US20070137355A1 - Gears and gearing apparatus - Google Patents
Gears and gearing apparatus Download PDFInfo
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- US20070137355A1 US20070137355A1 US11/528,651 US52865106A US2007137355A1 US 20070137355 A1 US20070137355 A1 US 20070137355A1 US 52865106 A US52865106 A US 52865106A US 2007137355 A1 US2007137355 A1 US 2007137355A1
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- Prior art keywords
- tooth
- gear
- teeth
- contact
- line contact
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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
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/08—Profiling
- F16H55/0886—Profiling with corrections along the width, e.g. flank width crowning for better load distribution
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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
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/14—Construction providing resilience or vibration-damping
- F16H55/16—Construction providing resilience or vibration-damping relating to teeth only
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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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/0006—Vibration-damping or noise reducing means specially adapted for gearings
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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
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19949—Teeth
- Y10T74/19963—Spur
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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
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19949—Teeth
- Y10T74/19963—Spur
- Y10T74/19972—Spur form
Definitions
- the present invention relates to gears and a gearing apparatus for transmitting a rotational motion between two associated shafts, i.e., from one to the other of two associated shafts, through a pair of gears which are engaged with each other so that teeth of the engaged gears are operatively mated with each other. More particularly, the present invention relates to gears and a gearing apparatus capable of reducing generation of noise during the rotational motion transmitting operation of a pair of gears engaged with each other, and also reducing an error in transmission of the rotational motion.
- gears in a conventional gearing apparatus typically, gears called standard gears having symmetrical tooth profiles are used.
- the tooth tip and the tooth root of each of teeth have identical tooth widths when measured in a direction along the axes of the respective gears and the total tooth depth of each tooth is unchanged and constant in a tooth width direction. Therefore, in the case where opposite teeth are mated with each other, since an amount of change in a spring constant of a tooth which functions as a type of spring between the double-teeth-mating arrangement and the single-tooth-mating arrangement, is large, sometimes, noise due to the mating of the gear teeth becomes large and also the vibration is increased. Further, the increase in the vibration of the mated gear teeth could often cause an increase in an error in the rotation transmission of the engaged gears.
- a gearing apparatus in which a pair of gears is configured by involute spur gears and at least one gear of the pair of gears is provided with rigidity reducing means incorporated therein for reducing the rigidity in the double-teeth-mating region of the said one gear, in comparison with the rigidity to be provided by the standard involute spur gear
- this rigidity reducing means in the gear for example, there is a through-hole formed in a gear, which runs through from one of end face of a tooth tip portion toward the other end face thereof.
- an object of the present invention is to provide firstly gears comprised of one and the other mutually engaged gears, and secondly a gearing apparatus capable of reducing noise generated when a pair of gears is engaged with each other and also, reducing an error in rotation transmission of the gears.
- the predetermined region in at least one tooth flank of each tooth of the one gear is formed in the configuration such that, from at least one place in the tooth width direction on the crossing of the tooth flank and the tooth tip surface, the mating of each tooth of the one gear with the teeth of the other engaged gear starts with point contact or the line contact shorter than the total tooth width and thereafter, gradually shifts to line contact so that the length of contact line thereof is continuously increased as the line contact moves from the tooth tip side toward the tooth root side.
- the contact at the mating time of the opposite teeth does not start firstly with the line contact on the tooth flank, but starts with the point contact or the line contact shorter than the total tooth width.
- the predetermined region in at least one tooth flank of each tooth is formed in the shape such that, from at least one place in the tooth width direction on the crossing of the tooth flank and the tooth tip surface, the mating with the teeth of the mating gear starts with the point contact or the line contact shorter than the total tooth width, and thereafter, rapidly or in stepwise shifts to the line contact of the total tooth width from the tooth tip side toward the tooth root side so that the length of contact line thereof is increased.
- the contact at the mating time of the opposite teeth does not start firstly with the line contact on the tooth flank, but starts with the point contact or the line contact shorter than the total tooth width.
- a gearing apparatus for transmitting a rotational motion from one to the other of associated two shafts by engaging a pair of gears to allow opposite teeth of the mating gears to be mated with each other, wherein for at least one gear of the pair of gears, a predetermined region in at least one of tooth flanks of each tooth is formed in a configuration such that mating of each tooth of the one gear with the teeth of the other engaged gear starts with a point contact or a line contact shorter than the total tooth width from at least one place in a tooth width direction on a crossing of the tooth flank and a tooth tip surface and thereafter, rapidly or in stepwise shifts to the line contact of the total tooth width from a tooth tip side toward a tooth root side so that the length of contact line thereof is increased.
- the contact at the mating time of the opposite teeth does not start firstly with the line contact of the total tooth width on the tooth flank, but starts with the point contact or the line contact shorter than the total tooth width. Then, the point contact rapidly or in stepwise moves to the line contact shorter than the total tooth width, and thereafter, further rapidly or in stepwise moves to the larger line contact within a range of the total tooth width. Further, the line contact shorter than the total tooth width then rapidly or in stepwise moves to the larger line contact within the range of the total tooth width. As a result, the contact to the teeth of the mating gear is softened and therefore, the shock can be absorbed.
- FIGS. 7A and 7B are main part perspective views showing modified examples of the profile of the tooth of the one gear in the second embodiment
- FIGS. 7A and 7B are main part perspective views showing modified examples of the shape of the tooth 1 of the gear G 1 in the second embodiment.
- a position ( 16 ) of the one place in the tooth width direction in the embodiment shown in FIG. 6 for when the chamfering is performed so as to form, on the crossing 8 of the one tooth flank 7 and the tooth tip surface 3 , the inclined planes which extend from the one place in the tooth width direction toward both of the end faces of the tooth 1 is not limited to the center portion in the tooth width direction, and is set at an arbitrary position in the tooth width direction within the tooth width for each tooth 1 .
- FIG. 7A shows a state where the position ( 16 ) of the one place is set so as to be shifted irregularly within the tooth width.
- FIG. 7B shows a state where the position ( 16 ) of the one place is set to be shifted sequentially from the one side end portion to the other end portion within the tooth width.
- FIGS. 10A and 10B are main part perspective views showing modified examples of the shape of the tooth 1 of the gear G 1 in the third embodiment.
- a lightening portion 30 of triangle, trapezoid or the like of certain fixed depth is formed on the one tooth flank 7 toward the crossing 8 of the tooth flank 7 and the tooth tip surface 3 .
- the chipped portions 17 a and 17 b are formed in plural places by chipping off from the one tooth flank 7 triangular incline planes which extend from three sites 18 a , 18 b and 18 c on the one tooth flank 7 toward the crossing 8 of the tooth flank 7 and the tooth tip 3 to both of the end face sides.
- the chipped portions 17 a and 17 b are formed in plural places by chipping off from the one tooth flank 7 triangular inclined planes which extend from four sites 18 a , 18 b , 18 c and 18 d in FIG. 11C , and five sites 18 a , 18 b , 18 c , 18 d and 18 e in FIG. 11D , on the one tooth flank 7 toward the crossing 8 of the tooth flank 7 and the tooth tip surface 3 to both of the end face sides.
- the involute curve 20 on the one end portion 5 side and the curve 21 on the other end portion 6 side, in the tooth width direction of the one tooth flank 7 shown in FIG. 13 are smoothly connected to each other with parallel lines 22 each of which curvature direction is reversed halfway, to thereby form the curved surface shape.
- the point contact gradually shifts to the line contact shorter than the total tooth width, and thereafter, further gradually shifts to the larger line contact within the range of the total tooth width. Further, the line contact shorter than the total tooth width then gradually shifts to the larger line contact within the range of the total tooth width.
- the contact to the teeth ( 2 ) of the mating gear (G 2 ) is softened and therefore, the shock can be absorbed.
- the curved surfaces 19 a and 19 b viewed from above the tooth tip surface 3 of the tooth 1 are planar, and an angle ⁇ at which the curved surfaces 19 a and 19 b intersect with each other, is sequentially increased from the side of the tooth tip through the tooth root 4 . In this case, it becomes easy to perform the processing and finishing of the tooth flank 7 of the tooth 1 .
- the triangular notched concave portion 23 is formed in plural places, by chipping off from the one tooth flank 7 triangular shapes which extend from the two sites 18 a and 18 b on the one tooth flank 7 to both of the end portion 5 and 6 sides of the tooth tip surface 3 and also run through to the other tooth flank. Furthermore, in FIG. 19C , the triangular notched concave portion 23 is formed in plural places, by chipping off from the one tooth flank 7 triangular shapes from the three sites 18 a , 18 b and 18 c on the one tooth flank 7 to both sides of the end portion 5 and 6 of the tooth tip surface 3 and also run through to the other tooth flank.
- FIGS. 20A through 20D are perspective views showing a main part of a seventh embodiment of the shape of the tooth 1 of the gear G 1 .
- a predetermined region A′ in at least the one tooth flank 7 of each tooth 1 is formed in a configuration such that the mating with the teeth ( 2 ) of the mating gear (G 2 ) starts from at least one place in the tooth width direction on a crossing 24 of the tooth flank 7 and a tooth root surface with the point contact or the line contact shorter than the total tooth width, and thereafter, gradually shifts to the line contact so that the length of contact line thereof is sequentially increased as the line contact moves from a tooth root side ( 24 ) toward the tooth tip side ( 3 ).
- the contact at the mating time of the opposite teeth 1 and 2 does not start firstly with the line contact of the total tooth width at a tooth root portion, but starts with the point contact or the line contact shorter than the total tooth width. Then, the point contact gradually shifts to the line contact shorter than the total tooth width, and thereafter, further gradually shifts to the larger line contact within the range of the total tooth width. Further, the line contact shorter than the total tooth width then gradually shifts to the larger line contact within the range of the total tooth width. As a result, the contact to the teeth ( 2 ) of the mating gear (G 2 ) is softened and therefore, the shock can be absorbed.
- FIGS. 20B through 20D are partial perspective views showing a main part of the respective modified examples of the shape of the tooth 1 of the gear G 1 in the seventh embodiment.
- chipped portions 17 c and 17 d are formed, by chipping off from the tooth flank 7 the triangular inclined planes which extend from a site 26 of the one place on the one tooth flank 7 to both of the end face sides toward the crossing 24 of the tooth flank 7 and the tooth root surface. Further, in FIG.
- the chipped portions 17 c and 17 d are formed on plural places by chipping off from the tooth flank 7 the triangular inclined planes which extend from two sites 26 a and 26 b on the one tooth flank 7 to both of the end face sides toward the crossing 24 of the tooth flank 7 and the tooth root surface. Furthermore, in FIG. 20D , the chipped portions 17 c and 17 d are formed on plural places by chipping off from the tooth flank 7 the triangular inclined planes which extend from three sites 26 a , 26 b and 26 c on the one tooth flank 7 to both of the end face sides toward the crossing 24 of the tooth flank 7 and the tooth root surface.
- FIGS. 21A through 21D are partial perspective views showing a main part of an eighth embodiment of the shape of the tooth 1 of the gear G 1 .
- the modification of the tooth profile on the tooth tip side shown in FIG. 6 is basically combined with the modification of the tooth profile on the tooth root side shown in FIG. 20A .
- FIG. 21A shows the combination of the embodiment shown in FIG. 6 and the embodiment shown in FIG. 20A
- FIG. 21B shows the combination of the embodiment shown in FIG. 9 and the embodiment shown in FIG. 20B
- FIG. 21C shows the combination of the embodiment shown in FIG. 11A and the embodiment shown in FIG. 20C
- FIG. 21D shows the combination of the embodiment shown in FIG. 11B and the embodiment shown in FIG. 20D .
- rectangular chipped portions 27 a and 27 b are formed, by chipping off from the one tooth flank 7 predetermined places in the tooth width direction on the crossing 8 of the one tooth flank 7 and the tooth tip surface 3 , in rectangular concave stepped portions, in this case, from the center portion toward the involute curve portions on the end face sides on both sides.
- the contact at the mating time of the Opposite teeth 1 and 2 does not start firstly with the line contact on the tooth flank 7 , but starts with the point contact or the line contact shorter than the total tooth width. Then, the point contact rapidly or in stepwise shifts to the line contact shorter than the total tooth width, and thereafter, further rapidly or in stepwise shifts to the larger line contact within the range of the total tooth width. Further, the line contact shorter than the total tooth width then rapidly or in stepwise shifts to the larger line contact within the range of the total tooth width. As a result, the contact to the teeth ( 2 ) of the mating gear (G 2 ) is softened and therefore, the shock can be absorbed.
- FIGS. 22B through 22D are partial perspective views showing a main part of the respective modified examples of the shape of the tooth 1 of the gear G 1 in the ninth embodiment.
- a rectangular chipped portion 27 is formed, by chipping off from the tooth flank 7 the center portion in the tooth width direction on the crossing 8 of the one tooth flank 7 and the tooth tip surface 3 in a rectangular concave stepped portion.
- FIG. 22B a rectangular chipped portion 27 is formed, by chipping off from the tooth flank 7 the center portion in the tooth width direction on the crossing 8 of the one tooth flank 7 and the tooth tip surface 3 in a rectangular concave stepped portion.
- stepped chipped portions 28 a and 28 b are formed, by chipping off from the tooth flank 7 predetermined places in the tooth width direction on the crossing 8 of the one tooth flank 7 and the tooth tip surface 3 in stair concave stepped portions, in this case, from the center portion toward the involute curve portions on the end face sides on both sides.
- the mating with the teeth of the mating gear starts from at least one place in the tooth width direction on the crossing 8 of the tooth flank 7 and the tooth tip surface 3 with the point contact or the line contact shorter than the total tooth width, and thereafter, in stepwise shifts to the line contact of the total tooth width from the tooth tip side toward the tooth root side so that the length of contact line 10 thereof is increased. Furthermore, in FIG.
- a plurality of recesses 29 of small diameter (for example, rectangular recesses) is intermittently formed in parallel to the crossing 8 of the tooth flank 7 and the tooth tip surface 3 , toward the involute curve portions on the end face sides on both sides, and also, a plurality of rows of this plurality of recesses 29 is formed at a small interval.
- the mating with the teeth of the mating gear starts with the line contact shorter than the total tooth width, and thereafter, rapidly shifts to the line contact of the total tooth width so that the length of contact line thereof is increased.
- FIGS. 23A and 23B are partial perspective views showing a main part of the tenth embodiment of the shape of the tooth 1 of the gear G 1 .
- the configuration of the predetermined region A′ in at least the one tooth flank 7 of each tooth 1 is formed such that the mating with the teeth ( 2 ) of the mating gear (G 2 ) starts from at least one place in the tooth width direction on the crossing 24 of the tooth flank 7 and the tooth root surface with the point contact or the line contact shorter than the total tooth width, and thereafter, rapidly or in stepwise shifts to the line contact of the total tooth width from the tooth root side ( 24 ) toward the tooth tip side ( 3 ) so that the length of contact line thereof is increased.
- the contact at the mating time of the opposite teeth 1 and 2 does not start firstly with the line contact of the total tooth width at the tooth root portion, but starts with the point contact or the line contact shorter than the total tooth width. Then, the point contact rapidly or in stepwise shifts to the line contact shorter than the total tooth width, and thereafter, further rapidly or in stepwise shifts to the larger line contact within the range of the total tooth width. Further, the line contact shorter than the total tooth width then rapidly or in stepwise shifts to the larger line contact within the range of the total tooth width. As a result, the contact to the teeth ( 2 ) of the mating gear (G 2 ) is softened and therefore, the shock can be absorbed.
- the present invention is not limited to the above, and the chamfered portion 9 , the chipped portions 17 a and 17 b , the curved surface 19 , the rectangular chipped portions 27 a and 27 b , and the stepped chipped portions 28 a and 28 b may be formed on both of the tooth flanks of each tooth 1 .
- the above described chamfered portion is not limited to the inclined plane, and may be formed in a convex curved surface or a concave curved surface.
- This gear G 2 is provided with the plurality of teeth 2 , 2 , . . . , and these teeth 2 are mated with the teeth 1 of the mating gear G 1 , to thereby transmit the rotational motion.
- the tooth 2 is formed in a shape exactly same as the shape of the tooth 1 of the one gear G 1 shown in FIGS. 3 through 23 A and 23 B.
- a predetermined region in a tooth flank of each tooth 2 is a region on a tooth tip side or a tooth root side from the vicinity of a branching point between the (n+1) teeth mating and the n teeth mating (n is integer of one or more) at the mating time with the teeth 1 of the mating gear G 1 .
- the chamfered portion 9 , the chipped portions 17 a and 17 b , the curved surface 19 , the rectangular chipped portions 27 a and 27 b , and the stepped chipped portions 28 a and 28 b may be formed on both tooth flanks of each tooth 2 .
- FIGS. 24A through 24C are cross section explanatory diagrams showing combination states of the one gear G 1 and the other gear G 2 in the gearing apparatus configured as described above.
- the chamfered portion 9 is formed, by cutting away from the one tooth flank 7 the triangular inclined plane from the corner portion on the one end portion 5 side in the tooth width direction of the tooth tip surface 3 toward the involute curve portion on the other end portion 6 side.
- the other gear G 2 is formed to have the tooth profile of the standard gear.
- each of the chamfered portions 9 , 9 is formed, by cutting away from the one tooth flank 7 shown in FIG. 3 the triangular inclined plane from the corner portion on the one end portion 5 side in the tooth width direction of the tooth tip surface 3 , toward the involute curve portion on the other end portion 6 side.
- the opposed state of the inclined planes of the chamfered portions 9 , 9 of the one gear G 1 and the other gear G 2 is made to be point symmetrical to the boundary line.
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Abstract
In a gear G1 according to the present invention, which is provided with a plurality of teeth 1 to be mated with teeth of a mating gear to thereby transmit a rotational motion, a predetermined region A in at least one tooth flank 7 of each tooth 1 is formed in a configuration such that, from at least one place in a tooth width direction on a crossing 8 of the tooth flank 7 and a tooth tip surface 3, the mating with the teeth of the mating gear is started with the point contact or the line contact shorter than the total tooth width, and thereafter, is gradually shifted to the line contact so that the length of contact line 10 thereof is sequentially increased as the line contact moves from a tooth tip surface 3 side toward a tooth root side.
Description
- 1. Field of the Invention
- The present invention relates to gears and a gearing apparatus for transmitting a rotational motion between two associated shafts, i.e., from one to the other of two associated shafts, through a pair of gears which are engaged with each other so that teeth of the engaged gears are operatively mated with each other. More particularly, the present invention relates to gears and a gearing apparatus capable of reducing generation of noise during the rotational motion transmitting operation of a pair of gears engaged with each other, and also reducing an error in transmission of the rotational motion.
- 2. Description of the Related Art
- As gears in a conventional gearing apparatus, typically, gears called standard gears having symmetrical tooth profiles are used. In a combination of such standard gears, the tooth tip and the tooth root of each of teeth have identical tooth widths when measured in a direction along the axes of the respective gears and the total tooth depth of each tooth is unchanged and constant in a tooth width direction. Therefore, in the case where opposite teeth are mated with each other, since an amount of change in a spring constant of a tooth which functions as a type of spring between the double-teeth-mating arrangement and the single-tooth-mating arrangement, is large, sometimes, noise due to the mating of the gear teeth becomes large and also the vibration is increased. Further, the increase in the vibration of the mated gear teeth could often cause an increase in an error in the rotation transmission of the engaged gears.
- In order to cope with the above problems, there has been conventionally proposed a gearing apparatus in which a pair of gears is configured by involute spur gears and at least one gear of the pair of gears is provided with rigidity reducing means incorporated therein for reducing the rigidity in the double-teeth-mating region of the said one gear, in comparison with the rigidity to be provided by the standard involute spur gear As this rigidity reducing means in the gear, for example, there is a through-hole formed in a gear, which runs through from one of end face of a tooth tip portion toward the other end face thereof. In this case, when opposite teeth are mated with each other, a deflection amount of the tooth is relatively increased, in comparison with a deflection amount of a tooth of the standard involute spur gear, and therefore, the fluctuation in the deflection amount in the duration of mating of the opposite teeth is suppressed and accordingly, the silence during the rotation transmission time is improved, and also, the vibration is reduced (refer to Japanese Unexamined Patent Publication No. 8-312755 (
FIG. 4 )). - However, in the gears of the conventional gearing apparatus, as shown in
FIG. 4 of Japanese Unexamined Patent Publication No. 8-312755, although the through-hole as the rigidity reducing means runs through from the one end face of the tooth tip portion to the other end face thereof, a tooth profile of each tooth is still kept as an involute spur tooth profile, and the tooth contact at the time of mating of each tooth with each tooth of the mating gear is in a line contact state. In this case, in the mating of the opposite teeth, the line contact state is maintained from the beginning to the end in the mating, and therefore, it is impossible to appreciably reduce noise generated when the pair of gears is mated with each other. Also, it is impossible to sufficiently improve the vibration suppression at the mating time, and also, to sufficiently reduce the error in the rotation transmission of the gearing apparatus. - In view of the above problems, an object of the present invention is to provide firstly gears comprised of one and the other mutually engaged gears, and secondly a gearing apparatus capable of reducing noise generated when a pair of gears is engaged with each other and also, reducing an error in rotation transmission of the gears.
- To achieve the above object, in accordance with a first aspect of the present invention, gears comprised of one and the other mutually engaged gears, each being provided with a plurality of teeth to be mated with the teeth of the other engaged gear to thereby transmit a rotational motion, wherein a predetermined region in at least one of tooth flanks of each tooth of the one gear is formed in a configuration such that mating of each tooth of the one gear with the teeth of the other engaged gear starts with either point contact or line contact shorter than a total length of a tooth width of the one gear from at least one place in a direction of a tooth width on a crossing of the tooth flank and a surface of tooth tip of the one gear and thereafter, gradually shifts to the line contact so that a length of contact line thereof is continuously increased as the line contact moves from a tooth tip side toward a tooth root side. It should be understood that the term “surface” generally includes not only a flat surface but also a surface with a curvature of unevenness throughout the description of this specification.
- According to the above configuration, the predetermined region in at least one tooth flank of each tooth of the one gear is formed in the configuration such that, from at least one place in the tooth width direction on the crossing of the tooth flank and the tooth tip surface, the mating of each tooth of the one gear with the teeth of the other engaged gear starts with point contact or the line contact shorter than the total tooth width and thereafter, gradually shifts to line contact so that the length of contact line thereof is continuously increased as the line contact moves from the tooth tip side toward the tooth root side. In this case, mainly in the gear on a driven side, the contact at the mating time of the opposite teeth does not start firstly with the line contact on the tooth flank, but starts with the point contact or the line contact shorter than the total tooth width. Then, the point contact gradually moves to the line contact shorter than the total tooth width, and thereafter, further gradually moves to a longer line contact within a range of the total tooth width. Further, the line contact shorter than the total tooth width then gradually moves to the longer line contact within the range of the total tooth width. As a result, the contact to the teeth of the mating gear can be soft and therefore, the contacting shock can be absorbed. Accordingly, it is possible to reduce the generation of vibration at the mating time of the pair of gears, to thereby reduce generation of noise due to the mating. Further, by reducing the vibration, it is possible to reduce an error in transmission of rotational motion.
- Further, the predetermined region in the tooth flank is chamfered. Hence, the configuration thereof is made to be an inclined plane which extends from at least one place in the tooth width direction on the crossing of the tooth flank and the tooth tip surface toward one of end faces of the tooth or both of the end faces thereof. As a result, by the shape in which the predetermined region in the tooth flank is chamfered, a portion which is not mated with the mating gear appears in the tooth flank, so that a contact area is decreased. In this case, the mating of the tooth of the one gear with the teeth of the mating gear always starts with the point contact or the line contact shorter than the total tooth width. Then, the point contact gradually moves to the line contact shorter than the total tooth width, and thereafter, further gradually moves to the larger line contact within the range of the total tooth width. Further, the line contact shorter than the total tooth width then gradually moves to the larger line contact within the range of the total tooth width. As a result, the contact to the teeth of the mating gear can be soft and therefore, the shock can be absorbed.
- Furthermore, a reduced portion is formed by chipping, cutting off or the like (it will be hereinbelow referred to as a chipped portion), so that the configuration in the predetermined region in the tooth flank is made to be an inclined plane which extends from one place or a plurality of places of the tooth flank to both of the end faces of the tooth toward the crossing of the tooth flank and the tooth tip surface. As a result, by forming the chipped portion in the predetermined region in the tooth flank, the portion which is not mated with the mating gear appears in the tooth flank, so that the contact area is decreased. In this case, the mating of the tooth of the one gear with the teeth of the engaged gear starts with the point contact or the line contact shorter than the total tooth width. Then, the point contact gradually moves to the line contact shorter than the total tooth width, and thereafter, further gradually moves to the larger line contact within the range of the total tooth width. Further, the line contact shorter than the total tooth width then gradually moves to the larger line contact within the range of the total tooth width. As a result, the contact to the teeth of the mating gear is softened and therefore, the shock can be absorbed.
- Still further, in the configuration of the predetermined region in the tooth flank, a curved surface which gradually decreases the tooth thickness, is formed toward the one end face of the tooth or both end faces thereof in the tooth width direction of the tooth flank. As a result, by forming the curved surface which gradually decreases the tooth thickness, in the predetermined region in the tooth flank, the portion which is not mated with the mating gear appears in the tooth flank, so that the contact area is decreased. In this case, the mating with the teeth of the mating gear starts with the point contact or the line contact shorter than the total tooth width. Then, the point contact gradually moves to the line contact shorter than the total tooth width, and thereafter, further gradually moves to the larger line contact within the range of the total tooth width. Further, the line contact shorter than the total tooth width then gradually moves to the larger line contact within the range of the total tooth width. As a result, the contact to the teeth of the mating gear can be soft and therefore, the shock can be absorbed.
- Moreover, the predetermined region in the tooth flank is a region on the tooth tip side from the vicinity of a branching point between the (n+1) teeth mating and the n teeth mating (n is integer of one or more) at the mating time with the teeth of the mating gear. As a result, the mating with the teeth of the mating gear starts with the point contact or the line contact shorter than the total tooth width. Then, the point contact gradually moves to the line contact shorter than the total tooth width, and thereafter, further gradually moves to the larger line contact within the range of the total tooth width. Further, the line contact shorter than the total tooth width then gradually moves to the larger line contact within the range of the total tooth width. A shifting region of the point contact or the line contact shorter than the total tooth width is on the tooth tip side from the vicinity of the branching point between the (n+1) teeth mating and the n teeth mating at the mating time with the teeth of the mating gear. Accordingly, in the mating with the opposite teeth of the mating gear, the rotational motion can be surely transmitted by a portion serving as a main power transmission plane, in a state where the tooth flank is formed from the one end portion to the other end portion in the tooth width direction.
- In accordance with a second aspect of the present invention, a gearing apparatus is provided for transmitting a rotational motion from one to the other of associated two shafts by engaging a pair of engaged gears to allow opposite teeth of the engaged gears to be mated with each other, wherein for at least one gear of the pair of gears, a predetermined region in at least one of tooth flanks of each tooth is formed in a configuration such that mating of each tooth of the one gear with the teeth of the other engaged gear starts with a point contact or a line contact shorter than a total length of a tooth width from at least one place in a tooth width direction on a crossing of the tooth flank and a tooth tip surface and thereafter, gradually shifts to the line contact so that a length of contact line thereof is continuously increased as the line contact moves from a tooth tip side toward a tooth root side.
- According to the above configuration, for at least one gear in the pair of gears, the predetermined region in at least one tooth flank of each tooth is formed in the shape such that, from at least one place in the tooth width direction on the crossing of the tooth flank and the tooth tip surface, the mating with the teeth of the mating gear starts with the point contact or the line contact shorter than the total tooth width, and thereafter, gradually shifts to the line contact so that the length of contact line thereof is continuously increased as the line contact moves from the tooth tip side toward the tooth root side. In this case, mainly in the gear on a driven side, the contact at the mating time of the opposite teeth does not start firstly with the line contact of the total tooth width, but starts with the point contact or the line contact shorter than the total tooth width. Then, the point contact gradually moves to the line contact shorter than the total tooth width, and thereafter, further gradually moves to the larger line contact within a range of the total tooth width. Further, the line contact shorter than the total tooth width then gradually moves to the larger line contact within the range of the total tooth width. As a result, the contact to the teeth of the mating gear is softened and therefore, the shock can be absorbed. Accordingly, it is possible to reduce the generation of vibration during engagement of the pair of gears due to mating of the teeth with each other, to thereby reduce the noise due to the mating. Further, by reducing the vibration, it is possible to reduce the error in gear rotation transmission.
- In accordance with a third aspect of the present invention, there are provided gears comprised of one and the other mutually engaged gears, each having a plurality of teeth to be mated with teeth of the other engaged gear to thereby transmit a rotational motion, wherein a predetermined region in at least one of tooth flanks of each tooth is formed in a configuration such that mating of each tooth of the one gear with the teeth of the other engaged gear starts with a point contact or a line contact shorter than the total tooth width from at least one place in a tooth width direction on a crossing of the tooth flank and a surface of tooth root and thereafter, gradually shifts to the line contact so that the length of contact line thereof is continuously increased as the line contact moves from a tooth root side toward a tooth tip side. It should be understood that the term “surface” generally includes not only a flat surface but also a surface with a curvature of unevenness throughout the description of this specification.
- According to the above configuration, the predetermined region in at least one tooth flank of each tooth is formed in the shape such that, from at least one place in the tooth width direction on the crossing of the tooth flank and the tooth tip surface, mating of each tooth of the one gear with the teeth of the other engaged gear starts with the point contact or the line contact shorter than the total tooth width and thereafter, gradually shifts to the line contact so that the length of contact line thereof is continuously increased as the line contact moves from the tooth root side toward the tooth tip side. In this case, mainly in the gear on a driving side, the contact by mating with the opposite teeth does not start firstly with the line contact on the tooth flank, but starts with the point contact or the line contact shorter than the total tooth width. Then, the point contact gradually moves to the line contact shorter than the total tooth width, and thereafter, further gradually moves to the larger line contact within a range of the total tooth width. Further, the line contact shorter than the total tooth width then gradually moves to the larger line contact within the range of the total tooth width. As a result, the contact to the teeth of the mating gear is softened and therefore, the shock can be absorbed.
- In accordance with a fourth aspect of the present invention, a gearing apparatus is provided for transmitting a rotational motion from one to the other of associated two shafts by engaging a pair of gears to allow opposite teeth of the engaged gears to be mated with each other, wherein for at least one gear of the pair of gears, a predetermined region in at least one of tooth flanks of each tooth is formed in a configuration such that mating of each tooth of one of the engaged pair of gears with the teeth of the other engaged gear starts with a point contact or a line contact shorter than the total tooth width from at least one place in a tooth width direction on a crossing of the tooth flank and a surface of tooth root and thereafter, gradually moves to the line contact so that a length of contact line thereof is continuously increased as the line contact moves from a tooth root side toward a tooth tip side.
- According to the above configuration, for at least one gear in the pair of gears, the predetermined region in at least one tooth flank of each tooth is formed in the shape such that, from at least one place in the tooth width direction on the crossing of the tooth flank and the tooth root surface, the mating with the teeth of the mating gear starts with the point contact or the line contact shorter than the total tooth width, and thereafter, gradually moves to the line contact so that the length of contact line thereof is sequentially increased as the line contact moves from the tooth root side toward the tooth tip side. In this case, mainly in the gear on a driving side, the contact at the mating time of the opposite teeth does not start firstly with the line contact of the total tooth width on the tooth flank, but starts with the point contact or the line contact shorter than the total tooth width. Then, the point contact gradually moves to the line contact shorter than the total tooth width, and thereafter, further gradually moves to the larger line contact within a range of the total tooth width. Further, the line contact shorter than the total tooth width then gradually moves to the larger line contact within the range of the total tooth width. As a result, the contact to the teeth of the mating gear is softened and therefore, the shock can be absorbed.
- In accordance with a fifth aspect of the present invention, there are provided gears comprised of one and the other mutually engaged gears, each provided with a plurality of teeth to be mated with the teeth of the other engaged gear to thereby transmit a rotational motion, wherein a predetermined region in at least one of tooth flanks of each tooth of the one gear is formed in a configuration such that mating of each tooth of the one gear with the teeth of the other engaged gear starts with a point contact or a line contact shorter than the total tooth width from at least one place in a tooth width direction on a crossing of the tooth flank and a surface of tooth tip and thereafter, rapidly or in stepwise shifts to the line contact of a total length of the tooth width from a tooth tip side toward a tooth root side so that the length of contact line thereof is increased.
- According to the above configuration, the predetermined region in at least one tooth flank of each tooth is formed in the shape such that, from at least one place in the tooth width direction on the crossing of the tooth flank and the tooth tip surface, the mating with the teeth of the mating gear starts with the point contact or the line contact shorter than the total tooth width, and thereafter, rapidly or in stepwise shifts to the line contact of the total tooth width from the tooth tip side toward the tooth root side so that the length of contact line thereof is increased. In this case, mainly in the gear on a driven side, the contact at the mating time of the opposite teeth does not start firstly with the line contact on the tooth flank, but starts with the point contact or the line contact shorter than the total tooth width. Then, the point contact rapidly or in stepwise moves to the line contact shorter than the total tooth width, and thereafter, further rapidly or in stepwise moves to the larger line contact within a range of the total tooth width. Further, the line contact shorter than the total tooth width then rapidly or in stepwise moves to the larger line contact within the range of the total tooth width. As a result, the contact to the teeth of the mating gear is softened and therefore, the shock can be absorbed.
- In accordance with a sixth aspect of the present invention, a gearing apparatus is provided for transmitting a rotational motion from one to the other of associated two shafts by engaging a pair of gears to allow opposite teeth of the mating gears to be mated with each other, wherein for at least one gear of the pair of gears, a predetermined region in at least one of tooth flanks of each tooth is formed in a configuration such that mating of each tooth of the one gear with the teeth of the other engaged gear starts with a point contact or a line contact shorter than the total tooth width from at least one place in a tooth width direction on a crossing of the tooth flank and a tooth tip surface and thereafter, rapidly or in stepwise shifts to the line contact of the total tooth width from a tooth tip side toward a tooth root side so that the length of contact line thereof is increased.
- According to the above configuration, for at least one gear of the pair of gears, the predetermined region in at least one tooth flank of each tooth is formed in the shape such that, from at least one place in the tooth width direction on the crossing of the tooth flank and the tooth tip surface, the mating of each tooth of one gear with the teeth of the other engaged gear starts with the point contact or the line contact shorter than the total tooth width and thereafter, rapidly or in stepwise shifts to the line contact of the total length of a tooth width from the tooth tip side toward the tooth root side so that the length of contact line thereof is increased. In this case, mainly in the gear on a driven side, the contact at the mating time of the opposite teeth does not start firstly with the line contact of the total tooth width on the tooth flank, but starts with the point contact or the line contact shorter than the total tooth width. Then, the point contact rapidly or in stepwise moves to the line contact shorter than the total tooth width, and thereafter, further rapidly or in stepwise moves to the larger line contact within a range of the total tooth width. Further, the line contact shorter than the total tooth width then rapidly or in stepwise moves to the larger line contact within the range of the total tooth width. As a result, the contact to the teeth of the mating gear is softened and therefore, the shock can be absorbed.
- In accordance with a seventh aspect of the present invention, there are provided gears comprised of one and the other mutually engaged gears, each provided with a plurality of teeth to be mated with the teeth of the engaged gear to thereby transmit a rotational motion, wherein a predetermined region in at least one of tooth flanks of each tooth is formed in a configuration such that mating of each tooth of the one gear with the teeth of the other engaged gear starts with a point contact or a line contact shorter than the total tooth width from at least one place in a tooth width direction on a crossing of the tooth flank and a surface of tooth root, and thereafter, rapidly or in stepwise moves to the line contact of the total tooth width from a tooth root side toward a tooth tip side so that the length of contact line thereof is increased.
- According to the above configuration, the predetermined region in at least one tooth flank of each tooth is formed in the shape such that, from at least one place in the tooth width direction on the crossing of the tooth flank and the tooth root surface, the mating with the teeth of the mating gear starts with the point contact or the line contact shorter than the total tooth width, and thereafter, rapidly or in stepwise moves to the line contact of the total tooth width from the tooth root side toward the tooth tip side so that the length of contact line thereof is increased. In this case, mainly in the gear on a driving side, the contact at the mating time of the opposite teeth does not start firstly with the line contact on the tooth flank, but starts with the point contact or the line contact shorter than the total tooth width. Then, the point contact rapidly or in stepwise moves to the line contact shorter than the total tooth width, and thereafter, further rapidly or in stepwise moves to the larger line contact within a range of the total tooth width. Further, the line contact shorter than the total tooth width then rapidly or in stepwise moves to the larger line contact within the range of the total tooth width. As a result, the contact to the teeth of the mating gear is softened and therefore, the shock can be absorbed.
- In accordance with an eighth aspect of the present invention, a gearing apparatus is provided for transmitting a rotational motion from one to the other of two associated shafts by engagement of a pair of gears to allow opposite teeth of the mating gears to be mated with each other, wherein for at least one gear of the pair of gears, a predetermined region in at least one of tooth flanks of each tooth is formed in a configuration such that mating of each tooth of the one gear with the teeth of the other engaged gear starts with a point contact or a line contact shorter than the total tooth width from at least one place in a tooth width direction on a crossing of the tooth flank and a tooth root surface and thereafter, rapidly or in stepwise shifts to the line contact of the total tooth width from a tooth root side toward a tooth tip side so that the length of contact line thereof is increased.
- According to the above configuration, for at least one gear of the pair of gears, the predetermined region in at least one tooth flank of each tooth is formed in the shape such that, from at least one place in the tooth width direction on the crossing of the tooth flank and the tooth root surface, the mating with the teeth of the mating gear starts with the point contact or the line contact shorter than the total tooth width, and thereafter, rapidly or in stepwise moves to the line contact of the total tooth width from the tooth root side toward the tooth tip side so that the length of contact line thereof is increased. In this case, mainly in the gear on a driving side, the contact at the mating time of the opposite teeth does not start firstly with the line contact of the total tooth width on the tooth flank, but starts with the point contact or the line contact shorter than the total tooth width. Then, the point contact rapidly or in stepwise moves to the line contact shorter than the total tooth width, and thereafter, further rapidly or in stepwise moves to the larger line contact within a range of the total tooth width. Further, the line contact shorter than the total tooth width then rapidly or in stepwise moves to the larger line contact within the range of the total tooth width. As a result, the contact to the teeth of the mating gear is softened and therefore, the shock can be absorbed.
- The other objects and features of the invention will become understood from the following description with reference to the accompanying drawings.
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FIG. 1 is a diagram showing an embodiment of a gearing apparatus according to the present invention, for explaining a main part of the apparatus in a state where a pair of gears is engaged with each other; -
FIG. 2 is a perspective view showing a tooth profile of a standard gear; -
FIG. 3 is a perspective view showing a profile of a tooth of one of the pair of gears; -
FIG. 4 is a side view explaining the detail of the tooth profile formed as shown inFIG. 3 ; -
FIG. 5 is a front elevation view showing an entire shape of the one gear; -
FIG. 6 is a main part perspective view showing a second embodiment of the profile of the tooth of the one gear; -
FIGS. 7A and 7B are main part perspective views showing modified examples of the profile of the tooth of the one gear in the second embodiment; -
FIGS. 8A through 8D are main part perspective views showing further modified examples of the profile of the tooth of the one gear in the second embodiment; -
FIG. 9 is a main part perspective view showing a third embodiment of the profile of the tooth of the one gear; -
FIGS. 10A and 10B are main part perspective views showing modified examples of the profile of the tooth of the one gear in the third embodiment; -
FIGS. 11A through 11D are main part perspective views showing further modified examples of the profile of the tooth of the one gear in the third embodiment; -
FIGS. 12A through 12C are main part perspective views showing still further modified examples of the profile of the tooth of the one gear in the third embodiment; -
FIG. 13 is a main part perspective view showing a fourth embodiment of the profile of the tooth of the one gear; -
FIG. 14 is an explanatory diagram showing a planar vision shape of a curved surface in one of tooth flanks of the tooth shown inFIG. 13 viewed from above a tooth tip surface thereof; -
FIGS. 15A and 15B are explanatory diagrams showing modified examples of the profile of the tooth in the fourth embodiment shown in FIG. 13; -
FIG. 16 is a main part perspective view showing a fifth embodiment of the profile of the tooth of the one gear; -
FIG. 17 is an explanatory diagram showing a planar vision shape of a curved surface in one of tooth flanks of the tooth shown inFIG. 16 viewed from above a tooth tip surface thereof; -
FIGS. 18A and 18B are explanatory diagrams showing modified examples of the profile of the tooth in the fifth embodiment shown inFIG. 16 ; -
FIGS. 19A through 19C are main part perspective views showing a sixth embodiment of the profile of the tooth of the one gear; -
FIGS. 20A through 20D are main part perspective views showing a seventh embodiment of the profile of the tooth of the one gear; -
FIGS. 21A through 21D are main part perspective views showing an eighth embodiment of the profile of the tooth of the one gear; -
FIGS. 22A through 22D are main part perspective views showing a ninth embodiment of the profile of the tooth of the one gear; -
FIGS. 23A and 23B are main part perspective views showing a tenth embodiment of the profile of the tooth of the one gear; and -
FIGS. 24A through 24C are cross section explanatory diagrams showing combination states of the one gear and the other gear in the gearing apparatus configured as above. - There will be described hereunder embodiments of the present invention based on the accompanying drawings.
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FIG. 1 is a diagram showing an embodiment of a gearing apparatus according to the present invention, for explaining a main part of the apparatus in a state where a pair of gears is mated with each other. This gearing apparatus is for transmitting a rotational motion from one shaft to the other of two associated shafts by engagement of the pair of gears so as to mate opposite teeth of the engaged gears with each other, and is configured by combining one gear G1 and the other gear G2. The one gear G1 is, for example a gear having a small number of teeth, and is called a pinion. The other gear G2 is, for example a gear having a large number of teeth, and is called a main wheel. - In
FIG. 1 , symbol P1 indicates a pitch circle of the one gear G1, and symbol P2 indicates a pitch circle of the other gear G2. Further, symbol B indicates a backlash which is a clearance between a tooth flank of atooth 1 and a tooth flank of atooth 2 for when the pair of gears G1 and G2 are mated with each other. - Firstly, there will be described a shape of the one gear G1. This gear G1 is provided with a plurality of
teeth teeth 1 are mated withteeth 2 of the mating gear (G2), to thereby transmit the rotational motion. Typically, as shown inFIG. 2 , each of theteeth 1 is formed in a standard gear tooth profile which is made symmetric by an involute curve. Namely, in each of theteeth 1, the tooth width W3 of atooth tip surface 3 has the same size as the tooth width W4 of atooth root 4, and the total tooth height H is fixed in a tooth width direction. - Here, in the present invention, as shown in
FIG. 3 , in each of theteeth 1, a predetermined region A in at least onetooth flank 7 of eachtooth 1 is formed in a configuration such that, from at least one place in the tooth width direction on acrossing 8 of thetooth flank 7 and thetooth tip surface 3, the mating with the teeth of the mating gear starts with the point contact or the line contact shorter than the total tooth width, and thereafter, gradually shifts or moves to the line contact so that the length of contact line thereof is sequentially increased as the line contact moves from a tooth tip side (3) toward a tooth root side (4). In the example ofFIG. 3 , the predetermined region A in the tooth flank is chamfered, so that the configuration thereof is made to be an inclined plane which extends from the one place in the tooth width direction on thecrossing 8 of thetooth flank 7 and thetooth tip surface 3 toward one of end faces of thetooth 1. Namely, a chamferedportion 9 is formed, by cutting away from the one tooth flank 7 a triangular inclined plane which extends from a corner portion on a side of oneend portion 5 in the tooth width direction of thetooth tip surface 3 toward an involute curve portion on a side of theother end portion 6. -
FIG. 4 is a side view explaining the details of the shape of thetooth 1 formed as shown inFIG. 3 . Here, the predetermined region A in the tooth flank is a region on the tooth tip side from the vicinity of a branching point between the (n+1) teeth mating and the n teeth mating (n is integer of one or more) at the mating time with the teeth (2) of the mating gear (G2). The example ofFIG. 4 shows the case where a mating rate to the teeth (2) of the mating gear (G2) is equal to or larger than 1, but equal to or smaller than 2, and the predetermined region A in the tooth flank is the region on the tooth tip side from the vicinity of the branching point between the 2 teeth mating and the 1 tooth mating. Namely, inFIG. 4 , provided that a 1 tooth mating region is E1 in an intermediate portion and 2 teeth mating regions are E2 on the tooth tip side and E2′ on the tooth root side, the predetermined region A in the tooth flank is the 2 teeth mating region E2 on the tooth tip side. - According such a shape, the configuration of the predetermined region A in at least the one
tooth flank 7 of eachtooth 1 can be formed such that the mating with the teeth (2) of the mating gear (G2) starts from the corner portion on the oneend portion 5 side in the tooth width direction of thetooth tip surface 3 with the point contact or the line contact shorter than the total tooth width, and thereafter, gradually shifts to the line contact so that the length ofcontact line 10 thereof is sequentially increased as the line contact moves from the tooth tip side (3) toward the tooth root side (4). In this case, mainly in the gear on a driven side, the contact at the mating time of theopposite teeth - Further, in the mating of the
teeth portion 9 is formed in the tooth flank of eachtooth 1 as described above, thecontact line 10 in the portion where the tooth sliding speed is higher is reduced so that a contact area is small, and therefore, sliding noise due to the tooth sliding can also be reduced. - Incidentally, in the mating of
opposite teeth FIG. 1 , since portions serving as main power transmission planes are the 1 tooth mating region E1 and the 2 teeth mating region E2′ on the tooth root side, shown inFIG. 4 , the tooth flank is formed from one edge up to the other edge in a tooth width W3 direction, and therefore, the rotational motion can be surely and sufficiently transmitted. - Moreover, in
FIG. 3 , aboundary line 14 on a side of thetooth flank 7 and aboundary line 15 on an end face on theother end portion 6 side, of the chamferedportion 9 which is cut away from the onetooth flank 7 in the triangular inclined plane, are formed in a linear shape. However, these boundary lines are not limited to this shape, and may be formed in a curved shape. Further, the chamferedportion 9 is not limited to the inclined plane, and may be formed in a convex curved surface or a concave curved surface, or may be formed in a lightening shape of fixed depth. Furthermore, differently from the example ofFIG. 4 , in the case where the mating rate to the teeth (2) of the mating gear (G2) is equal to or larger than 2 but is equal to or smaller than 3, a region on the tooth tip side from the vicinity of the branching point between the 3 teeth mating and the 2 teeth mating of the tooth tip side may be made the predetermined region A. -
FIG. 5 is a front elevation view showing the entire shape of the one gear G1 configured as described in the above. InFIG. 5 , the gear G1 is configured such that the plurality ofteeth web 11 of substantially circular plate, and aboss 13 through which a shaft bore 12 fixing therein a rotation shaft is formed, is formed on a center portion of theweb 11, so that the rotational motion is transmitted between parallel two shafts. Note, the symbol P1 indicates the pitch circle of the one gear G1. -
FIG. 6 is a main part perspective view showing a second embodiment of the shape of thetooth 1 of the gear G1. In this embodiment, the predetermined region A in the tooth flank is chamfered so that the configuration thereof is made to be inclined planes which extend from the one place in the tooth width direction on thecrossing 8 of the onetooth flank 7 and thetooth tip surface 3 to both of the end faces of thetooth 1. Namely, chamferedportions tooth flank 7 predetermined places in the tooth width direction on thecrossing 8 of the onetooth flank 7 and thetooth tip surface 3 in triangular inclined planes, in this case, from acenter portion 16 toward the involute curve portions on theend portion - According to such a shape, the configuration of the predetermined region A in at least the one
tooth flank 7 of eachtooth 1 can be formed such that the mating with the teeth (2) of the mating gear (G2) starts from thecenter portion 16 in the tooth width direction of thetooth tip surface 3 with the point contact or the line contact shorter than the total tooth width, and thereafter, gradually shifts to the line contact so that the length ofcontact line 10 thereof is sequentially increased as the line contact moves from the tooth tip side (3) toward the tooth root side (4). In this case, the contact at the mating time of theopposite teeth - Incidentally, in
FIG. 6 , boundary lines on thetooth flank 7 side and boundary lines on the end faces on theend portion portions tooth flank 7 in the triangular inclined planes, are formed in a linear shape. However, these boundary lines are not limited to this shape, and may be formed in a curved shape. Further, thechamfered portions -
FIGS. 7A and 7B are main part perspective views showing modified examples of the shape of thetooth 1 of the gear G1 in the second embodiment. In these modified examples, a position (16) of the one place in the tooth width direction in the embodiment shown inFIG. 6 for when the chamfering is performed so as to form, on thecrossing 8 of the onetooth flank 7 and thetooth tip surface 3, the inclined planes which extend from the one place in the tooth width direction toward both of the end faces of thetooth 1, is not limited to the center portion in the tooth width direction, and is set at an arbitrary position in the tooth width direction within the tooth width for eachtooth 1.FIG. 7A shows a state where the position (16) of the one place is set so as to be shifted irregularly within the tooth width.FIG. 7B shows a state where the position (16) of the one place is set to be shifted sequentially from the one side end portion to the other end portion within the tooth width. -
FIGS. 8A through 8D are main part perspective views showing further modified examples of the shape of thetooth 1 of the gear G1 in the second embodiment. In each of these modified examples, arecess 9 e of triangle, square, trapezoid or the like of certain fixed depth is formed between thechamfered portions tooth flank 7 in the embodiment shown inFIG. 6 . In this case, it is possible to further reduce the length of the line contact on the tooth tip side in eachtooth 1. -
FIG. 9 is a main part perspective view showing a third embodiment of the shape of thetooth 1 of the gear G1. In this embodiment, chippedportions tooth flank 7 to both of the end face sides toward the crossing 8 of thetooth flank 7 and thetooth tip surface 3. Namely, the chippedportions tooth flank 7 the triangular inclined planes which extend from asite 18 of the one place on the onetooth flank 7 to both of the end face sides toward the crossing 8 of thetooth flank 7 and thetooth tip surface 3. - According to such a shape, the configuration of the predetermined region A in at least the one
tooth flank 7 of eachtooth 1 can be formed such that the mating with the teeth (2) of the mating gear (G2) is started from the corner portion on the oneend portion 5 side or theother end portion 6 side in the tooth width direction of thetooth tip surface 3 with the point contact or the line contact shorter than the total tooth width, and thereafter, is gradually shifted to the line contact so that the length ofcontact line 10 thereof is sequentially increased as the line contact moves from the tooth tip side (3) toward the tooth root side (4). In this case, the contact at the mating time of theopposite teeth - Incidentally, in
FIG. 9 , boundary lines on thetooth flank 7 side of the chippedportions tooth flank 7 in the triangular inclined planes, are formed in a linear shape. However, these boundary lines are not limited to this shape, and may be formed in a curved shape. -
FIGS. 10A and 10B are main part perspective views showing modified examples of the shape of thetooth 1 of the gear G1 in the third embodiment. In each of these modified examples, in place of the chippedportions tooth flank 7 in the embodiment shown inFIG. 9 , a lighteningportion 30 of triangle, trapezoid or the like of certain fixed depth is formed on the onetooth flank 7 toward the crossing 8 of thetooth flank 7 and thetooth tip surface 3. -
FIGS. 11A through 11D are main part perspective views showing further modified examples of the shape of thetooth 1 of the gear G1 in the third embodiment. In each of these modified examples, the chippedportions FIG. 9 are formed on plural places in the onetooth flank 7. InFIG. 11A , the chippedportions tooth flank 7 triangular inclined planes which extend from twosites tooth flank 7 toward the crossing 8 of thetooth flank 7 and thetooth tip surface 3 to both of the end face sides. Further, inFIG. 11B , the chippedportions tooth flank 7 triangular incline planes which extend from threesites tooth flank 7 toward the crossing 8 of thetooth flank 7 and thetooth tip 3 to both of the end face sides. Similarly to this, the chippedportions tooth flank 7 triangular inclined planes which extend from foursites FIG. 11C , and fivesites FIG. 11D , on the onetooth flank 7 toward the crossing 8 of thetooth flank 7 and thetooth tip surface 3 to both of the end face sides. -
FIGS. 12A though 12C are main part perspective views showing still further modified examples of the shape of thetooth 1 of the gear G1 in the third embodiment. In each of these modified examples, as shown inFIG. 12A , for the predetermined region A in the tooth flank in the embodiment shown inFIG. 9 , the chippedportion 17 is formed, by chipping off from the tooth flank 7 a fan-shaped concave curved surface which extends from thesite 18 of the one place on the onetooth flank 7 toward the crossing 8 of thetooth flank 7 and thetooth tip surface 3 to both of the end face sides. Further, inFIG. 12B , the chippedportion 17 is formed in plural places by chipping off or cutting away from thetooth flank 7 fan-shaped concave curved surfaces which extend from the twosites tooth flank 7 toward the crossing 8 of thetooth flank 7 and thetooth tip surface 3 to both of the end face sides Furthermore, inFIG. 12C , the chippedportion 17 is formed in plural places by chipping off from thetooth flank 7 fan-shaped concave curved surfaces which extend from the threesites tooth flank 7 toward the crossing 8 of thetooth flank 7 and thetooth tip surface 3 to both of the end face sides. -
FIG. 13 is a main part perspective view showing a fourth embodiment of the shape of thetooth 1 of the gear G1. In this embodiment, for the predetermined region A in the tooth flank, acurved surface 19 which gradually decreases the tooth thickness is formed from the one end face of the tooth toward the other end face thereof in the tooth width direction of the onetooth flank 7. Namely, thecurved surface 19 is formed in a convex curved surface, and smoothly connects withparallel curves 22 between aninvolute curve 20 on the oneend portion 5 side in the tooth width direction of the onetooth flank 7 and acurve 21 which modifies the tooth thickness of thetooth tip surface 3 on theother end portion 6 side with a modification amount p. At this time, a planar vision shape of thecurved surface 19 viewed from above thetooth tip surface 3 of thetooth 1 inFIG. 13 is shown inFIG. 14 , in which a curvature radius r of thecurved surface 19 in the tooth width direction is sequentially increased from the tooth tip to thetooth root 4 side. - According to such a shape, the configuration of the predetermined region A in at least the one
tooth flank 7 of eachtooth 1 can be formed such that the mating with the teeth (2) of the mating gear (G2) starts from the oneend portion 5 side in the tooth width direction of thetooth tip surface 3 with the point contact or the line contact shorter than the total tooth width, and thereafter, gradually shifts to the line contact so that the length of contact line thereof is sequentially increased as the line contact moves from the tooth tip side (3) toward the tooth root side (4). In this case, the contact at the mating time of theopposite teeth - Incidentally, in
FIG. 13 , thecurve 21 which modifies, with the modification amount p, the tooth thickness of thetooth tip surface 3 to be thinned on the side of theother end portion 6 in the tooth width direction in the onetooth flank 7, is made linear. However, the shape of thecurve 21 is not limited to the above, and may be formed in a curved shape. -
FIGS. 15A and 15B are explanatory diagrams showing modified examples of the shape of thetooth 1 of the fourth embodiment shown inFIG. 13 . Each of these modified examples, similarly toFIG. 14 , shows the planar vision shape of thecurved surface 19 viewed from above thetooth tip surface 3 of thetooth 1 InFIG. 15A , theinvolute curve 20 on the oneend portion 5 side and thecurve 21 on theother end portion 6 side, in the tooth width direction of the onetooth flank 7 shown inFIG. 13 , are connected to each other with parallel lines. At this time, thecurved surface 19 viewed from above thetooth tip surface 3 of thetooth 1 is planar, and an angle α at which the oneend portion 5 in the tooth width direction and thecurved surface 19 intersect with each other, is sequentially increased from the tooth tip through the tooth root side. In this case, it becomes easy to perform the processing and finishing of thetooth flank 7 of thetooth 1. - Further, in
FIG. 15B , theinvolute curve 20 on the oneend portion 5 side and thecurve 21 on theother end portion 6 side, in the tooth width direction of the onetooth flank 7 shown inFIG. 13 , are smoothly connected to each other withparallel lines 22 each of which curvature direction is reversed halfway, to thereby form the curved surface shape. At this time, the planar vision shape of thecurved surface 19 viewed from above thetooth tip surface 3 of thetooth 1 has a shape obtained by connecting two curved surfaces each of which curvature direction is reversed halfway, and provided that a curvature radius of the one curved surface in the tooth width direction is r1 and a curvature radius of the other curved surface in the tooth width direction is r2, each of the curvature radiuses r1 and r2 is sequentially increased from the tooth tip through thetooth root 4 side. -
FIG. 16 is a main part perspective view showing a fifth embodiment of the shape of thetooth 1 of the gear G1. In this embodiment, for the predetermined region A in the tooth flank, curved surfaces 19 a and 19 b each of which gradually decreases the tooth thickness are formed on predetermined places in the tooth width direction of the onetooth flank 7, in this case, from the center portion toward both of the end face sides. Namely, each of thecurved surfaces parallel curves 22 between theinvolute curve 20 on the center portion in the tooth width direction of the onetooth flank 7 and curves 21 a and 21 b which respectively modify with a modification amount q the tooth thickness of thetooth tip surface 3 on the oneend portion 5 side and theother end portion 6 side. At this time, planar vision shape of thecurved surface tooth tip surface 3 of thetooth 1 inFIG. 16 is shown inFIG. 17 , in which a curvature radius r3 in the tooth width direction obtained by connecting the twocurved surfaces tooth root 4 side. - According to such a shape, the configuration of the predetermined region A in at least the one
tooth flank 7 of eachtooth 1 can be formed such that the mating with the teeth (2) of the mating gear (G2) starts from the center portion in the tooth width direction of thetooth tip surface 3 with the point contact or the line contact shorter than the total tooth width, and thereafter, gradually shifts to the line contact so that the length of contact line thereof is sequentially increased as the line contact moves from the tooth tip side (3) toward the tooth root side (4). In this case, the contact at the mating time of theopposite teeth - Incidentally, in
FIG. 16 , thecurves tooth tip surface 3 to be thinned on the side of the oneend portion 5 and the side of theother end portion 6 in the tooth width direction of the onetooth flank 7, are made linear. However, the shape of thecurves -
FIGS. 18A and 18B are explanatory diagrams showing modified examples of the shape of thetooth 1 of the fifth embodiment shown inFIG. 16 . These modified examples, similarly toFIG. 17 , show the planar vision shapes of thecurved surfaces tooth tip surface 3 of thetooth 1. InFIG. 18A , theinvolute curve 20 on the center portion in the tooth width direction of the onetooth flank 7 shown inFIG. 16 , and thecurves end portion 5 and the side of theother end portion 6, are connected to each other with parallel lines. At this time, thecurved surfaces tooth tip surface 3 of thetooth 1 are planar, and an angle β at which thecurved surfaces tooth root 4. In this case, it becomes easy to perform the processing and finishing of thetooth flank 7 of thetooth 1. - Further, in
FIG. 18B , theinvolute curve 20 on the center portion in the tooth width direction of the onetooth flank 7 shown inFIG. 16 , and thecurves end portion 5 side and theother end portion 6 side, are smoothly connected to each other with theparallel lines 22 each of which curvature direction is reversed halfway, to thereby form the curved surface shapes. At this time, the planar vision shape of thecurved surfaces tooth tip surface 3 of thetooth 1 is in a shape obtained by connecting two curved surfaces each of which curvature direction is reverted halfway, and provided that a curvature radius in the tooth width direction of the curved surface on the center portion is r4 and a curvature radius in the tooth width direction of each of the curved surfaces on both sides is r5, the curvature radiuses r4 and r5 are sequentially increased from the tooth tip through the side of thetooth root 4. -
FIGS. 19A through 19C are main part perspective views showing a sixth embodiment of the shape of thetooth 1 of the gear G1. In this embodiment, as shown inFIG. 19A , for the predetermined region A in the tooth flank, a triangular notchedconcave portion 23 is formed, by chipping off from the one tooth flank 7 a triangular shape which extends from thesite 18 of the one place on the onetooth flank 7 to both of the sides of theend portion tooth tip surface 3 and also runs through to the other tooth flank. Further, inFIG. 19B , the triangular notchedconcave portion 23 is formed in plural places, by chipping off from the onetooth flank 7 triangular shapes which extend from the twosites tooth flank 7 to both of theend portion tooth tip surface 3 and also run through to the other tooth flank. Furthermore, inFIG. 19C , the triangular notchedconcave portion 23 is formed in plural places, by chipping off from the onetooth flank 7 triangular shapes from the threesites tooth flank 7 to both sides of theend portion tooth tip surface 3 and also run through to the other tooth flank. -
FIGS. 20A through 20D are perspective views showing a main part of a seventh embodiment of the shape of thetooth 1 of the gear G1. In this embodiment, as shown inFIG. 20A , a predetermined region A′ in at least the onetooth flank 7 of eachtooth 1 is formed in a configuration such that the mating with the teeth (2) of the mating gear (G2) starts from at least one place in the tooth width direction on a crossing 24 of thetooth flank 7 and a tooth root surface with the point contact or the line contact shorter than the total tooth width, and thereafter, gradually shifts to the line contact so that the length of contact line thereof is sequentially increased as the line contact moves from a tooth root side (24) toward the tooth tip side (3). Namely, chamferedportions tooth flank 7 predetermined places in the tooth width direction on the crossing 24 of the onetooth flank 7 and the tooth root side, in this case from acenter portion 25 toward the involute curve portions on the end face sides on both sides - According to such a shape, mainly in the gear on a driving side, the contact at the mating time of the
opposite teeth - Further,
FIGS. 20B through 20D are partial perspective views showing a main part of the respective modified examples of the shape of thetooth 1 of the gear G1 in the seventh embodiment. For these modified examples, inFIG. 20B , chippedportions tooth flank 7 the triangular inclined planes which extend from asite 26 of the one place on the onetooth flank 7 to both of the end face sides toward the crossing 24 of thetooth flank 7 and the tooth root surface. Further, inFIG. 20C , the chippedportions tooth flank 7 the triangular inclined planes which extend from twosites tooth flank 7 to both of the end face sides toward the crossing 24 of thetooth flank 7 and the tooth root surface. Furthermore, inFIG. 20D , the chippedportions tooth flank 7 the triangular inclined planes which extend from threesites tooth flank 7 to both of the end face sides toward the crossing 24 of thetooth flank 7 and the tooth root surface. -
FIGS. 21A through 21D are partial perspective views showing a main part of an eighth embodiment of the shape of thetooth 1 of the gear G1. In this embodiment, the modification of the tooth profile on the tooth tip side shown inFIG. 6 is basically combined with the modification of the tooth profile on the tooth root side shown inFIG. 20A . To be specific,FIG. 21A shows the combination of the embodiment shown inFIG. 6 and the embodiment shown inFIG. 20A , andFIG. 21B shows the combination of the embodiment shown inFIG. 9 and the embodiment shown inFIG. 20B . Further,FIG. 21C shows the combination of the embodiment shown inFIG. 11A and the embodiment shown inFIG. 20C , andFIG. 21D shows the combination of the embodiment shown inFIG. 11B and the embodiment shown inFIG. 20D . -
FIGS. 22A through 22D are partial perspective views showing a main part of a ninth embodiment of the shape of thetooth 1 of the gear G1. For this embodiment, as shown inFIG. 22A , the configuration of the predetermined region A in at least the onetooth flank 7 of eachtooth 1 is formed such that the mating with the teeth (2) of the mating gear (G2) starts from at least one place in the tooth width direction on thecrossing 8 of thetooth flank 7 and thetooth tip surface 3 with the point contact or the line contact shorter than the total tooth width, and thereafter, rapidly or in stepwise shifts to the line contact of the total tooth width from the tooth tip side toward the tooth root side so that the length ofcontact line 10 thereof is increased. Namely, rectangular chippedportions tooth flank 7 predetermined places in the tooth width direction on thecrossing 8 of the onetooth flank 7 and thetooth tip surface 3, in rectangular concave stepped portions, in this case, from the center portion toward the involute curve portions on the end face sides on both sides. - According to such a shape, mainly in the gear on the driven side, the contact at the mating time of the
Opposite teeth tooth flank 7, but starts with the point contact or the line contact shorter than the total tooth width. Then, the point contact rapidly or in stepwise shifts to the line contact shorter than the total tooth width, and thereafter, further rapidly or in stepwise shifts to the larger line contact within the range of the total tooth width. Further, the line contact shorter than the total tooth width then rapidly or in stepwise shifts to the larger line contact within the range of the total tooth width. As a result, the contact to the teeth (2) of the mating gear (G2) is softened and therefore, the shock can be absorbed. - Further,
FIGS. 22B through 22D are partial perspective views showing a main part of the respective modified examples of the shape of thetooth 1 of the gear G1 in the ninth embodiment. For these modified examples, inFIG. 22B , a rectangular chippedportion 27 is formed, by chipping off from thetooth flank 7 the center portion in the tooth width direction on thecrossing 8 of the onetooth flank 7 and thetooth tip surface 3 in a rectangular concave stepped portion. Further, inFIG. 22C , stepped chippedportions tooth flank 7 predetermined places in the tooth width direction on thecrossing 8 of the onetooth flank 7 and thetooth tip surface 3 in stair concave stepped portions, in this case, from the center portion toward the involute curve portions on the end face sides on both sides. In this case, the mating with the teeth of the mating gear starts from at least one place in the tooth width direction on thecrossing 8 of thetooth flank 7 and thetooth tip surface 3 with the point contact or the line contact shorter than the total tooth width, and thereafter, in stepwise shifts to the line contact of the total tooth width from the tooth tip side toward the tooth root side so that the length ofcontact line 10 thereof is increased. Furthermore, inFIG. 22D , in the predetermined region A in the onetooth flank 7 of eachtooth 1, a plurality ofrecesses 29 of small diameter (for example, rectangular recesses) is intermittently formed in parallel to thecrossing 8 of thetooth flank 7 and thetooth tip surface 3, toward the involute curve portions on the end face sides on both sides, and also, a plurality of rows of this plurality ofrecesses 29 is formed at a small interval. In this case, in a range of the predetermined region A in the onetooth flank 7, the mating with the teeth of the mating gear starts with the line contact shorter than the total tooth width, and thereafter, rapidly shifts to the line contact of the total tooth width so that the length of contact line thereof is increased. -
FIGS. 23A and 23B are partial perspective views showing a main part of the tenth embodiment of the shape of thetooth 1 of the gear G1. For this embodiment, as shown inFIG. 23A , the configuration of the predetermined region A′ in at least the onetooth flank 7 of eachtooth 1 is formed such that the mating with the teeth (2) of the mating gear (G2) starts from at least one place in the tooth width direction on the crossing 24 of thetooth flank 7 and the tooth root surface with the point contact or the line contact shorter than the total tooth width, and thereafter, rapidly or in stepwise shifts to the line contact of the total tooth width from the tooth root side (24) toward the tooth tip side (3) so that the length of contact line thereof is increased. Namely, rectangular chippedportions tooth flank 7 predetermined places in the tooth width direction on the crossing 24 of the onetooth flank 7 and the tooth root surface in rectangular concave stepped portions, in this case, from the center portion toward the involute curve portions on the end face sides on both sides. - According to such a shape, mainly in the gear on the driving side, the contact at the mating time of the
opposite teeth - Further,
FIG. 23B is a perspective view showing a main part of the modified example of the shape of thetooth 1 of the gear G1 in the tenth embodiment. In this modified example, the rectangular chippedportion 27 is formed, by chipping off from the tooth flank 7 a predetermined place in the tooth width direction on the crossing 24 of the onetooth flank 7 and the tooth root surface in the rectangular concave stepped portion, in this case, at the center portion. Note, although omitted inFIG. 23 , the stepped chippedportions FIG. 22C , or the plurality of small diameter recesses 29 shown inFIG. 22D may be formed from the tooth root surface side (24) of thetooth flank 7 toward the tooth tip surface side (3) thereof. - In the above description, in the predetermined region in the tooth flank of each
tooth 1, the chamfered portion 9 (refer toFIG. 3 ), the chippedportions FIG. 9 ), the curved surface 19 (refer toFIG. 13 ), the rectangular chippedportions portions FIGS. 22A through 22D ) are formed on only the onetooth flank 7. However, the present invention is not limited to the above, and the chamferedportion 9, the chippedportions curved surface 19, the rectangular chippedportions portions tooth 1. In this case, the above described chamfered portion is not limited to the inclined plane, and may be formed in a convex curved surface or a concave curved surface. - Next, there will be described a shape of the other gear G2 constituting the gearing apparatus shown in
FIG. 1 . This gear G2 is provided with the plurality ofteeth teeth 2 are mated with theteeth 1 of the mating gear G1, to thereby transmit the rotational motion. Thetooth 2 is formed in a shape exactly same as the shape of thetooth 1 of the one gear G1 shown inFIGS. 3 through 23 A and 23B. Further, a predetermined region in a tooth flank of eachtooth 2 is a region on a tooth tip side or a tooth root side from the vicinity of a branching point between the (n+1) teeth mating and the n teeth mating (n is integer of one or more) at the mating time with theteeth 1 of the mating gear G1. Incidentally, for the shape of the other gear G2, similarly to the above, the chamferedportion 9, the chippedportions curved surface 19, the rectangular chippedportions portions tooth 2. -
FIGS. 24A through 24C are cross section explanatory diagrams showing combination states of the one gear G1 and the other gear G2 in the gearing apparatus configured as described above. InFIG. 24A , for the one gear G1 in the pair of gears G1 and G2, on the tooth flank of eachtooth 1 shown inFIG. 3 , the chamferedportion 9 is formed, by cutting away from the onetooth flank 7 the triangular inclined plane from the corner portion on the oneend portion 5 side in the tooth width direction of thetooth tip surface 3 toward the involute curve portion on theother end portion 6 side. In this case, the other gear G2 is formed to have the tooth profile of the standard gear. - In
FIG. 24B , for the pair of gears G1 and G2, on the tooth flank of each ofteeth portions tooth flank 7 shown inFIG. 3 the triangular inclined plane from the corner portion on the oneend portion 5 side in the tooth width direction of thetooth tip surface 3, toward the involute curve portion on theother end portion 6 side. In this case, an opposed state of the inclined planes of the chamferedportions - In
FIG. 24C , also for the pair of gears G1 and G2, on the tooth flank of each ofteeth portions tooth flank 7 shown inFIG. 3 the triangular inclined plane from the corner portion on the oneend portion 5 side in the tooth width direction of thetooth tip surface 3, toward the involute curve portion on theother end portion 6 side. In this case, the opposed state of the inclined planes of the chamferedportions - Incidentally, in
FIGS. 24A through 24C , there has been shown the case where theteeth 1 of the gear shown inFIG. 3 is used to configure the gearing apparatus. However, the present invention is not limited thereto, and the gearing apparatus can be configured by using in any one of all of the above describedgear teeth 1. Further, in the present invention, materials for each of the pair of gears G1 and G2 may be a metal material or a resin material. In the case of resin gears G1 and G2, the production thereof can be made by the injection molding.
Claims (12)
1. Gears comprised of one and the other mutually engaged gears, each having a plurality of teeth to be mated with teeth of the other engaged gear to thereby transmit a rotational motion,
wherein a predetermined region in at least one of tooth flanks of each tooth of the one gear is formed in a configuration such that mating of said each tooth of the one gear with the teeth of the other engaged gear starts with a point contact or a line contact shorter than a total length of a tooth width of the one gear from at least one place in a tooth width direction on a crossing of said tooth flank and a surface of tooth tip of said one gear and thereafter, gradually shifts to the line contact so that a length of contact line thereof is continuously increased as the line contact moves from a tooth tip side toward a tooth root side.
2. Gears according to claim 1 , wherein said predetermined region in the tooth flank is chamfered, so that a configuration thereof is made to be an inclined plane which extends from at least one place in the tooth width direction on said crossing of the tooth flank and the surface of tooth tip, toward one of end faces of the tooth or both of the end faces thereof.
3. Gears according to claim 1 , wherein a chipped portion is formed, so that a configuration of said predetermined region in the tooth flank is made to be an inclined plane which extends from one place or a plurality of places of said tooth flank to both of end faces of the tooth toward said crossing of the tooth flank and the surface of tooth tip.
4. Gears according to claim 1 , wherein in a configuration of said predetermined region in the tooth flank, a curved surface which gradually decreases the tooth thickness, is formed toward one of end faces of the tooth or both of the end faces thereof in the tooth width direction of said tooth flank.
5. Gears according to claim 1 , wherein said predetermined region in the tooth flank is a region on the tooth tip side from the vicinity of a branching point between the (n+1) teeth mating and the n teeth mating (n is integer of one or more) at the mating time with the teeth of the mating gear.
6. A gearing apparatus for transmitting a rotational motion from one to the other of two associated shafts by engaging a pair of gears to allow opposite teeth of the engaged gears to be mated with each other,
wherein for at least one gear of the pair of engaged gears, a predetermined region in at least one of tooth flanks of each tooth is formed in a configuration such that mating of the each tooth of the one gear with the teeth of the other engaged gear starts with a point contact or a line contact shorter than a total length of a tooth width from at least one place in a tooth width direction on a crossing of the tooth flank and a surface of tooth tip of said one gear and thereafter, gradually shifts to the line contact so that a length of contact line thereof is continuously increased as the line contact moves from a tooth tip side toward a tooth root side.
7. Gears comprised of one and the other mutually engaged gears, each having a plurality of teeth to be mated with teeth of the other engaged gear to thereby transmit a rotational motion,
wherein a predetermined region in at least one of tooth flanks of each tooth is formed in a configuration such that mating of said each tooth of the one gear with the teeth of the other engaged gear starts with a point contact or a line contact shorter than a total length of a tooth width of one gear from at least one place in a tooth width direction on a crossing of said tooth flank and a surface of tooth root of said one gear and thereafter, gradually shifted to the line contact so that a length of contact line thereof is continuously increased as the line contact moves from a tooth root side toward a tooth tip side.
8. A gearing apparatus for transmitting a rotational motion from one to the other of two associated shafts by engaging a pair of gears to allow opposite teeth of the engaged gears to be mated with each other,
wherein for at least one of the pair of engaged gears, a predetermined region in at least one of tooth flanks of each tooth is formed in a configuration such that mating of the each tooth of the one gear with teeth of the other engaged gear starts with a point contact or a line contact shorter than a total length of a tooth width from at least one place in a tooth width direction on a crossing of the tooth flank and a surface of tooth root of said one gear and thereafter, gradually shifts to the line contact so that a length of contact line thereof is continuously increased as the line contact moves from a tooth root side toward a tooth tip side.
9. Gears comprised of one and the other mutually engaged gears, each having a plurality of teeth to be mated with teeth of the other engaged gear to thereby transmit a rotational motion,
wherein a predetermined region in at least one of tooth flanks of each tooth of the one gear is formed in a configuration such that mating of said each tooth of the one gear with the teeth of the other engaged gear starts with a point contact or a line contact shorter than a total length of a tooth width of the one gear from at least one place in a tooth width direction on a crossing of said tooth flank and a surface of tooth tip of said one gear and thereafter, rapidly or in stepwise shifts to the line contact of the total tooth width from a tooth tip side toward a tooth root side so that the length of contact line thereof is increased.
10. A gearing apparatus for transmitting a rotational motion from one to the other of two associated shafts by engaging of a pair of gears to allow opposite teeth of the engaged gears to be mated with each other,
wherein for at least one gear of the pair of engaged gears, a predetermined region in at least one of tooth flanks of each tooth is formed in a configuration such that, mating of the each tooth of the one gear with the teeth of the other engaged gear starts with a point contact or a line contact shorter than a total length of a tooth width from at least one place in a tooth width direction on a crossing of the tooth flank and a surface of tooth tip and thereafter, rapidly or in stepwise shifts to the line contact of the total tooth width from a tooth tip side toward a tooth root side so that a length of contact line thereof is increased.
11. Gears comprised of one and the other mutually engaged gears, each having a plurality of teeth to be mated with teeth of the other engaged gear to thereby transmit a rotational motion,
wherein a predetermined region in at least one of tooth flanks of each tooth is formed in a configuration such that mating of said each tooth of the one gears with the teeth of the other engaged gear starts with a point contact or a line contact shorter than a total length of a tooth width of the one gear from at least one place in a tooth width direction on a crossing of said tooth flank and a surface of tooth root of said one gear and thereafter, rapidly or in stepwise shifts to the line contact of the total tooth width from a tooth root side toward a tooth tip side so that the length of contact line thereof is increased.
12. A gearing apparatus for transmitting a rotational motion from one to the other of two associated shafts by engaging a pair of gears to allow opposite teeth of the engaged gears to be mated with each other,
wherein for at least one gear of the pair of engaged gears, a predetermined region in at least one of tooth flanks of each tooth is formed in a configuration such that mating of the each tooth of the one gear with the teeth of the other engaged gear starts with a point contact or a line contact shorter than a total length of a tooth width from at least one place in a tooth width direction on a crossing of said tooth flank and a surface of tooth root of said one gear and thereafter, rapidly or in stepwise shifts to the line contact of the total tooth width from a tooth root side toward a tooth tip side so that the length of contact line thereof is increased.
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US12/567,672 US8201471B2 (en) | 2005-09-28 | 2009-09-25 | Gears and gearing apparatus |
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US8225690B2 (en) * | 2007-02-19 | 2012-07-24 | Toyota Jidosha Kabushiki Kaisha | Power transmission device |
US20080236320A1 (en) * | 2007-03-26 | 2008-10-02 | Enplas Corporation | Resin gear |
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US20110249988A1 (en) * | 2010-04-07 | 2011-10-13 | Canon Kabushiki Kaisha | Image forming apparatus |
US8744313B2 (en) * | 2010-04-07 | 2014-06-03 | Canon Kabushiki Kaisha | Image forming apparatus |
US20130160589A1 (en) * | 2010-09-24 | 2013-06-27 | Miba Sinter Austria Gmbh | Toothed wheel and backlash free gear train |
US9222569B2 (en) * | 2010-09-24 | 2015-12-29 | Miba Sinter Austria Gmbh | Toothed wheel and backlash free gear train |
US20150377336A1 (en) * | 2013-03-15 | 2015-12-31 | Aisin Aw Co., Ltd. | Drive plate and method for manufacturing the same |
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US10584784B2 (en) | 2014-12-05 | 2020-03-10 | Enplas Corporation | Resin helical gear |
CN108138936A (en) * | 2015-09-29 | 2018-06-08 | 恩普乐斯股份有限公司 | Resin helical gear |
US20180274649A1 (en) * | 2015-09-29 | 2018-09-27 | Enplas Corporation | Plastic helical gear |
US10816076B2 (en) * | 2015-09-29 | 2020-10-27 | Enplas Corporation | Plastic helical gear |
US20180259055A1 (en) * | 2015-11-23 | 2018-09-13 | Bayerische Motoren Werke Aktiengesellschaft | Helical Tooth System Having Modified Tooth Meshing |
US10907720B2 (en) * | 2015-11-23 | 2021-02-02 | Bayerische Motoren Werke Aktiengesellschaft | Helical tooth system having modified tooth meshing |
WO2017143340A1 (en) * | 2016-02-18 | 2017-08-24 | Purdue Research Foundation | Pressure compensated external gear machine |
US11125227B2 (en) | 2016-02-18 | 2021-09-21 | Purdue Research Foundation | Pressure compensated external gear machine |
US20170276219A1 (en) * | 2016-03-23 | 2017-09-28 | Kabushiki Kaisha Tokai Rika Denki Seisakusho | Gear drive device |
US10393240B2 (en) * | 2016-03-23 | 2019-08-27 | Kabushiki Kaisha Tokai Rika Denki Seisakusho | Gear drive device |
US11054013B1 (en) * | 2021-01-08 | 2021-07-06 | Enplas Corporation | Profile modification for planetary gear device gear teeth |
Also Published As
Publication number | Publication date |
---|---|
CN1940350B (en) | 2012-01-11 |
EP1770308A2 (en) | 2007-04-04 |
JP4868893B2 (en) | 2012-02-01 |
CN1940350A (en) | 2007-04-04 |
JP2007120743A (en) | 2007-05-17 |
US20100011895A1 (en) | 2010-01-21 |
US8201471B2 (en) | 2012-06-19 |
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