ROTARY MEMBER FOR TRANSMITTING DRIVE FORCE/BRAKE FORCE

Abstract: A rotary member (1) for transmitting a drive force or brake force, the rotary member comprising an annular hub portion (3) arranged on a center side, an annular ring portion (4) arranged on an outer circumferential side, and a plurality of arm portions (5) connecting the hub portion (2) and the ring portion (4), with a plurality of weight reduction holes (6) partitioned by the arm portions (5) between the hub portion (3) and the ring portion (4). The plurality of arm portions (5) are provided so that centers (P1) of their distal end portions on the ring portion (4) side and centers (P2) of their proximal end portions on the hub portion (3) side are offset in one circumferential direction, respectively, and the hub portion (3) and the ring portion (4) are not directly connected to each other by longitudinal sectional lines that intersect with the arm portions (5) in a radial direction of the rotary member (1).

Description: TITLE OF THE INVENTION ROTARY MEMBER FOR TRANSMITTING DRIVE FORCE/BRAKE FORCE BACKGROUND OF THE INVENTION The present invention relates to a rotary member for transmitting a drive force or a braking force of a sprocket, a brake disc or the like- In general, a mechanism having a pair of sprockets and a change laid therebetween has been widely used as a drive force transmission means in a motorcycle or a bicycle. Usually, a sprocket is integrally formed of an annular hub portion arranged in the center thereof, an annular ring portion arranged in a circumferential portion thereof, and a plurality of arm portions extending radially and arranged between the hub portion and the ring portion for connecting the hub portion and the ring portion at a constant angular interval in the circumferential direction. A carbon steel plate has been widely used as a material for the sprocket. In a manufacturing method, after the carbon steel plate has been machined to have a form of the sprocket by mechanical machining or pressing, a tooth portion is annealed to have a desired hardness. Thereafter, a finishing treatment is effected on the sprocket. Also, in view of an aesthetic design demand, there is a sprocket 100, as shown in Fig. 15, in which a center PR of a distal end portion on a ring portion 102 side and a center PH of a proximal end portion on a hub 103 side of each arm portion 101 are offset at a constant angle in the circumferential direction. On the other hand, a brake disc in which an annular brakin portion is formed in its outer circumferential portion and the brakin portion clamped by pad members to generate the braking force has bee extensively used as a braking mechanism in a motorcycle or the like A so-called floating disc brake mechanism has been widel practically used, inwhich abrakingportion againstwhichpadmember are to be pressed and a disc like hub portion externally fixedl mounted on an axle or the like are formed of discrete members, respectively; a plurality of pin members are mounted between the hu portion and the braking member; the braking portion is floatingl supported to the hubportion; and the braking portion andhub portion are slitted at their edge to thereby prevent a warpage of the dis brake caused by heat generated during the braking operation. Also, in a brake disc 110 as shown in Fig. 16, a hub portion 11 and a braking portion 112 are integrally formed with each other; th hub portion 111 and the braking portion 112 are coupled with eac other through a plurality of arm portions 113; and in view of th aesthetic design demand, a center PR of a distal end portion on braking portion 112 side and a center PH of a proximal end portion o a hub 111 side of each arm portion are offset in the circumferential direction with constant regularity. In the sprocket in which the arm portions are radially arranged, after the annealing treatment for the tooth portion, the ring portio tends to shrink inwardly, but the hardness of the ring portion per se is high by the annealing treatment so that the shrinkage force is applied to the arm portions and the hub portion as a compression stress. Then, due to the compression stress, such a phenomenon that portions, corresponding to the arm portions, of the hub portion are deformed inwardly is generated. For this reason, after the annealing treatment of the tooth portion, a machining is effected to the inner circumferential surface of the hubportion. A cutting step is required to keep the inner circumferential surface in an exact circle. Thus, there is a disadvantage that the manufacturing steps for the sprocket are complicated. Also, in order to solve this problem, it is possible to try to form the ring portion and the hub portion from discrete members like the braking portion and the hub portion of the floating disc brake. However, in this case, the number of the components is increased to raise the manufacturing cost corresponding to the additional components. The present applicant made and tested various changes in shape of the arm portions and weight reduction holes on the basis of the concept that the compression stress applied to the hub portion was reduced by elastically deforming the arm portions. As a result, the present applicant has found out that the centers of the distal ends of the arm portions on the ring portion side and the centers of the proximal ends of the arm portions on the hub portion side are offset in one circumferential direction with a constant regularity, respectively, so that the deformation of the inner circumferential surface of the hub portion 102 may be reduced. Also, as shown in Fig. 15, even if the distal ends and the proximal ends of the arm portio 101 are offset in one circumferential direction with a consta regularity, if there are regions where the hub portion 102 and t ring portion 103 are directly connected with each other b longitudinal sectional lines intersecting with the arm portions 10 in the radial direction of the sprocket 100 like regions A indicate by hatching, it has been found that the deformation of the inne circumferential surface of the hub portion 102 is remarkable. Namely, it has been found that not only in view of the desig demand but also of the demand on the manufacture, the distal en portions and the proximal end portions of the arm portion are offse in one circumferential direction with a constant regularity, and i addition, the arm portions are formed so that the hub portion and th ring portion are not directly connected to each other by th longitudinal sectional lines intersecting with the arm portions i the radial direction of the sprocket, and in other words, the ar portions and the weight reduction holes are formed so that the line in the radial direction of the sprocket are always kept to intersec with any weight reduction holes over the entire circumference of th sprocket, whereby it is possible to considerably reduce th deformation of the inner circumferential surface of the hub portion Also, even in a disc brake which is integrally made of a singl steel plate, after the braking portion is annealed, there occurred problem that is similar to that of the sprocket. In addition, due t the heat generation during the braking operation, the braking portio is expanded and a tension stress is effected at the arm portion so that the brake disc as a whole is subjected to the warpage. It is also found that the deformation of the inner circumferential surface of the hub portion or the warpage of the brake disc as a whole may be prevented in the same method. In the case where the ring portion is expandeddue to the heat generation during the brakingoperation, this expansion is effectively absorbed by the arm portions. SUMMARY OF THE INVENTION An object of the present invention is to provide a rotary member for transmitting a drive force/brake force, which can reduce a compression stress or tension stress to be effected on a hub portion and can effectively prevent a deformation of an inner circumferential surface of the hub portion or a warpage of the rotary member without requiring any complicated structure for the rotary member. According to the present invention, there is provided a rotary member for transmitting a drive force or brake force, the rotary member comprising an annular hub portion arranged on a center side, an annular ringportion arrangedon an outer circumferential side, and a plurality of arm portions connecting the hub portion and the ring portion, with aplurality ofweight reduction holes partitionedby the armportions between the hub portion and the ringportion, wherein the plurality of armportions are provided so that centers of their distal end portions on the ring portion side and centers of their proximal end portions on the hub portion side are offset in one circumferential direction, respectively, and the hub portion and the ring portion are not directly connected to each other by longitudinal sectional line that intersect with the arm portions in a radial direction of th rotary member. It is preferable that the centers of their distal end portion on the ring portion side and the centers of their proximal en portions on the hub portion side are offset in one circumferentia direction with a constant regularity, respectively, that the rotar member is a sprocket having a plurality of teeth along an oute circumferential portion of the ringportion, or that the rotary membe is a brake disc having a braking portion on the ring portion. In the rotary member for transmitting the drive force/brak force according to the present invention, since the plurality of ar portions are provided so that centers of their distal end portions o the ring portion side and centers of their proximal end portions o the hub portion side are offset in one circumferential direction respectively, and the hub portion and the ring portion are no directly connected to each other by longitudinal sectional lines tha intersect with the arm portions in a radial direction of the rotar member, the expansion or shrinkage of the ringportionmay be absorbe by the deformations of the arm portions and the weight reductio holes. Also, the weight reduction holes serve as spaces for allowin the elastic deformation of each arm portion and are deforme concomitant with the elastic deformation of the arm portion. Namely, since the distal ends and the proximal ends of the ar portions are offset in one circumferential direction, even if th distance between the ring portion and hub portion is changed due to the expansion or shrinkage of the ring portion, the arm portions are elastically deformed with their distal ends being expanded or shrunk in the radial direction, so that the change in this distance is effectively absorbed. Also, in each portion of the full length of each arm portion, since the longitudinal lines are not directly connected to the hub portion and the ring portion, the tension stress or compression stress due to the expansion or shrinkage of the ring portions is positively prevented from being applied directly to the hub portion by the tension of the arm portions. In addition, the tension stress or shrinkage is effectively applied to the armportions to accelerate the elastic deformation of the arm portions, so that the tension or compression stress to be applied to the hub portion is further effectively absorbed. Also, if the centers of the distal end portions of the plurality of arm portions and the centers of the proximal ends thereof are offset in one circumferential direction, respectively, with a constant regularity, the expansion or shrinkage of the ring portions may be absorbed with a good balance by the plurality of arm portions. If this rotary member is applied to the sprocket, the shrinkage into inside of the ring portion due to the annealing treatment to the tooth portions is effectively absorbed and the deformation of the inner circumferential surface of the hub may be prevented. Also, if the rotary member is applied to the brake disc, in the case way as in the case of the sprocket, the shrinkage into inside of the ring portion due to the annealing treatment to the braking portions is effectively absorbed and the deformation of the inner circumferential surface of the hub may be prevented. Even if the ring portion is expanded due to heat generation at brake operation, the arm portions are elastically deformed to absorb the change in distance between the ring portion and the hub portion due to the expansion, thus effectively preventing the warpage of the brake disc. BRIEF DESCRIPTION OF THE DRAWINGS In the accompanying drawings: Fig. 1 is a frontal view of a sprocket according to the invention; Fig. 2 is a view showing an operation of the sprocket; Fig. 3 is a view showing another operation of the sprocket; Fig. 4 is a frontal view showing a sprocket having another structure; Fig. 5 is a frontal view showing a sprocket having another structure; Fig. 6 is a frontal view showing a sprocket having another structure; Fig. 7 is a frontal view showing a sprocket having another structure; Fig. 8 is a frontal view showing a sprocket having another structure; Fig. 9 is a frontal view showing a sprocket having another structure; Fig. 10 is a frontal view showing a sprocket having another structure; Fig. 11 is a frontal view of a brake disc according to the invention; Fig. 12 is a view showing an operation of a brake disc according to the invention; Fig. 13 is a view showing another operation of a brake disc according to the invention; Fig. 14 is a frontal view showing a disc brake having another structure; Fig. 15 is a frontal view showing a conventional sprocket; and Fig. 16 is a frontal view showing a conventional brake disc. PREFERRED EMBODIMENT OF THE INVENTION Embodiments of the invention will now be described with reference to the accompanying drawings. <First Embodiment> A first embodiment is directed to a case where the present invention is applied to a sprocket for a torque transmission in a motorcycle. As shown in Fig. 1, a sprocket 1 is externally mounted on and fixed to a wheel hub shaft of a transmission (not shown) with bolts. The sprocket 1 has a hub portion 3 having an engagement hole 2 through which the wheel hub shaft is caused to centrally pass, an annular ring portion 4 on its outer circumferential side, and eight arm portions 5 each connecting the hub portion 3 and the ring portion 4 at a constant interval along the circumference. The sprocket 1 integrally formed of a carbon steel plate. Weight reducing holes 6 and the arm portions 5 are alternative formed between the ringportion 4 and the hub portion 3. Four mounti holes 7 for fastening the sprocket 1 are formed in the vicinity of t proximal ends of the arm portions 5 in the hub portion 3. A plurali of tooth portions 8 are formed in the outer circumferential porti of the ring portion 4. The tooth portions 8 are subjected to a he treatment so that they have a hardness in the range of 35 to 55 terms of Rockwll C. Namely, after the sprocket 1 is worked in the fo of a sprocket 1 by machining or pressing the carbon steel plate, t annealing treatment is applied to the tooth portions 8 or t tempering treatment is applied thereto after the annealing treatmen The eight arm portions 5 are formed in gentle curves as shown Fig. 1, and are alternatively arranged to be offset at offset angl θl and Θ2 in one circumferential direction relative to the center of the distal end on the ring portion 4 side and the center P2 of t proximal end on the hub portion 3 side. The centerline LI of each a portion 5 is arranged to be obliquely in one direction relative lines extending radially of the sprocket 1 and intersecting with t arm portion 5. Also, each arm portion 5 is arranged so that the h portion 3 and the ring portion 4 are not directly connected to ea other by a longitudinal sectional line L2 which intersects with t arm portion 5 in the radial direction of the sprocket 1. In oth words, each arm portion 5 is arranged so that the line extending the radial direction of the sprocket 1 is always crossed with any weight reduction hole 6 over the entire circumference of the sprocket 1. The operation of the sprocket 1 will now be described. Since the center Pl at the distal end and the center P2 at the proximal end of each arm portion 5 are offset at offset angles θl and Θ2 in one circumferential direction relative to each other, and each arm portion 5 is oblique relative to the line in the radial direction of the sprocket, the expansion of the ring portion 4 in the radial direction is absorbed by the elastic deformation of the arm portion 5 as indicated by phantom lines in Fig. 2, whereas the shrinkage of the ring portion 4 in the radial direction is absorbed by the elastic deformation of the arm portion 5 as indicated by phantom lines in Fig. 3. Incidentally, the weight reduction holes 6 serve as spaces for allowing the elastic deformation of each arm portion 5 and are deformed concomitant with the elastic deformation of the arm portion 5. Also, in each portion of the overall length of each arm portions 5, since the longitudinal sectional line L2 will not be connected directly to the hub portion 3 and the ring portion 4, in the expansion or shrinkage of the ring portion 4, the tension stress or compression stress due to the expansion or shrinkage of the ring portion 4 by the expansion of the arm portion 5 is positively prevented from being applied to the hub portion 3, and in addition, the tension stress or shrinkage stress is effectively applied to the arm portion 5 to accelerate the elastic deformation of the arm portion 5 and to furt effectively absorb the tension stress or compression stress to applied to the hub portion 3. Namely, during the manufacture of the sprocket 1, even if t ring portion 4 is shrunk by the heat treatment applied to the too portions 8 and the compression stress Fl in the radial direction applied to the arm portions 5 as shown in Fig. 3, the compressi stress Fl is absorbed by the deformation of the arm portions 5 and t weight reduction holes 6. For this reason, the compression stress applied to the h portion 3 is reduced to thereby prevent the deformation of the h portion 3 toward the center. Even if any mechanical work is n applied thereto after the heat treatment, it is possible to obtai sufficient exactness of a circular property of the engagement hole A modification will now be described in which the structure the above-described sprocket 1 is partially changed so that all t weight reduction holes have the same shape to thereby simplify t punching step. It shouldbe noted that the same reference numerals a used to indicate like members or components and details of t explanation therefor will be omitted. (1) In a sprocket IA as shown in Fig.4, the mounting holes 7 a arranged inside the end portions toward the central side of t weight reduction holes 6A, the centers Pl of the distal end portio and the centers P2 of the proximal end portions of the twelve a portions 5A are offset at a constant angle Θ3 in one circumferenti direction, and the arm portion 5A are provided in curves so that the weight reduction holes 6A are formed to have crescent shape. (2) In a sprocket IB as shown in Fig. 5, expansion portions 9 are formed on the proximal end portions of the eight arm portions 5B, respectively, the centers Pl of the distal end portions and the centers P2 of the proximal end portions of the eight arm portions 5B are offset at a constant angle Θ4 in one circumferential direction, and the mounting holes 7 are formed for every two expansion portions 9 so that the eight weight reduction holes 6B are all formed in the same shape. (3) In a sprocket 1C as shown in Fig. 6, the mounting holes 7 are arranged inside the end portions toward the central side of the weight reduction holes 6C, the centers Pl of the distal end portions and the centers P2 of the proximal end portions of the six arm portions 5C are offset at a constant angle Θ5 in one circumferential direction, and the arm portion 5C are provided in curves so that the weight reduction holes 6A are substantially formed to have boomerang shape. (4) In a sprocket ID as shown in Fig.7, substantiallyboomerang- shaped weight reduction holes 6D are arranged outside the weight reduction holes 6C of the sprocket 1C and the hub portion 3 and the ring portion 4 are connected by arm portions 5D. (5) In a sprocket IE as shown in Fig.8, the mounting holes 7 are arranged inside the end portions toward the central side of the weight reduction holes 6E, the centers Pl of the distal end portions and the centers P2 of the proximal end portions of the twelve a portions 5E are offset at a constant angle Θ6 in one circumferenti direction, and the curved direction of the arm portions 5E ar opposite to the curved direction of the arm portions 5 of the previou embodiment so that a width of the arm portions 5E is graduall increased from the proximal end to the distal end thereof. (6) In a sprocket IF as shown in Fig. 9, the centers Pl of th distal end portions and the centers P2 of the proximal endportions o eight arm portions 5F are offset at a constant angle Θ7 in on circumferential direction, awidth of the proximal endportions of th arm portions 5F is set at a large one, the mounting holes 7 are forme for every two of the eight arm portions 5F so that the mechanica strength of the arm portions 5F is kept at a high level, and the shap of the eight weight reduction holes 6F may be the same. (7) In a sprocket 1G as shown in Fig. 10, the centers Pl of th distal end portions and the centers P2 of the proximal end portions o four arm portions 5G are offset at a constant angle Θ8 in on circumferential direction, awidth of the proximal endportions of th arm portions 5G is set at a large one, the mounting holes 7 are forme at the proximal end portions of the four arm portions 5G so that th mechanical strength of the arm portions 5G is kept at a high level and the shape of the four weight reduction holes 6G may be the same Incidentally, it is possible to set the number of the arms 5, 5 through 5G as desired in response to the size of the sprocket 1, IA t 1G. In the foregoing embodiment, the invention is applied to the sprockets 1, IA to 1G of the torque transmission system of the motorcycle. It is however apparent that the present invention may be applied to any other sprockets of a rotational transmission system than that of the driving torque transmission and also may be applied to a sprocket in a rotation transmission system of equipment or apparatus other than the motorcycle. <Second Embodiment> A second embodiment is directed to a case where the present invention is applied to a brake disc of a braking mechanism in a motorcycle. As shown in Fig.11, a brake disc 10 is externally mounted on and fixed to a wheel hub shaft (not shown) with bolts. The brake disc 11 has a hub portion 13 having an engagement hole 12 through which the automotive axle is caused to pass, an annular braking portion 14 (corresponding to the ring portion) on its outer circumferential side, and a plurality of arm portions 15 each connecting the hub portion 13 and the braking portion 14 at a constant interval along the circumference. The disc brake 10 is integrally formed of a carbon steel plate. It is to be noted that the number of the arm portions 15 may be selected to any one as desired than that shown in the figure. A plurality of slits 16 are formed at a constant interval in order to enhance the braking force. Centers Ql of the outer distal end side of the connecting portions 17 arranged between the slits 16 are arranged to be offset in the circumferential direction by a constant angle o relative to inside centers Q2 of the proximal end Incidentally, instead of the plurality of slits 16, a plurality round holes may be arranged to enhance the braking force. Weight reductionholes 18 andthe armportions 15 are alternate formed between the braking portion 14 and the hub portion 13, and t mounting holes 11 for fastening the brake disc 10 are formed for eve three arm portions 15 at the hub portion 13 in the vicinity of t proximal ends of the arm portions 15. The plurality of arm portions 15 are formed as shown in Fig. 1 and the centers P10 of the distal ends on the braking portion 14 si and the centers Pll of the proximal ends on the hub portion 13 side a repeatedly arranged to be offset at offset angles Θ10, θll and Θ12 this order inone circumferential direction. The centerline LI of ea arm portion 15 is arranged to be obliquely in one direction relati to lines extending radially of the brake disc 10 and intersectingwi the arm portion 15. Also, each arm portion 15 is arranged so that t hub portion 13 and the braking portion 14 are not directly connect to each other by a longitudinal sectional line L2 which intersec with the arm portion 15 in the radial direction of the brake disc at each portion of the entire length of each arm portion 15. The operation of the disc brake 10 will now be described. Since the centers P10 of the distal ends and the centers Pll the proximal ends of the arm portions 15 are repeatedly arranged to offset at offset angles in the order of Θ10, θll and Θ12 in o circumferential direction, and each arm portion 15 is arranged to obliquely in one direction relative to the radial direction of the brake disc 10, the expansion of the braking portion 14 in the radial direction is absorbed by the elastic deformation of the arm portion 15 as indicated by phantom lines in Fig. 12, whereas the shrinkage of the braking portion 14 in the radial direction is absorbed by the elastic deformation of the arm portion 15 as indicated by phantom lines in Fig. 13. Incidentally, the weight reduction holes 18 serve as spaces for allowing the elastic deformation of each arm portion 15 and are deformed concomitant with the elastic deformation of the arm portion 15. Also, in each portion of the entire length of each arm portions 5, since the longitudinal sectional line L2 will not be connected directly to the hub portion 13 and the braking portion 14, in the expansion or shrinkage of the braking portion 14, the tension stress or compression stress due to the expansion or shrinkage of the braking portion 14 by the expansion of the arm portion 15 is positively prevented from being applied to the hub portion 13, and in addition, the tension stress or compression stress is effectively applied to the arm portion 15 to accelerate the elastic deformation of the arm portion 15 and to further effectively absorb the tension stress or compression stress to be applied to the hub portion 13. Namely, even if, during the manufacture of the brake disc 10, the braking portion 14 is shrunk by the heat treatment applied to the braking portion 14 and the compression stress Fll in the radial direction is applied to the arm portions 15 as shown in Fig. 13, the compression stress Fll is absorbed by the deformation of the a portions 15 and the weight reduction holes 18. For this reason, the compression stress applied to the h portion 13 is reduced to thereby prevent the deformation of the h portion 13 toward the center. Even if any mechanical work is no applied thereto after the heat treatment, it is possible to obtain sufficient exactness of a circular property of the engagement hole 12 Also, even if the braking portion 14 is expanded by the hea generation in the braking operation and the tension stress F12 in th radial direction is applied to the arm portions 15 as shown in Fig 12, the tension stress F12 is absorbed by the deformation of the ar portions 15 and the weight reduction holes 18. For this reason, eve if the braking portion and the hub portion are not made of discret members as in the brake disc of the floating disc brake mechanism, i is possible to positively prevent the warpage of the brake disc 10 i the braking operation, and to remarkably reduce the cost of the brak disc 10 while keeping the sufficient performance in the brakin operation. Incidentally, in a modification of the second embodiment, it i possible to set the oblique directions of the connecting portion 1 and the arm portion 15 in the opposite direction in a brake disc 10 as shown in Fig. 14. Also, it is possible to adopt the arm portions 1 and the weight reduction holes as shown in the above-describe sprockets 1, IA to 1G for the arm portions 15 and the weight reductio holes 18. Incidentally, in the first and second embodiments, the present invention has been applied to the sprockets and the brake discs. However, the present invention may be equally applied to a clutch disc or the like a rotary member for transmitting the braking force and drive force. With the rotary member for transmitting the driving torque or braking force according to the present invention, it is possible to effectively absorb the expansion or shrinkage of the ring member and to prevent the warpage of the rotary member or deformation of the inner circumferential surface of the hub portion without increasing the number of the components with a simple structure in which the shapes of the armportions and the weight reduction holes are changed. Also, if the centers of the distal end portions of the plurality of arm portions and the centers of the proximal ends thereof are offset in one circumferential direction, respectively, with a constant regularity, the expansion or shrinkage of the ring portions may be absorbed with a good balance by the plurality of arm portions, and it is possible to further effectively absorb the warpage of the rotary member or deformation of the inner circumferential surface of the hub portion. For this reason, if this rotary member is applied to the sprocket, the shrinkage of the ring portion due to the annealing treatment to the tooth portions is effectively absorbed and the deformation of the inner circumferential surface of the hub may be prevented. The machine work to the inner circumferential surface of the hub portion after the annealing treatment may be dispensed wi and the sprocket manufacturing step may be simplified. In additio since the sprocket is composed of a single member, its manufacturi cost is less expensive. Also, if the rotary member is applied to the brake disc, in t case way as in the case of the sprocket, the shrinkage of the ri portion due to the annealing treatment to the braking portions effectively absorbed and the deformation of the inner circumferenti surface of the hub may be prevented. The machine work to the inn circumferential surface of the hub portion may be dispensed with a the brake disc manufacturing stepmaybe simplified. In addition, al in the case where the ring portion is expanded due to the he generation during the braking operation, this expansion effectively absorbedby the armportions. Accordingly, it is possib to effectively prevent the generation of the warpage even in the bra disc made of a single member and to enhance the performance of t brake discwhile considerably reducing themanufacturingcost there without such a structure that the braking portion and the hub porti are made of discrete members like the brake disc of the floating di brake mechanism.

Claims: CLAIMS 1. A rotary member for transmitting a drive force or brake force, said rotary member comprising an annular hub portion arranged on a center side, an annular ring portion arranged on an outer circumferential side, and a plurality of arm portions connecting the hub portion and the ring portion, with a plurality of weight reduction holes partitioned by the arm portions between the hub portion and the ring portion, wherein said plurality of arm portions are provided so that centers of their distal end portions on the ring portion side and centers of their proximal end portions on the hub portion side are offset in one circumferential direction, respectively, and said hub portion and said ringportion are not directly connected to each other by longitudinal sectional lines that intersect with the arm portions in a radial direction of said rotary member. 2. The rotary member according to claim 1, wherein the centers of their distal end portions on the ring portion side and the centers of their proximal end portions on the hub portion side are offset in one circumferential direction with a constant regularity, respectively. 3. The rotary member according to claim 1, wherein said rotary member is a sprocket having a plurality of teeth along an outer circumferential portion of said ring portion. 4. The rotary member according to claim 2, wherein said rotary member is a sprocket having a plurality of teeth along an outer circumferential portion of said ring portion. 5. The rotary member according to claim 1, wherein said rot member is a brake disc having a braking portion on said ring portio 6. The rotary member according to claim 2, wherein said rot member is a brake disc having a braking portion on said ring porti

Inventors: METSUGI FUMIHIKO, OHATA AKIHITO, TAKAMORI NORIHIKO, METSUGI, FUMIHIKO, OHATA, AKIHITO, TAKAMORI, NORIHIKO
Applicants: METSUGI FUMIHIKO, OHATA AKIHITO, SUNSTAR ENGINEERING INC, TAKAMORI NORIHIKO, METSUGI, FUMIHIKO, OHATA, AKIHITO, SUNSTAR ENGINEERING INC., TAKAMORI, NORIHIKO
Application year: 1996
Main classification: F16H55
IPC codes: F16D65, F16D69, F16H55