a serviceman.
The developer cylinder must be coupled to a drive mechanism that rotates the cartridge. Typically this is accomplished by a driving member with a hole or recess that couples with a projecting end in the driven member, which includes the cartridge. U.S. Patent No. 5,987,287 to Huang, which is incorporated by reference into this disclosure, is a typical attempt to address the problems of connecting the developer cylinder. FIG. 1 of Huang depicts a typical prior art coupling and is the reference on which the following description is based. The drive coupling includes a drive shaft B that is centered in drive gear A that, in turn, drives developer cylinder E. The end of developer cylinder E has a fixedly mounted a flange that includes a transmission gear F and triangular coupling block D that fits in coupling recess C, which is disposed at the end of drive shaft B. Recess C is a twisted triangular hole, while coupling block D is a twisted triangle that is engageable with recess C. The driven end of the cylinder is typically made of plastic. Although not shown in Huang, many prior art couplings, including those in commercial use, include some form of pin and hole that assist the coaxial alignment of the driving and driven portions of the coupling.
Because the torque on twisted coupling block D of Huang is concentric to its three pointed vertices, the driven cylinder flange with its projection and the driving mechanism both encounter high stresses. An example of this problematic arrangement can be seen in FIG. 18 of U.S. Patent No. 5,903,803 to Kawai et al. In FIG. 18a a triangular projection fits in a larger triangular recess without the two pieces engaging. FIG. 18b depicts the relative rotation of the two pieces such that they engage where the tips of the smaller triangle meet the flat sides of the larger recess. The relative sizes of the projection and recess, and the lack of precise engagement, occur because replacing the developer cartridge requires some dimensional tolerance. Many existing machines use a triangular or twisted triangular recess as the driving mechanism and some form of triangular driven mechanism.
In an effort to reduce the stress where the driving and driven portions of the coupling engage, some have tried beveling the triangular tips in an attempt to achieve a greater contact area between the triangular tips and the sides of the recess into which it fits. See, e.g., Kawai FIGS. 19a and 19b. Other examples of attempted solutions to the coupling problem can be seen in U.S. Patent No. 7,433,631 to Karz et al; U.S. Patent No. 6,768,890 to Cho et al; U.S. Patent No. 6,173,146 to Wang et al; and, U.S. Patent Appl. No. 2010/0196047 to Jin. Karz uses a triangular recess that engages with three skewed blades mounted on a rod. Cho uses a tapered recess with spiral protrusions that engages with a tapered shaft that has spiral sloping ribs. Wang et al describes a triangular recess coupling with a shaft that has a plurality of teeth spaced spirally around the shaft. Wang has circular spiral teeth, not the more adaptable and effective helical involute teeth of the present invention. Jin emphasizes the tradeoffs between accuracy and wear, highlighting that his invention involves point rather than surface contact. According to Jin, that arrangement - point contact - makes torque transmission more mechanically reliable, which in turn makes the printing more accurate. The point contact, however, hastens the wear of the driving and driven mechanisms because of the stress concentration at the point. Jin is also more likely to damage the recess of the driving mechanism, which affects the coaxial alignment of the driving and driven mechanisms and thus causes the print quality to deteriorate as the coupling wears. If the wear to the recess of the driving mechanism is too great, the driving mechanism could require replacement. This part of the device is much more difficult to remove and repair than simply replacing a plastic cartridge that contains a developer cylinder with ink or toner.
During the life of a device such as a printer or facsimile, the developer cartridge may be replaced many times, depending on the design of the device and the user's printing needs. A successful mechanical coupling must be designed in a way to 1) maximize the torque that can be transferred from the driving mechanism to the driven mechanism and the developer cylinder; 2) maintain the coaxial alignment of the driving and driven mechanism, which also maintains the accuracy of the printing process; 3) minimize the wear on the driving and driven mechanisms, which in turn maintains the accuracy and reduces the maintenance cost of the machine; 4) maintain the coupling's dimensional tolerances to facilitate easy replacement of the cartridge with the developer cylinder; and, 5) render a low manufacture cost. Despite the numerous designs of mechanical couplings, both for devices like photocopiers and facsimiles as well as for other types of mechanical couplings, there remains a need for an improved rotational coupling that will overcome all of these problems.
Summary of the Invention
The present invention is a substantial improvement to the mechanical coupling, because manufacture and maintenance costs can be reduced without sacrificing printing accuracy.
Because the twisted coupling hole or recess is engaged with a plurality of helical involute teeth, the stress transferred from the torque generated between the driving mechanism and the driven mechanism is reduced while the coaxial alignment of the driving and driven portions of the coupling is maintained. As a result, more powerful torque may be transferred with the same size coupling or, alternatively, materials of less strength (and less cost) may be used in fabricating the coupling.
The invention includes a plurality of helical involute teeth projecting from a cylinder, as shown in FIG. 1. The teeth engage with a twisted, preferably petaline recess or coupling hole in the drive shaft, as shown in FIGS. 2 and 3. The invention permits the involute teeth and petaline recess to engage each other so that a curved surface of the gear and a curved surface of the recess engage in three locations. Moreover, this engagement minimizes the shear stress, maximizes the compression force, and distributes the compression force over a greater surface area on the tooth and on the side of the recess. Greater shear means more wear, less printing accuracy, and a greater chance of failure. In testing, these ends of the developer cylinder have outlasted the prior art coupling ends. This endurance, which results from emphasizing the compression force over
the shear and spreading it out over a larger area, ultimately means less part wear, less maintenance cost, and greater printing accuracy.
One embodiment of the invention includes a driving member having an end portion; a driven member having an end portion that is engageable with the driving member; a petaline recess defined by petaline sides and disposed in the end portion of the driving member; a projection disposed on the end portion of the driven member that is coaxially and rotationally engageable with the petaline recess, the projection comprising a plurality of teeth constructed on a base cylinder; and, wherein rotation of the driving member causes the sides of the petaline recess to drivably engage with the teeth.
In a preferred embodiment the diameter of a base circle, defines the shape and the placement of the helical involute teeth, is approximately 0.25 to 0.57 of the side of a triangle defined by vertices in the recess, although the invention is not limited by that ratio. Ratios on the order of 1/6 to 3/4, i.e., about 0.16 to 0.75, are acceptable limits of the invention. Preferably, the helix angle, the angle between a helix tooth and the axial line on its cylinder, is approximately 0 to 40 degrees.
In another embodiment, the teeth can be comprised of twisted or helical cycloid curves. Other embodiments are also contemplated, such as three helical involute teeth that are not connected by a center cylinder.
Brief Description of the Drawings
The objects and advantages of the invention will become apparent to and appreciated by those of skill in the art from the following detailed description of the invention, including the preferred embodiment, in conjunction with the accompanying drawings of which:
FIG. 1 is a perspective view of the invention's helical involute teeth and recess;
FIG. 2 is a cross-sectional view along the line A-A in FIG. 1 after the projection is inserted into the twisted petaline recess but has not yet engaged with the helical involute teeth;
FIG. 3 is a cross-sectional view similar to FIG. 2 with the twisted petaline recess engaged with the helical involute teeth;
FIG. 4 is a perspective view of another embodiment of the twisted involute coupling in which the helical involute teeth are not connected to a center cylinder;
FIG. 5 is a cross-sectional view of along the line B-B in FIG. 4 after the projection is inserted into the recess but is not yet engaged with the helical involute teeth;
FIG. 6 is a cross-sectional view similar to FIG. 5 in which the recess is engaged with the helical involute teeth;
FIG. 7 is a cross-sectional view similar to FIG. 2 illustrating an alternative recess; and
FIG. 8 is a cross-sectional view similar to FIG. 3 illustrating the alternative recess of FIG.
7.
Detailed Description of the Illustrative Embodiments
FIGS. 1-3 depict a preferred embodiment of the present invention. Mounted on the end of developer cylinder 118 is a driven member or driven coupling 110 that is adapted to engage with driving member or driving coupling 100. Drive gear 101 includes a gear shaft 103 at its center and an outside edge 102 having gear teeth. Gear shaft 103 has a front surface 104, which includes a twisted petaline recess 105 having defined vertices 106a, 106b, 106c formed therein. The twisted petaline recess 105 is engageable with the plurality of helical involute teeth 116a, 116b, 116c.
Driven coupling 110 is attached to photosensitive drum 118 of a replaceable or changeable developer cylinder and has geared driven shaft cylinder 112 that includes shaft cylinder flange 111. Concentric shaft 113 extends longitudinally outwardly from shaft cylinder flange 111. Concentric shaft 113 includes a front surface 114 from which extends an engagement projection 115 that has a plurality of helical involute teeth 116 extending radially outward from the centerline of rotation of driven shaft cylinder 112, concentric shaft 113, and engagement projection 115. The plurality of helical involute teeth 116a, 116b, 116c are adapted to fit within twisted petaline recess 105 shown in driving shaft 103 of driving coupling member 100. The helical involute teeth 116 are constructed on a helical petaline cylinder along the axis of rotation AR of the driven coupling 110.
FIG. 2 depicts the initial, non-rotational engagement of the driving and driven couplings 100, 110 shown in FIG. 1. Recess 105 in gear shaft 103 is petaline (or petaloid) shaped, with three petal tips 106a, 106b, 106c. In the preferred embodiment the three petal tips are pointed. The three tips 106 define an equilateral triangle with center C2 and side length T. FIG. 2 also depicts engagement projection 115 that includes three helical involute teeth 116a, 116b, 116c that preferably have flattened tips 117a, 117b, 117c. Engagement projection 115 is preferably symmetrical and has a center CI . In FIG. 2, when engagement projection 115 is not engaged with the sides of recess 105, centers CI and C2 do not coincide. When driving shaft 103 rotates in the direction of arrow A, the surface areas near or adjacent the flattened tips 117a, 117b, 117c of teeth 116a, 116b, 116c eventually contact the sides 105a, 105b, 105c of recess 105. At this point centers CI and C2 become concentric, which places driving coupling 100 and driven coupling 110 in coaxial alignment. From this single center there is the Base Circle BC of diameter D, as shown in FIG. 3. The profile of teeth 116a, 116b, 116c is the involute of the Base Circle. The involute curves of teeth 116a, 116b, 116c engage recess 105 at the rounded sides 105a, 105b, 105c. Hole or recess 119 in projection 115 is adapted to receive a pin (not shown) in recess 105 to facilitate co-axial alignment. Various pin-and-hole arrangements are known in the prior art and are currently used in commercial applications.
As noted above, the invention's configuration distributes the shear and compressive forces far better than if the teeth were simply a twisted triangle or circular segments like those of Wang et al. The projection 115 has larger surface areas that contact with recess 105 and in turn permit any compressive force to be distributed over more area, thus lessening the stress. A greater area also improves the frictional engagement that develops from the shear stresses.
Experience with the invention has established a preferable range for diameter D: approximately 0.25 to 0.57 of the length of side T of the inscribed triangle of recess 105 shown in FIG. 2. A larger range, on the order of 0.16 to 0.75, can be used. As D increases the involute curve becomes flatter, so that a more powerful torque can be transmitted. At the same time, however, the tolerance for reinstalling the replaceable developer cylinder decreases. Similarly, as D decreases the tolerance for reinstallation increases, but the radius of curvature of the involute curve of the teeth decreases, decreasing the amount of torque that can be transmitted through the coupling and increasing the shear stress in the coupling. Nevertheless, testing of the invention has demonstrated that it is a significant improvement over the prior art. Even when the helical
involute teeth are used with a typical prior art triangular recess 105' as shown in FIGS. 7 and 8, the performance of the torque driving mechanism is significantly improved. In a triangular prior art recess the radius of curvature of each side T of the recess 105' is infinity, because each side of the recess 105' is flat. Nevertheless, the flatness of the involute curve on the side of the teeth 116a, 116b, 116c (i.e., a greater radius of curvature of the side of the tooth) enables greater stability, because there is a greater surface area of engagement between each tooth surface and the surface of the recess 105'. In either configuration, it is preferred that the maximum radius of each tooth is between approximately 50% to 75% the radius of each petal tip. As a result, the coupling can substantially increase the torque transmission from the driving to the driven mechanism. Alternatively, if greater torque is not necessary, the torque of the driving
mechanism can be reduced, which results in less stress, longer part life, continued precise coaxial alignment, and printing accuracy.
As those of skill in the art will understand, the configuration of a helical involute tooth depends on several parameters, including the helix angle of the tooth and the radius of the base cylinder to which the tooth is attached. The preferable range for the helix angle of the tooth is approximately 15 to 30 degrees. The helix angle is measured between a helix tooth and the axial line on the base cylinder of the tooth. It should be emphasized that the radius of base circle BC is ordinarily not the same as the radius of the base cylinder 120 of the helical involute tooth. For example, in FIG. 3 diameter D of the base circle BC is less than the diameter of the base cylinder 120 to which teeth 116a, 116b, 116c is attached. In FIG. 3, the base cylinder 120 has center CI and the edge of the base cylinder 120 is a circle defined by points 116m, 116n, 116o.
The preceding description represents a preferred embodiment of the invention.
Nevertheless, all modifications and variations to the invention claimed below, whether specified or not, should be considered within the scope of the claims. For example, the coupling should not be limited in use to electrophotographic, xerographic, or other copying, printing, and document production devices. It could, for example, find use in the automobile industry, in which sp lined shaft and sleeve couplings have been used in transmissions. The petaline projection may be part of a conical or cylindrical structure. Depending on how the coupling is used, the drive mechanism and driven mechanism could switch functions. In other words, drive coupling 100 and driven coupling 110 would retain the same or similar structure, but drive coupling 100 would
be the driven coupling and driven coupling 110 would become the drive coupling. Likewise, diameter D should not be limited to the preferred range. Depending upon its application, the invention may require, say, larger forces for which smaller tolerances are a necessary
consequence.
Although the preceding description is the preferred embodiment, it is possible to implement the invention by using only the unconnected helical involute teeth. As noted above, these teeth can be used to engage a triangular or twisted triangular recess. That way the helical involute teeth can function with prior art recesses in the driving mechanism of existing printing devices that are still in use. As the preferred petaline recess becomes commercially implemented with the helical involute teeth, the mechanical life of the both the driving and driven portions of the coupling will continue to improve. For example, FIGS. 4-6 depict an alternate embodiment, with the numerals generally corresponding to the numerals in FIGS. 1-3. When engaged, as depicted in FIG. 6, driving member 200 in FIG. 4 couples with and rotates driven member 210, which is attached to developer cylinder 218. The rotation in the direction of arrow A' causes the helical involute profiles of teeth 216a, 216b, 216c of the driven member 210 to engage with the sides 205a, 205b, 205c defining recess 205. As depicted in FIGS. 4-6, teeth 216a, 216b, 216c are separate structures, whereas in FIGS. 1-3 teeth 116a, 116b, 116c are part of a unitary helical involute projection 115 that has a cylindrical center. In FIGS. 5-6, a cylinder of material has been removed from the projection. It should be noted that it is unnecessary for sides 216x, 216y, 216z to be circular arcs. The sides could be flat. In an embodiment such as the one in FIGS. 4-6 circle BC with diameter D' can be an imaginary construct that facilitates designing the relationship between teeth 216a,b,c and recess 205. Similarly, the petaline recess 205 could be designed to that tips 206a, 206b, 206c, which define triangle T', exist inside the empty space of recess 205 or within the material of gear shaft 203.
Those of skill in the art will also understand that there can be variations in the
terminology used to describe the invention. For example, in FIG. 2 the three petals are depicted as part of the projection 115. In FIG. 3 the three petals are depicted as separate teeth 116a, 116b, 116c. Some in the art would refer to projection as a single helical involute gear or a portion of such gear. Other uses and variations of the invention will become apparent to those skilled in the art. Therefore, it is intended that the invention not be limited to the particular embodiments or
uses described here, but that the invention will include all embodiments falling within the scope of the claims.
Claims
1. A drive coupling for transferring a rotational force, comprising:
a first member having an end portion;
a second member having an end portion that is engageable with the first member;
a petaline recess defined in the end portion of the first member, the petaline recess having a recess axis and including a plurality of interconnected petal shaped recess portions about the axis, each petal shaped recess portion including petaline sides interconnecting at a petal tip with the petaline sides of adjacent recess portions meeting at a common plane;
a projection disposed on the end portion of the second member that is coaxially and rotationally engageable with the petaline recess, the projection comprising a plurality of teeth about a projection axis;
wherein one of the first or second members is a driving member and the other is a driven member such that rotation of the driving member causes engagement between each tooth and a respective petaline side whereby the recess axis and the projection axis become coaxial and the driven member is driven, and
wherein a radius of each tooth as measured from a center of the projection to a tip of the tooth is substantially less than the radius of each petal tip as measured from a center of the recess such that the position of the center of the projection relative to the center of the recess is radially adjustable.
2. The drive coupling of claim 1, wherein the projection has a base circle with a diameter and straight lines between adjacent petal tips define a regular polygon.
3. The drive coupling of claim 1, wherein the petaline recess has symmetrically three petal shaped recess portions.
4. The drive coupling of claim 3, wherein the projection comprises three teeth.
5. The drive coupling of claim 4, wherein a profile of each tooth is defined by an involute curve.
6. The drive coupling of claim 1, wherein the teeth are helical.
7. The drive coupling of claim 1, wherein the maximum radius of each tooth is approximately 75% or less than the radius of each petal tip.
8. The drive coupling of claim 2, wherein each tooth has a profile defined by an involute curve which is a function of the base circle diameter.
9. The drive coupling of claim 8, wherein the diameter of the base circle is about 0.25 to 0.57 of the length of a side of the regular polygon.
10. The drive coupling of claim 8, wherein the diameter of the base circle is about 0.16 to 0.75 of the length of a side of the regular polygon.
11. The drive coupling of claim 1, wherein the projection comprises a plurality of symmetrical, helical involute teeth.
12. The drive coupling of claim 11, wherein the petaline recess is symmetrical and helical and comprises the same number of petal recess portions as the number of teeth on the projection.
13. The drive coupling of claim 12, wherein the teeth are each at a tooth helix angle relative to the projection axis and the petal recess portions are each at a recess helix angle relative to the recess axis, and wherein the tooth helix angle and the recess helix angle are equal.
14. The drive coupling of claim 13, wherein the tooth and recess helix angles are about 15 to 30 degrees.
15. The drive coupling of claim 1, wherein the first member is the driving member and the second member is the driven member.
16. The drive coupling of claim 4, wherein the teeth are shaped based on a cycloid curve.
17. The drive coupling of claim 13, wherein the tooth and recess helix angles are between 0 (zero) and 40 degrees.
18. The drive coupling of claim 1, wherein the first member is the driven member and the second member is the driving member.
19. A first member of a drive coupling for transferring a rotational force between the first member and a second member having an end portion with a helical recess defined therein, the recess having a recess axis and including a plurality of interconnected recess portions about the axis, each recess portion including sides interconnecting at a recess tip with the sides of adjacent recess portions meeting at a common plane, each recess portion is defined by straight sides between adjacent recess tips such that the recess has a regular polygon configuration, the first member comprising:
a helical projection disposed on an end portion of the first member that is configured to be coaxially and rotationally engaged with the recess, the projection comprising a plurality of teeth about a projection axis, each of the teeth having a profile defined by an involute curve or a cycloid curve;
wherein one of the first or second members is a driving member and the other is a driven member such that rotation of the driving member causes engagement between each tooth and a respective side whereby the recess axis and the projection axis become coaxial and the driven member is driven.
20. The drive coupling of claim 19, wherein each tooth extends radially from a base cylinder.
21. The drive coupling of claim 19, wherein the number of teeth is equal to the number of sides of the regular polygon.
22. The drive coupling of claim 19, wherein the number of teeth is equal to three.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP12827257.2A EP2751620B1 (en) | 2011-09-02 | 2012-08-16 | Rotating drive shaft coupling |
CN201280003861.4A CN103460146B (en) | 2011-09-02 | 2012-08-16 | The shaft coupling of rotary drive |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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US13/224,900 | 2011-09-02 | ||
US13/224,900 US8628269B2 (en) | 2011-09-02 | 2011-09-02 | Rotating drive shaft coupling |
Publications (1)
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WO2013032721A1 true WO2013032721A1 (en) | 2013-03-07 |
Family
ID=47753305
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/US2012/051072 WO2013032721A1 (en) | 2011-09-02 | 2012-08-16 | Rotating drive shaft coupling |
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US (2) | US8628269B2 (en) |
EP (1) | EP2751620B1 (en) |
CN (1) | CN103460146B (en) |
WO (1) | WO2013032721A1 (en) |
Families Citing this family (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8429968B2 (en) * | 2009-10-08 | 2013-04-30 | Moscow Mills, Inc. | Balance test indexing tool for balance-testing a rotor |
US8628269B2 (en) | 2011-09-02 | 2014-01-14 | Roy Fan | Rotating drive shaft coupling |
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US20130248315A1 (en) * | 2012-03-23 | 2013-09-26 | Mitsubishi Chemical Corporation | Rotating part for image forming apparatus, cartridge for forming image, and image forming apparatus |
US20130287488A1 (en) * | 2012-04-30 | 2013-10-31 | Mitsubishi Chemical Corporation | Drive transmission part for image forming apparatus |
DE102012207271A1 (en) * | 2012-05-02 | 2013-11-07 | Robert Bosch Gmbh | A method of connecting a shaft to a rotating member and a turbocharger shaft made by this method |
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US9164474B2 (en) * | 2013-01-08 | 2015-10-20 | Clover Technologies Group, Llc | Toner drum gear projection |
JP6504449B2 (en) * | 2014-08-27 | 2019-04-24 | 株式会社リコー | Drive transmission device and image forming apparatus |
JP6684477B2 (en) * | 2014-08-27 | 2020-04-22 | 株式会社リコー | Drive transmission device and image forming apparatus |
CA3135772A1 (en) * | 2015-02-27 | 2016-09-01 | Canon Kabushiki Kaisha | Drum unit, cartridge and coupling member |
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JP6657652B2 (en) * | 2015-08-12 | 2020-03-04 | 富士ゼロックス株式会社 | Driving force transmission device and image forming apparatus |
US10267335B1 (en) | 2015-09-23 | 2019-04-23 | Anthony Freakes | Methods and apparatus for mounting an impeller with positional repeatability |
CN108432101A (en) * | 2015-12-21 | 2018-08-21 | 艾坡泰克设备及不锈钢制品有限公司 | Electrical installation machine |
DE102017101741A1 (en) | 2017-01-30 | 2018-08-02 | Ebm-Papst St. Georgen Gmbh & Co. Kg | driving device |
CN107143586A (en) * | 2017-05-26 | 2017-09-08 | 广东志高暖通设备股份有限公司 | A kind of air-conditioning and its shaft coupling |
NO20190132A1 (en) * | 2019-01-31 | 2020-08-03 | Tocircle Ind As | Transmission |
WO2021071506A1 (en) | 2019-10-11 | 2021-04-15 | Hewlett-Packard Development Company, L.P. | Drive adapter |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH10153937A (en) * | 1996-09-26 | 1998-06-09 | Canon Inc | Electrophotographic image forming device and process cartridge |
US20070140735A1 (en) * | 2005-12-20 | 2007-06-21 | Xerox Corporation | Material supply module drive shaft |
US20080101858A1 (en) * | 2006-10-31 | 2008-05-01 | Xerox Corporation | Coupling apparatus |
US20090080936A1 (en) * | 2007-09-26 | 2009-03-26 | Xerox Corporation | Coupling mechanism for material supply module |
Family Cites Families (63)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1265889A (en) | 1916-01-05 | 1918-05-14 | Frederic Ecaubert | Coupling. |
US1381805A (en) * | 1919-12-09 | 1921-06-14 | Courtaulds Ltd | Spinning-box mounting |
US1912412A (en) * | 1931-10-16 | 1933-06-06 | Stubbs Everard | Splined shaft and sleeve couple |
US2567663A (en) | 1947-06-02 | 1951-09-11 | Deubel Joseph | Flexible coupling for shafts |
US2634991A (en) | 1948-11-13 | 1953-04-14 | William J Stevens | Splineless coupling machine element |
US2667373A (en) | 1949-07-20 | 1954-01-26 | Timken Roller Bearing Co | Rotary percussion drill |
US2813450A (en) | 1954-05-03 | 1957-11-19 | Dzus William | Rotatable fastener having circular toothed tool receiving groove |
US3013411A (en) | 1960-04-12 | 1961-12-19 | Gunnar A Wahlmark | Gear type constant velocity joint |
GB1185370A (en) * | 1967-12-18 | 1970-03-25 | Robert James Amos | A Coupling for Connecting Members for Rotation together about an Axis. |
AT281510B (en) | 1968-04-10 | 1970-05-25 | Gelenkwellenbau Gmbh | Quick-release tooth coupling |
US3529440A (en) | 1969-01-10 | 1970-09-22 | Scovill Manufacturing Co | Flexible coupling |
US3542178A (en) | 1969-03-25 | 1970-11-24 | Hoover Co | Flexible coupling for separable shafts |
US3545585A (en) | 1969-04-10 | 1970-12-08 | Proctor Silex Inc | Centrifugally interlocked coupling |
US3865500A (en) | 1973-07-09 | 1975-02-11 | E Strohm Newell | Locking handle |
US4046479A (en) | 1976-04-23 | 1977-09-06 | Paley Hyman W | Removable locking connector for luer fittings |
FR2356046A1 (en) | 1976-06-22 | 1978-01-20 | Gfd | Self-locking screw with socket head - is tightened by engagement of special tool with flap surfaces, on sides of equilateral triangle, with curved surfaces to prevent unscrewing |
US4074946A (en) | 1976-07-28 | 1978-02-21 | Swearingen Judson S | Shaft-rotor coupling |
US4288998A (en) | 1978-06-05 | 1981-09-15 | California Pellet Mill Company | Polylobe drive element |
US4685823A (en) * | 1980-12-23 | 1987-08-11 | The Boeing Company | Antibacklash shaft coupling |
DE3111771A1 (en) | 1981-03-25 | 1982-10-07 | Magyar Vagon- és Gépgyár, 9027 Györ | Method of producing radial control splines |
US4454922A (en) * | 1982-05-27 | 1984-06-19 | Consolidation Coal Company | Drill rod and drilling apparatus |
JPS59131485A (en) | 1983-01-18 | 1984-07-28 | Kyushu Matsushita Denki Kk | Ribbon cartridge |
JPS59228281A (en) | 1983-06-10 | 1984-12-21 | Fuji Xerox Co Ltd | Photosensitive body driving device of electrophotographic copying machine |
JPH0413190Y2 (en) | 1984-12-19 | 1992-03-27 | ||
DE3511534A1 (en) | 1985-03-29 | 1986-10-09 | Alfred Teves GmbH & Co oHG, 5275 Bergneustadt | Flexible shaft |
GB8516295D0 (en) | 1985-06-27 | 1985-07-31 | Northern Eng Ind | Lock & release device |
GB2180795B (en) | 1985-09-17 | 1990-08-29 | Canon Kk | Image bearing member and driving mechanism therefor |
DE3708418A1 (en) | 1987-03-14 | 1988-09-22 | Vdo Schindling | Coupling |
US4840259A (en) | 1987-12-03 | 1989-06-20 | Eastman Kodak Company | Drive mechanism for a reproduction apparatus |
US4975743A (en) | 1989-08-21 | 1990-12-04 | Surti Tyrone N | Process cartridge having removable drive means |
DE4117826A1 (en) | 1991-05-29 | 1992-12-03 | Brose Fahrzeugteile | Plug and socket shaft connection - has twisted plug or socket along part of connection length |
US5165881A (en) * | 1991-09-16 | 1992-11-24 | Opcon Autorotor Ab | Rotor for a screw rotor machine |
US5326114A (en) | 1992-04-08 | 1994-07-05 | Cincinnati Milacron, Inc. | Quickly interchangeable chuck with mechanical power assist clamping capabilities |
DE4215399A1 (en) | 1992-05-11 | 1993-11-18 | Braun Ag | Food processor, in particular multi-purpose food processor |
JP3285392B2 (en) | 1992-09-04 | 2002-05-27 | キヤノン株式会社 | Process cartridge and image forming apparatus |
JPH06258877A (en) | 1993-03-08 | 1994-09-16 | Ricoh Co Ltd | Image forming device |
JP3839932B2 (en) * | 1996-09-26 | 2006-11-01 | キヤノン株式会社 | Process cartridge, electrophotographic image forming apparatus, electrophotographic photosensitive drum and coupling |
JP2875203B2 (en) * | 1995-03-27 | 1999-03-31 | キヤノン株式会社 | Electrophotographic image forming apparatus, process cartridge, driving force transmitting component, and electrophotographic photosensitive drum |
US6226478B1 (en) * | 1996-03-21 | 2001-05-01 | Canon Kabushiki Kaisha | Process cartridge having drive mount for photosensitive drum |
US6240266B1 (en) * | 1996-03-21 | 2001-05-29 | Canon Kabushiki Kaisha | Process cartridge and drum mount for photosensitive drum |
JP4026895B2 (en) | 1996-09-26 | 2007-12-26 | キヤノン株式会社 | Electrophotographic image forming apparatus and process cartridge |
JP3745049B2 (en) * | 1996-09-26 | 2006-02-15 | キヤノン株式会社 | Process cartridge and electrophotographic image forming apparatus |
JP3745047B2 (en) | 1996-09-26 | 2006-02-15 | キヤノン株式会社 | Electrophotographic image forming apparatus and process cartridge |
US6604885B1 (en) * | 1997-10-30 | 2003-08-12 | Bayerische Motoren Werke Aktiengesellschaft | Torque transmitter connection assembly |
US5926673A (en) * | 1998-09-14 | 1999-07-20 | Lexmark International, Inc. | Driving mechanism for photosensitive image bearing drum in electrophotographic machines |
DE29901561U1 (en) * | 1999-01-29 | 1999-05-20 | General Plastic Industrial Co., Ltd., Wu-Chi, Taichung | Arrangement of a developer cylinder and a drive wheel |
US6173146B1 (en) * | 2000-01-21 | 2001-01-09 | Jui-Chi Wang | Developer cylinder and drive gear arrangement |
JP2002182446A (en) * | 2000-10-04 | 2002-06-26 | Canon Inc | Driving force transmission component, electrophotograhic photoreceptor drum, process cartridge and electrophotographic image forming device |
US6829455B2 (en) * | 2000-10-20 | 2004-12-07 | Canon Kabushiki Kaisha | Driving force transmission mechanism, image forming apparatus equipped with such a mechanism, and process unit of such an apparatus |
JP3542583B2 (en) * | 2001-02-02 | 2004-07-14 | キヤノン株式会社 | Process cartridge, electrophotographic photosensitive drum, electrophotographic image forming apparatus, and color electrophotographic image forming apparatus |
US6547479B2 (en) * | 2001-02-14 | 2003-04-15 | Ford Global Technologies, Inc. | Spline, an assembly utilizing the spline, and a method for transferring energy |
KR100381598B1 (en) | 2001-09-18 | 2003-04-26 | 삼성전자주식회사 | coupling apparatus and process cartridge and electrophotographic printer having the same |
KR100381601B1 (en) * | 2001-09-26 | 2003-04-26 | 삼성전자주식회사 | coupling apparatus and process cartridge and electrophotographic printer having the same |
JP2003307992A (en) * | 2002-04-17 | 2003-10-31 | Canon Inc | Process cartridge and electrophotographic image forming apparatus |
JP2003307931A (en) * | 2002-04-17 | 2003-10-31 | Canon Inc | Process cartridge and electrophotographic image forming apparatus |
US7236722B2 (en) | 2005-08-25 | 2007-06-26 | Lexmark International, Inc. | Helically splined drive member for an image forming device |
TWM306933U (en) | 2006-09-06 | 2007-03-01 | Hahntek Technology Corp | Improved driving structure of light-sensing drum of laser printer |
US7813676B2 (en) * | 2007-07-05 | 2010-10-12 | Static Control Components, Inc. | Systems and methods for remanufacturing imaging components |
CN201110941Y (en) * | 2007-08-23 | 2008-09-03 | 珠海天威技术开发有限公司 | Driving force transfer parts as well as processing box |
CN101649884B (en) * | 2008-08-15 | 2013-11-13 | 德昌电机(深圳)有限公司 | Transmission structure and motor assembly with same |
US20100296863A1 (en) * | 2009-05-22 | 2010-11-25 | Long Wing Scientific Enterprise Co., Ltd. | Transmission mechanism for toner cartridge |
KR101667927B1 (en) | 2009-05-29 | 2016-10-20 | 삼성전자 주식회사 | Image forming apparatus and power transmission unit thereof |
US8628269B2 (en) | 2011-09-02 | 2014-01-14 | Roy Fan | Rotating drive shaft coupling |
-
2011
- 2011-09-02 US US13/224,900 patent/US8628269B2/en active Active
-
2012
- 2012-08-16 CN CN201280003861.4A patent/CN103460146B/en active Active
- 2012-08-16 WO PCT/US2012/051072 patent/WO2013032721A1/en active Application Filing
- 2012-08-16 EP EP12827257.2A patent/EP2751620B1/en active Active
-
2013
- 2013-12-18 US US14/132,862 patent/US9284989B2/en active Active - Reinstated
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH10153937A (en) * | 1996-09-26 | 1998-06-09 | Canon Inc | Electrophotographic image forming device and process cartridge |
US20070140735A1 (en) * | 2005-12-20 | 2007-06-21 | Xerox Corporation | Material supply module drive shaft |
US20080101858A1 (en) * | 2006-10-31 | 2008-05-01 | Xerox Corporation | Coupling apparatus |
US20090080936A1 (en) * | 2007-09-26 | 2009-03-26 | Xerox Corporation | Coupling mechanism for material supply module |
Also Published As
Publication number | Publication date |
---|---|
EP2751620A1 (en) | 2014-07-09 |
US20130058710A1 (en) | 2013-03-07 |
US20140169868A1 (en) | 2014-06-19 |
EP2751620A4 (en) | 2016-07-27 |
EP2751620B1 (en) | 2019-01-02 |
US9284989B2 (en) | 2016-03-15 |
CN103460146A (en) | 2013-12-18 |
US8628269B2 (en) | 2014-01-14 |
CN103460146B (en) | 2017-03-01 |
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