Title of Invention	"DRIVEN PULLEY DEVICE OF V-BELT TYPE AUTOMATIC TRANSMISSION"
Abstract	A driven pulley device of a V-belt type automatic transmission comprising an inner cylinder (87) and an outer cylinder (88) slidably fitted to each other while their relative rotation around an axis line and their relative motion in an axial direction can be applied; a fixed half-pulley member (89) fixed to said inner cylinder (87); a movable half- pulley member (90) fixed to said outer cylinder (88) in opposition to said fixed half-pulley member (89);a torque cam mechanism (91) arranged between said inner cylinder (87) and said outer cylinder (88) so as to cause an axial partial force to act between said both half-pulley members in response to relative rotational phase difference between said movable half- pulley member ( 90) and said fixed half-pulley member (89); a spring receiving member (92) fixed to said inner cylinder (87) at a position where said movable half- pulley member (90) is held between it and said fixed half- pulley member (89); and a coil spring (93) enclosing said outer cylinder (88), shrunk and arranged between said movable half- pulley member (90) and said spring receiving member (92), a V-belt (80) for transmitting a rotational driving force from a driving pulley (78) being held between oppositely facing conical surfaces (89a, 90a) of said fixed half- pulley member (89) and said movable half-pulley member (90), characterized in that the same further comprises a guide member (106) for guiding at least the inner circumference of said coil spring (93) at said movable half- pulley member (90); and a thrust bearing means (107) placed between said spring (93). Fig: 6

Title of Invention

"DRIVEN PULLEY DEVICE OF V-BELT TYPE AUTOMATIC TRANSMISSION"

Abstract

A driven pulley device of a V-belt type automatic transmission comprising an inner cylinder (87) and an outer cylinder (88) slidably fitted to each other while their relative rotation around an axis line and their relative motion in an axial direction can be applied; a fixed half-pulley member (89) fixed to said inner cylinder (87); a movable half- pulley member (90) fixed to said outer cylinder (88) in opposition to said fixed half-pulley member (89);a torque cam mechanism (91) arranged between said inner cylinder (87) and said outer cylinder (88) so as to cause an axial partial force to act between said both half-pulley members in response to relative rotational phase difference between said movable half- pulley member ( 90) and said fixed half-pulley member (89); a spring receiving member (92) fixed to said inner cylinder (87) at a position where said movable half- pulley member (90) is held between it and said fixed half- pulley member (89); and a coil spring (93) enclosing said outer cylinder (88), shrunk and arranged between said movable half- pulley member (90) and said spring receiving member (92), a V-belt (80) for transmitting a rotational driving force from a driving pulley (78) being held between oppositely facing conical surfaces (89a, 90a) of said fixed half- pulley member (89) and said movable half-pulley member (90), characterized in that the same further comprises a guide member (106) for guiding at least the inner circumference of said coil spring (93) at said movable half- pulley member (90); and a thrust bearing means (107) placed between said spring (93). Fig: 6

Full Text	[Technical Field] [0001] This invention relates to a driven pulley device of a V-belt type automatic transmission comprising an inner cylinder and an outer cylinder slidably fitted to each other while their relative rotation around an axis line and their relative motion in an axial direction can be applied, a fixed half-pulley member fixed to the inner cylinder, a movable half-pulley member fixed to the outer cylinder in opposition to the fixed half-pulley member, a torque cam mechanism arranged between the inner cylinder and the outer cylinder so as to cause an axial partial force to act between both the half-pulley members in response to a relative rotational phase difference between the movable half-pulley member and the fixed half-pulley member, a spring receiving member fixed to the inner cylinder at a position where the movable half-pulley member is held between it and the fixed half-pulley member, and a coil spring enclosing the outer cylinder, shrunk and arranged between the movable half-pulley member and the spring receiving member, and a V-belt for transmitting a rotational driving force from a driving pulley device is held between oppositely facing conical surfaces of the fixed half-pulley member and the movable half-pulley member. [Background Art] [0002] A certain twisting can be generated at the coil spring shrunk and arranged between the movable pulley and the spring receiving member because the torque cam mechanism in such a driven pulley device as described above causes an axial force to act against the movable pulley in response to a relative rotational phase difference between the movable half-pulley member and the fixed half-pulley member. Such a twisting as above generates a reaction force against the axial force and causes a pressing force of the movable half-pulley member against the side face of the V-belt to be unstable and further this situation becomes a cause for generating vibration. In view of this fact, the invention disclosed in the patent document 1 prevents the coil spring from being twisted by arranging a plate-like bearing in at least one of one place between the movable half-pulley member and the coil spring and the other place between the spring receiving member and the coil spring. [Patent Document 1] JP-A No. 42655/1996 [Disclosure of the Invention] [Problem to be Solved by the Invention] [0003] However, the coil spring is not only easily twisted as described above, but also a wavy phenomenon is easily generated at the cylindrical surface by a partial eccentric state, and occurrence of the pulsation phenomenon can cause the coil spring to strike against its surrounding member to generate irregular sound. The aforesaid prior art system cannot prevent any occurrence of the pulsation phenomenon at the coil spring. [0004] The present invention has been invented in view of such circumstances as described above, and it is an object of the present invention to provide a driven pulley device of a V-belt type automatic transmission capable of not only preventing any twisting a the coil spring, but also preventing occurrence of any pulsation phenomenon. [Means for Solving the Problem] [0005] In order to solve the aforementioned problem, the first characteristic of the present invention is to provide a driven pulley device of V-belt type automatic transmission comprising an inner cylinder and an outer cylinder slidably fitted to each other while their relative rotation around an axis line and their relative motion in an axial direction can be applied, a fixed half-pulley member fixed to the inner cylinder, a movable half-pulley member fixed to the outer cylinder in opposition to the fixed half-pulley member, a torque cam mechanism arranged between the inner cylinder and the outer cylinder so as to cause an axial partial force to act between both the half-pulley members in response to a relative rotational phase difference between the movable half-pulley member and the fixed half-pulley member, a spring receiving member fixed to the inner cylinder at a position where the movable half-pulley member is held between it and the fixed half-pulley member, and a coil spring enclosing the outer cylinder, shrunk and arranged between the movable half-pulley member and the spring receiving. member, and a V-belt for transmitting a rotational driving force from a driving pulley device is held between oppositely facing conical surfaces of the fixed half-pulley member and the movable half-pulley member characterized in that the same comprises a guide member for guiding at least the inner circumference of the coil spring at the movable half-pulley member, and a thrust bearing means placed between the spring receiving member and the coil spring. [0006] The second characteristic of the present invention is that the thrust bearing means is made such that a pair of bearing members made of self-lubricating resin and overlapped to each other is held between the coil spring and the spring receiving member. [0007] The third characteristic of the present invention is that the guide member is formed by self-lubricating resin. [0008] Further, the fourth characteristic of the present invention is that a metallic collar is installed among the movable half-pulley member, the outer cylinder and the guide member for receiving an end face of the coil spring at the movable half-pulley member. [Effect of the Invention] [0009] According to the first characteristic, it is possible to rotate the coil spring together with the movable half-pulley member without producing any relative rotation in respect to the movable half-pulley member by arranging the thrust bearing means between the spring receiving member and the coil spring when a relative rotational phase difference occurs between the movable half-pulley member and the fixed half-pulley member and then it is possible to prevent the coil spring from being twisted. Further, it is possible to set the inner circumference of the coil spring at the movable half-pulley member at its center location and prevent a pulsation phenomenon from being generated at the coil spring because the inner circumference of the coil spring is guided by the guide member at the movable half-pulley member. In particular, an amount of work of the half-pulley member at the movable half-pulley member in the coil spring becomes relatively high in response to an axial motion of the movable half-pulley member and the inner circumference at the side where the amount of work is increased is guided by the guide member, so that the pulsation phenomenon can be effectively prevented. [0010] In addition, according to the second characteristic, the thrust bearing means can be constituted by a quite simple structure and both bearing members have a self-lubricating characteristic, so that it is possible to improve an anti-wearing characteristic against dusts. [0011] According to the third characteristic, a sliding action between the inner circumference of the coil spring at the movable half-pulley member and the guide member can be improved, a clearance between the coil spring and the guide member can be set low as much as possible, thereby a pulsation phenomenon at the coil spring can be prevented more effectively and then a workability characteristic can be improved. [0012] Further, according to the fourth characteristic, it is possible to set a thin thickness of the guide member, facilitate controlling over a clearance between the guide member made of resin and the inner circumference of the coil spring accompanied by a thermal expansion of the guide member, keep a difference in its friction coefficient in regard to that of the spring receiving member and generate a more positive relative rotation between the coil spring and the spring receiving member. [Best Mode for Carrying Out the Invention] [0013] A preferred embodiment of the present invention will be described as follows in reference to one preferred embodiment of the present invention shown in the accompanying drawings. [Brief Description of the Drawings] [0065] [Fig. 1] This is a side elevational view for showing a power unit and a rear wheel. [Fig. 2] This is a sectional view taken along line 2-2 of Fig. 1. [Fig. 3] This is a substantial part enlarged view of Fig. 2. [Fig. 4] This is a sectional view taken along line 4-4 of Fig. 3. [Fig. 5] This is a sectional view taken along line 5-5 of Fig. 3. [Fig. 6] This is an enlarged cross sectional view of a driven pulley^ device. [Fig. 7] This figure shows a case cover and a sound-proof cover from an arrow direction taken along line 7-7 of Fig. 2. [Fig. 8] This figure shows a case cover and a sound-proof cover from an arrow direction taken along line 8-8 of Fig. 2. [Fig. 9] This figure shows a test result of a noise generated state. - [0014] Figs. 1 to 9 illustrate one preferred embodiment of the present invention, Fig. i is a side elevational view for showing a power unit and a rear wheel, Fig. 2 is a sectional view taken along line 2-2 of Fig. i, Fig. 3 is a substantial part enlarged view of Fig. 2, Fig. 4 is a sectional view taken along line 4-4 of Fig. 3, Fig. 5 is a sectional view taken along line 5-5 of Fig. 3, Fig. 6 is an enlarged cross sectional view of a driven pulley device, Fig. 7 shows a case cover and a sound-proof cover from an arrow direction taken along line 7-7 of Fig. 2, Fig. 8 shows a case cover and a sound-proof cover from an arrow direction taken along line 8-8 of Fig. 2, and Fig. 9 shows a test result of a noise generated state. [0015] At first, in Figs. 1 and 2, a power unit P constituted by an engine E arranged at a forward part of a rear wheel WR and a V-belt type automatic transmission M installed between the engine E and the rear wheel WR is mounted on a chassis frame (not shown) of a scooter type motorcycle, and the rear wheel WR arranged at the rear right portion of the power unit P is pivotally supported at the rear part of the power unit P. [0016] An engine main body 11 of the engine E comprises a crank case 12 for rotatably supporting a crank shaft 16 having a rotating axis line in parallel with a rotating axis line of the rear wheel WR, a cylinder block 13 connected to the crank case 12, a cylinder head 14 connected to the cylinder block 13 at a side opposite to the crank case 12 and a head cover 15 connected to the cylinder head 14 at a side opposite to the cylinder block 13. [0017] The cylinder block 13 is arranged such that an axis line of the cylinder bore 17 set at the cylinder block 13, i.e. a cylinder axis line C1 is slightly raised at a front part along a forward or rearward direction of the motorcycle and becomes substantially to occupy a horizontal state. In addition, the crank case 12 comprises a pair of case half members 12a, 12b also including the cylinder axis line C1 and connected at a plane crossing at a right angle with an axis line of the crank shaft 16, a ball bearing 18 is installed between one case half member 12a of one of both case half members 12a, 12b and the crank shaft 16, and further a roller bearing 19 and an annular seal member 20 arranged more outside than that of the roller bearing 19 are installed between the other case half member 12b and the crank shaft 16. [0018] A combustion chamber 23 is formed between the cylinder head 14 and a piston 21 slidably fitted in the cylinder bore 17 . An intake valve 24 for controlling intake gas fed into the combustion chamber 23 and an exhaust valve 25 for controlling exhaust gas discharged out of the combustion chamber 23 are arranged at the cylinder head 14 in such a way that they may be arranged in a substantial V-shape on a projected figure for a top plan surface crossing at a right angle with the rotating axis line of the crank shaft 16. A spark plug 26 adjacent to the combustion chamber 23 is fixed to the side face of the cylinder head 14 in a state where it is faced in a forwarding direction of the motorcycle. [0019] Between the cylinder head 14 and the head cover 15 is stored a valve train 30 having an axis line in parallel with an axis line of the crank shaft 16, rotatably supported at the cylinder head 14 and including a cam shaft 27 having an intake cam 28 and an exhaust cam 29 so as to drive to open or close the intake valve 24 and exhaust valve 25. [0020] To one end of the cam shaft 27 is fixed a driven sprocket 31. In turn, the first driving sprocket 32 is fixed at such a position as one corresponding to the driven sprocket 31 at a more outside than that of the ball bearing 18 at the shaft 16. An endless cam chain 33 is wound around the first driving sprocket 32 and the driven sprocket 31. The cam chain 33 is stored in a chain chamber 34 formed over the cylinder block 13, cylinder head 14 and head cover 15 in such a way that the cam chain can run there. The cam shaft 27 is rotationally driven under the number of rotation of 1/2 of that of the crank shaft 16 by the first driving sprocket 32, the driven sprocket 31 and the cam chain 33. [0021] Referring now also to Fig. 3, the crank shaft 16 is provided with a pair of crank webs 16a, 16b oppositely faced to each other while being axially spaced apart, and both ends of the crank pin 37 are connected to these crank webs 16a, 16b. In turn, one end of a connecting rod 38 is connected to the piston 21, and the other end of this connecting rod 38, i.e. a large end 38 is connected to the above-mentioned crank pin 37 through a needle bearing 39. [0022] The second driving sprocket 40 is fixed to the crank shaft 16 at a more outside part than that of the first driving sprocket 31. In turn, an oil pump 41 (refer to Fig. 1) for use in sucking up oil from the lower portion at the crank case 12 and a cooling water pump 42 (refer to Fig. 1) for use in circulating cooling water to a cooling jacket 43 arranged at the cylinder block 13 and the cylinder head 14 are coaxially arranged at the lower portion of the crank case 12 and then a rotating force is transmitted from the second driving sprocket 40 to the oil pump 41 and the cooling water pump 42 through the chain 44. [0023] At a more outside location than that of the second driving sprocket 40, there is provided a generator 46 comprising a stator 47 fixed to a right cover 45 attached to the right side face of the crank case 12 and an outer rotor 48 fixed to the crank shaft 16 so as to enclose the stator 47. [0024] A driven gear 49 coaxially enclosing the crank shaft 16 and supported by the crank shaft 16 in such a manner that it can be rotated relatively is arranged between the second driving sprocket 40 and the outer rotor 48, and this driven gear 49 is connected to the outer rotor 48 through one-way clutch 50. In this way, a rotational driving force provided by a starter motor not shown can be inputted to the driven gear 49 and when the engine E starts to operate, a driving force from the crank shaft 16 is not transmitted to the starter motor from the starter motor is transmitted to the crank shaft 16 and the driving force from under an action of the one-way clutch 50 after the engine E starts to operate. [0025] A cylindrical supporting cylinder 45a enclosing the right end of the crank case 12 is integrally protruded at the central part of an inner surface of the right cover 45, an annular seal member 53 is arranged between the supporting cylinder 45a and the crank shaft 16, an oil chamber 54 into which the right end of the crank shaft 16 protrudes is formed at the central part of an inner surface of the right cover 45, and an oil passage 55 arranged at both crank case 12 and right cover 45 is communicated with this oil chamber 54 in such a way that oil from the oil pump 41 may be guided. [0026] The crank shaft 16 has coaxially the first oil passage hole 56 with a bottom part having its outer end communicated with the oil chamber 54 in such a way that its inner end is closed at a position substantially corresponding to the ball bearing 18. In addition, the crank pin 37 has coaxially the second oil passage hole 57 with a bottom part released to the ball bearing 18 for its light weight formation and supplying oil. In turn, the outer surface of one crank web 16a of the crank shaft 16 facing against the ball bearing 18 is formed with an annular fixing concave part 58 adjacent to an opening end of the second oil passage hole 57, and the outer circumference of an annular oil delivering plate 59 formed like a dish shape is press fitted and fixed against the fixing concave part 58 so as to cover the opening end of the second oil passage hole 57. [0027] In addition, the crank shaft 16 has the first communication hole 60 punched to cause the oil from the first oil passage hole 56 to be fed between the oil delivering plate 59 and the crank web 16a. Further, the crank pin 37 is provided with the second communication hole 61 for feeding the oil in the second oil passage hole 57 to the needle bearing 39. [0028] Accordingly, the oil fed from the oil pump 41 to the oil chamber 54 through the oil passage 55 is supplied to the needle bearing 39 through the first oil passage hole 56, first communication hole 60, between the oil delivering plate 59 and the crank web 16a, second oil passage hole 57 and second communication hole 61. In addition, the crank shaft 16 is also provided with the third communication hole 62 for use in feeding the oil from the first oil passage hole 56 to between the crank shaft 16 and the driven gear 49. [0029] Although the oil supplied to the needle bearing 3 9 is used for applying a lubrication between the large end part 38a of the connecting rod 38 and the crank pin 37, the oil splashes as the crank shaft 16 is rotated, the oil hole 63 for use in feeding a part of the splashed oil to the roller bearing 19 has an axis line in parallel with the axis line of the crank shaft 16 and is arranged at the other crank web 16b. [0030] Also referring to Fig. 4, the other aforesaid crank web 16b is provided with a weight part 16ba at a side opposite to a connected part of the crank pin 37 in regard to the axis line C2 of the crank shaft 16. The inner surface of this crank web 16b comprises an arcuate higher level surface 64 corresponding to the weight part 16ba, a middle level surface 65 extending in parallel with a straight line L passing through an axis line of the crank pin 37 and through an axis line C2 of the crank shaft 16 and further extending in a band-like manner between the connected part of the crank pin 37 and the weight part 16ba, and another low level surface 66. The middle level surface 65 forms a step part 67 between it and the low level surface 66 and is formed to be slightly more inwardly protruded than that of the low level surface 66. The higher level surface 64 forms a step part 68 between the low level surface 66 and the middle level surface 65 and is formed to be protruded more inwardly than that of the middle level surface 65. [0031] Thus, one end of the oil hole 63 is opened at the low level surface 66 near a location where both the steps 67, 68 are curved and connected to each other, oil splashed from the needle bearing 39 is transmitted along the steps 67, 68 and easily guided to one end of the oil hole 63. [0032] Also referring to Fig. 5, the outer surface of the other aforesaid crank web 16b oppositely facing against the roller bearing 19 is provided with a cavity 69 formed in an arcuate manner substantially corresponding to the roller bearing 19, and the other end of the oil hole 63 is opened at the cavity 69. Thus, oil fed from the oil hole 63 is easily accumulated at the cavity 69 and splashed from the cavity 69 to the roller bearing 19, thereby oil can be supplied to the roller bearing 19. [0033] Referring again to Fig. 2, the V-belt type automatic transmission M is stored in a storing chamber 70 in a transmission case 71 covering a part of the engine main body 11 from its side part to be cooperatively arranged at the engine main body 11 and extending to the left side of the rear wheel WR. The transmission case 71 comprises an inner case 72 integrally cooperated with the other case half member 12b of a pair of case half members 12a, 12b constituting the crank case 12, an outer case 73 fastened to the inner case 72 so as to cover the inner case 72 from outside and a gear reducer case 74 fastened to the rear part of the inner case 72 within the outer case 73. The storing chamber 70 is formed among the inner case 72, gear reducer case 74 and outer case 73, and a gear chamber 75 is formed between the inner case 72 and the gear reducer case 74. [0034] The V-belt type automatic transmission M comprises a driving pulley device 78 installed at the other end of the crank shaft 16 protruded from the crank case 12 into the storing chamber 70, a driven pulley device 79 having an axis line in parallel with the crank shaft 16 and installed at an output shaft 81 rotatably supported by an inner case 72 and a gear reducer case 74, and an endless V-belt 80 for transmitting a driving power from the driving pulley device 78 to the driven pulley device 79. [0035] The driving pulley device 78 comprises a fixed half-pulley member 81 fixed to the crank shaft 16, a movable half-pulley member 82 that can approach to or spaced apart from the fixed half-pulley member 81 and a centrifugal weight 83 moved in a radial outward direction in response to an increasing in the number of rotation of the crank shaft 16. The movable half-pulley member 82 is biased in such a direction as one in which it approaches to the fixed half-pulley member 81 while the centrifugal weight 83 moves in a radial outward direction in response to an increasing in the number of rotation of the crank shaft 16. [0036] In Fig. 6, the driven pulley device 79 comprises an inner cylinder 87 coaxially enclosing an output shaft 81 while installing a needle bearing 85 and a ball bearing 86 between it and the output shaft 81, an outer cylinder 88 enabling a relative rotation around an axis line and a relative motion in an axial direction and fitting the inner cylinder 87 in a slidable manner, a fixed half-pulley member 89 fixed to the inner cylinder 87, a movable half-pulley member 90 fixed to the outer cylinder 88 while being oppositely faced against the fixed half-pulley member 89, a torque cam mechanism 91 arranged between the inner cylinder 87 and the outer cylinder 88 while a partial force in an axial direction being applied between both half-pulley members 89, 90 in response to a relative rotational phase difference between the movable half-pulley member 90 and the fixed half-pulley member 89, a spring receiving member 92 fixed to the inner cylinder 87 at a position where the movable half-pulley member 90 is held between it and the fixed half-pulley member 89, a coil spring 93 enclosing the outer cylinder 88, shrunk and arranged between the movable half-pulley member 90 and the spring receiving member 92, and a centrifugal clutch 94 arranged between the inner cylinder 87 and the output shaft 81 while a power transmitting state is attained as the number of rotation of the engine exceeds a predetermined number of rotation. [0037] Then, the V-belt 80 is held between the oppositely facing conical surfaces 81a, 82a of the fixed half-pulley member 81 and the movable half-pulley member 82 at the driving pulley device 78 and between the oppositely facing conical surfaces 89a, 90a of the movable half-pulley member 90 at the driven pulley device 79. At the driving pulley device 78, a winding radius of the V-belt 80 to the fixed and movable half-pulley members 81, 82 is increased as the movable half-pulley member 82 approaches to the fixed half-pulley member 81 in response to an increasing in the number of rotation of the crank shaft 16, and correspondingly at the driven pulley device 79, a winding radius of the V-belt 80 to the fixed and movable half-pulley members 89, 90 is decreased. [0038] The fixed half-pulley member 89 is fixed to one end of the inner cylinder 87 with plural rivets 95 . . . and the spring receiving member 92 is fixed to the other end of the inner cylinder 87. Thus, the spring receiving member 92 also constitutes a part of the centrifugal clutch 94 . The centrifugal clutch 94 comprises a cup-like clutch outer 96 fixed to the other end of the output shaft 81, centrifugal weights 97 ... enabled to be turned around an axis line in parallel with the output shaft 81 and pivotally supported at plural locations of the spring receiving member 92 and clutch springs 98 ... arranged between each of the centrifugal weights 97 ... and the spring receiving members 92. The inner cylinder 87, i.e. the fixed half-pulley member 89 and the clutch outer 96, i.e. the output shaft 81 are connected to each other by frictionally engaging the centrifugal weights 97 ... with the clutch outer 96 when the centrifugal force acting on each of the centrifugal weights 97 ... in response to a rotation of the spring receiving member 92 exceeds a spring biasing force of each of the clutch springs 98 .... [0039] The movable half-pulley member 90 is fixed to one end of the outer cylinder 88 with plural rivets 102, ... so as to be oppositely faced against the fixed half-pulley member 89. In addition, the torque cam mechanism 91 is a well-known prior art mechanism comprising cam holes 103 . . . arranged at plural locations of the outer cylinder 88, cam pins 104 . . . implanted into the inner cylinder 87 while being inserted into these cam holes 103 ... and rollers 105 ... pivotally supported at the cam pins 104 ... rolled in the cam holes 103 .... [0040] Thus, a clearance between the fixed half-pulley member 89 at the driven pulley device 79 and the movable half-pulley member 90 is determined by a balance among an axial force generated by the torque cam mechanism 91, an axial resilient force generated by the coil spring 93 and a force from the V-belt 80 acted in such a direction as one spaced by the clearance between the fixed half-pulley member 89 and the movable half-pulley member 90. [0041] The inner circumference of the coil spring 93 at the movable half-pulley member 90 is guided by the guide member 106, and a thrust bearing means 107 is arranged between the spring receiving member 92 and the coil spring 93. [0042] The guide member 106 has at its one end a flange 106a for receiving one end of the coil spring 93 facing at the movable half-pulley member 90 and is formed into a cylindrical shape by self-lubricating resin. One end of the coil spring 93 is received by the flange 106a of the guide member 106 and further the inner circumference of the coil spring 93 at the movable half-pulley member 90 is guided by the guide member 106. In addition, the guide member 106 is provided with plural slits 108 . . . extending from its one end to the other end and plural slits 109 ... extending from the other end to one end. [0043] In addition, among the movable half-pulley member 90, the outer cylinder 88 and the guide member 106 having the flange 106a is present a metallic collar 110 receiving a flange 106a of the guide member 106, inserting one end of the coil spring 93, having integrally at one end a receiving part 110a formed into a substantial L-shape in its longitudinal section and formed into a cylindrical shape. This collar 110 coaxially encloses the outer cylinder 88 while closing from outside the cam holes 103 ... arranged in the outer cylinder 88. [0044] In regard to this arrangement, grease is filled in each of the cam holes 103 ... and an annular chamber 111 formed between the output shaft 81 and the inner cylinder 87 between the needle bearing 85 and the ball bearing 86 . The inner cylinder 87 is provided with communication holes 112 ... connecting between the annular chamber 111 and each of the cam holes 103 . . . . Annular seal members 113, 113 resiliently contacted with the inner circumference of the collar 110 are installed at both outer circumferential ends in an axial direction of the outer cylinder 88, and the annular seal members 114, 114 slidably contacting with the outer circumference of the inner cylinder 87 are installed at both inner circumferential ends of the outer cylinder 88 in an axial direction. [0045] The thrust bearing means 107 is made such that a pair of bearing members 115, 116 made of self-lubricating resin and overlapped to each other are held between the coil spring 93 and the spring receiving member 92, wherein one bearing member 115 has integrally a fitted cylindrical part 115a fitted to a circular cavity 117 arranged at the spring receiving member 92 and a flat plate ring-like bearing 115b contacted with a closing end of the cavity 117, and the other bearing member 116 is provided with a flat plate ring-like bearing 116a held between the bearing 115b and the coil spring 93, and a position setting cylinder 116b integrally cooperated at the inner circumference of the bearing 116a while its relative position with the coil spring 93 is defined by being inserted into the inner circumference at the other end of the coil spring 93. [0046] Further, referring again to Fig. 2, a wheel shaft 118 of the rear wheel WR is rotatably supported at the gear reducer case 74 and the inner case 72, and the end part of the wheel shaft 118 protruded from the transmission case 71 is rotatably supported at an arm 119 connected to the engine main body 11 and arranged at the right side of the rear wheel WR. [0047] A row of reduction gears 120 arranged between the output shaft 81 and the wheel shaft 118 is stored in the gear chamber 75, and the row of reduction gears 120 comprises the first gear 121 arranged at the output shaft 81, the second gear 123 arranged at an intermediate shaft 122 in parallel with the output shaft 81 and the wheel shaft 118 and rotatably supported at the inner case 72 and the gear reducer case 74 and engaged with the first gear 121, the third gear 124 arranged at the intermediate shaft 122 and the fourth gear 125 engaged with the third gear 124 and arranged at the wheel shaft 118. [0048] The side wall of the outer case 73 at the transmission case 71 opposing against the driving pulley device 78 is provided with a surrounding air intake port 126 for use in taking cooling air into the storing chamber 70, and a cooling fan 127 for dispersing the cooling air taken at the surrounding air intake port 126 into the storing chamber 70 is integrally-arranged at the outer circumference of the movable half-pulley member 90 at the driving pulley device 78. [0049] Also referring to Fig. 7, the outer surface of the transmission case 71 is covered by the case cover 128 and the sound-proof cover 129. The case cover 128 includes a portion where the surrounding air intake port 126 is arranged and is fastened to the outer case 73 at the transmission case 71 at plural locations there while covering the outer surface of the front half part of the transmission case 71. The sound-proof cover 129 is fastened to the outer case 73 at the transmission case 71 at plural locations so as to cover the outer surface of the rear half part of the transmission case 71 at a side corresponding to the driven pulley device 79. [0050] The case cover 128 and the sound-proof cover 129 are fixed to the transmission case 71 so as to cover the front edge of the sound-proof cover 129 at the rear edge of the case cover 128, two hubs 129a ... arranged at the front part of the sound-proof cover 129 are held between the rear part of the case cover 128 and the transmission case 71, and the rear part of the case cover 128 and the front part of the sound-proof cover 129 are fastened together to the transmission case 71 by the screw members 13 0 .... [0051] Further, an intake port 131 opened at a rear side is formed between the rear edge of the case cover 128 and the front edge of the sound-proof cover 129, and an air feeding chamber 132 communicated with the intake port 131 is formed between the case cover 128 and the transmission case 71. [0052] A filter 133 is fixed to the outer surface of the transmission case 71 so as to close the surrounding air intake port 126 from the side of the air feeding chamber 132, the surrounding air fed from the intake port 131 to the air feeding chamber 132 passes through the filter 133 to be purified and then sucked into the storing chamber 70. [0053] Referring also to Fig. 8, between the transmission case 71 and the sound-proof cover 129 are arranged four sound-proof members 137, 138, 139 and 140, for example, so as to define a space between the transmission case 71 and the sound-proof cover 129 into plural closed spaces, for example, three closed spaces 134, 135 and 136. [0054] Each of the sound-proof members 137 to 140 is formed into a stripe shape by cutting and forming a urethane sheet, respectively, and a surface of each of these sound-proof members 137 to 140 is adhered to any one of the transmission case 71 and the sound-proof cover 129 with adhesive agent, to the inner surface of the sound-proof cover 129 in this preferred embodiment. [0055] Then, an action of the preferred embodiment will be described as follows. At least, the inner circumference of the coil spring 93 is guided by a guide member 106 at the movable half-pulley member 90 in the driven pulley device 79 of the V-belt type automatic transmission M and the thrust bearing means 107 is present between the spring receiving member 92 and the coil spring 93, so that it is possible to rotate the coil spring 93 together with the movable half-pulley member 90 so as to prevent a relative rotation in respect to the movable half-pulley member 90, and further it is also possible to prevent the coil spring 93 from being twisted. Further, the inner circumference of the coil spring 93 at the movable half-pulley member 90 is guided by the guide member 106, so that it is possible to prevent the coil spring 93 from generating a pulsation phenomenon while a centering state of the inner circumference of the coil spring 93 is attained at the inner circumference of the coil spring 93. [0056] In particular, an amount of work of the half-part of the movable half-pulley member 90 in the coil spring 93 becomes relatively high in response to an axial motion of the movable half-pulley member 90 and the inner circumference of the side where the amount of work becomes high is guided by the guide member 106, so that occurrence of corrugation state can be prevented more effectively. [0057] In addition, the thrust bearing means 107 is made such that a pair of bearing members 115, 116 overlapped to each other are held between the coil spring 93 and the spring receiving member 92 and the thrust bearing means 107 can be constituted by a quite simple structure and further both bearing members 115, 116 are made of self-lubricating resin, so that an anti-wearing characteristic against dust can be improved even if cooling air fed into the storing chamber 70 contains dusts. [0058] In addition, the guide member 106 is also formed by the self-lubricating resin, thereby a sliding between the inner circumference of the coil spring 93 and the guide member 106 at the movable half-pulley member 90 can be improved. As a result, it becomes possible to set a clearance between the coil spring 93 and the guide member 106 as less as possible, occurrence of pulsation phenomenon generated at the coil spring 93 can be prevented as more effectively as possible and its workability can be improved. [0059] Further, since the metallic collar 110 is arranged among the movable half-pulley member 90, outer cylinder 88 and the guide member 106 receiving the end face of the coil spring 93 at the movable half-pulley member 90, a thickness of the guide member 106 can be set thin to facilitate a management over a clearance between it and the inner circumference of the coil spring 93 as the resin-made guide member 106 is thermally expanded, and additionally, it is possible to maintain a difference of frictional coefficient between it and the spring receiving member 92 and generate a more positive relative rotation between the coil spring 93 and the spring receiving member 92. [0060] Additionally, a space between the transmission case 71 and the sound-proof cover 129 covering the outer surface of the transmission case 71 and fixed to the transmission case 71 is defined into plural closed spaces 134 to 136 by the sound-proof members 137 to 140. Therefore, noise produced from the transmission case 71 is absorbed and restricted by the sound-proof members 137 to 140 arranged between the transmission case 71 and the sound-proof cover 129, and at the same time the noise is restricted by a sound resonance prevented from being generated by the plurality of closed spaces 134 to 136 formed between the transmission case 71 and the sound-proof cover 129. Accordingly, it is possible to attain a sufficient noise preventing effect with a simple structure in which a space between the transmission case 71 and the sound-proof cover 129 is defined into plural closed spaces 134 to 136 by the sound-proof members 137 to 140. [0061] In regard to this point, it is apparent that, under an assumption that a state having no sound-absorbing member between the sound-proof cover 129 and the transmission case 71 is defined as A, a state having sound-absorbing member over a front surface between the sound-proof cover 129 and the transmission case 71 is defined as B, and a state having a space between the sound-proof cover 129 and the transmission case 71 divided into plural closed spaces 134 to 136 by the sound-proof members 137 to 140 according to the present invention is defined as C, a test for checking an occurrence of noise at the time of acceleration of the motorcycle at each of the states A to C shows that a result indicated in Fig. 9 is attained and a superior noise-proof effect can be attained under the state C according to the present invention. [0062] In addition, the sound-proof members 137 to 140 are formed into a stripe shape by cutting and forming a urethane sheet and one surface of each of these sound-proof members 137 to 140 is adhered to one of the transmission case 71 and the sound-proof cover 129, the sound-proof cover 129 in this preferred embodiment with adhesive agent. Yield when the sound-proof members 137 to 140 are formed can therefore be increased as compared with that of the prior art using a sheet-like sound-proof member with a shape corresponding to the shape of the sound-proof cover 129. In addition, the sound-proof cover 129 can be fixed to the transmission case 71 in a state where the sound-proof cover 129 can be fixed to the transmission case 71 in a state where the sound-proof members 137 to 140 are adhered to any one of the transmission case 71 and the sound-proof cover 129, resulting in that a productivity at the time of assembling the power unit P is improved. [0063] Although a part of the V-belt type automatic transmission M stored in the storing chamber 70 opposing against the driving pulley device 78, i.e. a side wall of the transmission case 71 is provided with the surrounding air intake port 126 for use in taking the cooling air into the storing chamber 70, the sound-proof cover 129 is formed into such a shape as one covering a substantial half part of the outer surface of the transmission case 71 at a side corresponding to the driven pulley device 79 at the V-belt type automatic transmission M. The sound-proof members 137 to 140 can therefore be arranged between the transmission case 71 and the sound-proof cover 129 without considering the surrounding air intake port 126 arranged at the transmission case 71 so as to enable a productivity to be increased. [0064] Although the preferred embodiment of the present invention has been described as above, the present invention is not limited to the aforesaid preferred embodiment, and various modifications in design can be carried out without departing from a scope of the present invention described in the claim. [Description of Reference Numerals] [0066] 78: driving pulley device 79: driven pulley device 80: V-belt 87: inner cylinder 88: outer cylinder 89: fixed half-pulley member 89a, 90a: conical surface 90: movable half-pulley member 91: torque cam mechanism 92: spring receiving member 93: coil spring 106: guide member 107: thrust bearing member 110: collar 115, 116: bearina member We Claim: 1. A driven pulley device of a V-belt type automatic transmission comprising: an inner cylinder (87) and an outer cylinder (88) slidably fitted to each other while their relative rotation around an axis line and their relative motion in an axial direction can be applied; a fixed half-pulley member (89) fixed to said inner cylinder (87); a movable half- pulley member (90) fixed to said outer cylinder (88) in opposition to said fixed half-pulley member (89); a torque cam mechanism (91) arranged between said inner cylinder (87) and said outer cylinder (88) so as to cause an axial partial force to act between said both half-pulley members in response to relative rotational phase difference between said movable half- pulley member (90) and said fixed half- pulley member (89); a spring receiving member (92) fixed to said inner cylinder (87) at a position where said movable half- pulley member (90) is held between it and said fixed half- pulley member (89); and a coil spring (93) enclosing said outer cylinder (88), shrunk and arranged between said movable half-pulley member (90) and said spring receiving member (92), a V-belt (80) for transmitting a rotational driving force from a driving pulley device (78) being held between oppositely facing conical surfaces (89a, 90a) of said fixed half-pulley member (89) and said movable half-pulley member (90), characterized in that the same further comprises a guide member (106) for guiding at least the inner circumference of said coil spring (93) at said movable half- pulley member (90); and a thrust bearing means (107) placed between said spring receiving member (92) and said coil spring (93). 2. The driven pulley device of a V-belt type automatic transmission as claimed in claim 1, wherein said thrust bearing means (107) is made such that a pair of bearing members (115, 116) made of self-lubricating resin and overlapped to each other are held between said coil spring (93) and said spring receiving member (92). 3. The driven pulley device of a V-belt type automatic transmission as claimed in claim 1 or 2, wherein said guide member (106) is formed of self-lubricating resin. 4. The driven pulley device of a V-belt type automatic transmission as claimed in any one of claims 1 to 3, wherein a metallic collar (110) is installed among said movable half-pulley member (90), said outer cylinder (88) and said guide member (106) for receiving an end face of said coil spring (93) at the side of said movable half-pulley member (90).

Full Text

[Technical Field]
[0001]
This invention relates to a driven pulley device of a V-belt type automatic transmission comprising an inner cylinder and an outer cylinder slidably fitted to each other while their relative rotation around an axis line and their relative motion in an axial direction can be applied, a fixed half-pulley member fixed to the inner cylinder, a movable half-pulley member fixed to the outer cylinder in opposition to the fixed half-pulley member, a torque cam mechanism arranged between the inner cylinder and the outer cylinder so as to cause an axial partial force to act between both the half-pulley members in response to a relative rotational phase difference between the movable half-pulley member and the fixed half-pulley member, a spring receiving member fixed to the inner cylinder at a position where the movable half-pulley member is held between it and the fixed half-pulley member, and a coil spring enclosing the outer cylinder, shrunk and arranged between the movable half-pulley member and the spring receiving member, and a V-belt for transmitting a rotational driving force from a driving pulley device is held between oppositely facing conical surfaces of the fixed half-pulley member and the movable half-pulley member.
[Background Art]
[0002]
A certain twisting can be generated at the coil spring shrunk and arranged between the movable pulley and the spring receiving member because the torque cam mechanism in such a driven pulley device as described above causes an axial force to act against the movable pulley in response to a relative rotational phase difference between the movable half-pulley member and the fixed half-pulley member. Such a twisting as above generates a reaction force against the axial force and causes a pressing force of the movable half-pulley member against the side face of the V-belt to be unstable and further this situation becomes a cause for generating vibration. In view of this fact, the invention disclosed in the patent document 1 prevents the coil spring from being twisted by arranging a plate-like bearing in at least one of one place between the movable half-pulley member and the coil spring and the other place between the spring receiving member and the coil spring.
[Patent Document 1] JP-A No. 42655/1996 [Disclosure of the Invention] [Problem to be Solved by the Invention] [0003]
However, the coil spring is not only easily twisted as described above, but also a wavy phenomenon is easily generated at the cylindrical surface by a partial eccentric state, and occurrence of the pulsation phenomenon can cause the coil spring to strike against its surrounding member to generate irregular sound. The aforesaid prior art system cannot prevent any occurrence of the pulsation phenomenon at the coil
spring. [0004]
The present invention has been invented in view of such circumstances as described above, and it is an object of the present invention to provide a driven pulley device of a V-belt type automatic transmission capable of not only preventing any twisting a the coil spring, but also preventing occurrence of any pulsation phenomenon. [Means for Solving the Problem] [0005]
In order to solve the aforementioned problem, the first characteristic of the present invention is to provide a driven pulley device of V-belt type automatic transmission comprising an inner cylinder and an outer cylinder slidably fitted to each other while their relative rotation around an axis line and their relative motion in an axial direction can be applied, a fixed half-pulley member fixed to the inner cylinder, a movable half-pulley member fixed to the outer cylinder in opposition to the fixed half-pulley member, a torque cam mechanism arranged between the inner cylinder and the outer cylinder so as to cause an axial partial force to act between both the half-pulley members in response to a relative rotational phase difference between the movable half-pulley member and the fixed half-pulley member, a spring receiving member fixed to the inner cylinder at a position where the movable half-pulley member is held between it and the fixed half-pulley member, and a coil spring enclosing the outer cylinder, shrunk and arranged between the movable half-pulley member and the spring receiving.

member, and a V-belt for transmitting a rotational driving force from a driving pulley device is held between oppositely facing conical surfaces of the fixed half-pulley member and the movable half-pulley member characterized in that the same comprises a guide member for guiding at least the inner circumference of the coil spring at the movable half-pulley member, and a thrust bearing means placed between the spring receiving member and the coil spring. [0006]
The second characteristic of the present invention is that the thrust bearing means is made such that a pair of bearing members made of self-lubricating resin and overlapped to each other is held between the coil spring and the spring receiving member. [0007]
The third characteristic of the present invention is that the guide member is formed by self-lubricating resin. [0008]
Further, the fourth characteristic of the present invention is that a metallic collar is installed among the movable half-pulley member, the outer cylinder and the guide member for receiving an end face of the coil spring at the movable half-pulley member. [Effect of the Invention]

[0009]
According to the first characteristic, it is possible to rotate the coil spring together with the movable half-pulley member without producing any relative rotation in respect to the movable half-pulley member by arranging the thrust bearing means between the spring receiving member and the coil spring when a relative rotational phase difference occurs between the movable half-pulley member and the fixed half-pulley member and then it is possible to prevent the coil spring from being twisted. Further, it is possible to set the inner circumference of the coil spring at the movable half-pulley member at its center location and prevent a pulsation phenomenon from being generated at the coil spring because the inner circumference of the coil spring is guided by the guide member at the movable half-pulley member. In particular, an amount of work of the half-pulley member at the movable half-pulley member in the coil spring becomes relatively high in response to an axial motion of the movable half-pulley member and the inner circumference at the side where the amount of work is increased is guided by the guide member, so that the pulsation phenomenon can be effectively prevented. [0010]
In addition, according to the second characteristic, the thrust bearing means can be constituted by a quite simple structure and both bearing members have a self-lubricating characteristic, so that it is possible to improve an anti-wearing characteristic against dusts. [0011]

According to the third characteristic, a sliding action between the inner circumference of the coil spring at the movable half-pulley member and the guide member can be improved, a clearance between the coil spring and the guide member can be set low as much as possible, thereby a pulsation phenomenon at the coil spring can be prevented more effectively and then a workability characteristic can be improved. [0012]
Further, according to the fourth characteristic, it is possible to set a thin thickness of the guide member, facilitate controlling over a clearance between the guide member made of resin and the inner circumference of the coil spring accompanied by a thermal expansion of the guide member, keep a difference in its friction coefficient in regard to that of the spring receiving member and generate a more positive relative rotation between the coil spring and the spring receiving member.
[Best Mode for Carrying Out the Invention] [0013]
A preferred embodiment of the present invention will be described as follows in reference to one preferred embodiment of the present invention shown in the accompanying drawings.
[Brief Description of the Drawings] [0065]
[Fig. 1] This is a side elevational view for showing a power unit and a rear wheel.
[Fig. 2] This is a sectional view taken along line 2-2 of Fig. 1.
[Fig. 3] This is a substantial part enlarged view of Fig. 2.
[Fig. 4] This is a sectional view taken along line 4-4 of Fig. 3.
[Fig. 5] This is a sectional view taken along line 5-5 of Fig. 3.
[Fig. 6] This is an enlarged cross sectional view of a
driven pulley^ device.
[Fig. 7] This figure shows a case cover and a sound-proof cover from an arrow direction taken along line 7-7 of Fig. 2.
[Fig. 8] This figure shows a case cover and a sound-proof cover from an arrow direction taken along line 8-8 of Fig. 2.
[Fig. 9] This figure shows a test result of a noise
generated state. -
[0014]
Figs. 1 to 9 illustrate one preferred embodiment of the present invention, Fig. i is a side elevational view for showing a power unit and a rear wheel, Fig. 2 is a sectional view taken along line 2-2 of Fig. i, Fig. 3 is a substantial part enlarged view of Fig. 2, Fig. 4 is a sectional view taken along line

4-4 of Fig. 3, Fig. 5 is a sectional view taken along line 5-5 of Fig. 3, Fig. 6 is an enlarged cross sectional view of a driven pulley device, Fig. 7 shows a case cover and a sound-proof cover from an arrow direction taken along line 7-7 of Fig. 2, Fig. 8 shows a case cover and a sound-proof cover from an arrow direction taken along line 8-8 of Fig. 2, and Fig. 9 shows a test result of a noise generated state. [0015]
At first, in Figs. 1 and 2, a power unit P constituted by an engine E arranged at a forward part of a rear wheel WR and a V-belt type automatic transmission M installed between the engine E and the rear wheel WR is mounted on a chassis frame (not shown) of a scooter type motorcycle, and the rear wheel WR arranged at the rear right portion of the power unit P is pivotally supported at the rear part of the power unit P. [0016]
An engine main body 11 of the engine E comprises a crank case 12 for rotatably supporting a crank shaft 16 having a rotating axis line in parallel with a rotating axis line of the rear wheel WR, a cylinder block 13 connected to the crank case 12, a cylinder head 14 connected to the cylinder block 13 at a side opposite to the crank case 12 and a head cover 15 connected to the cylinder head 14 at a side opposite to the cylinder block 13. [0017]
The cylinder block 13 is arranged such that an axis line of the cylinder bore 17 set at the cylinder block 13, i.e. a cylinder axis line C1 is slightly raised at a front part along

a forward or rearward direction of the motorcycle and becomes substantially to occupy a horizontal state. In addition, the crank case 12 comprises a pair of case half members 12a, 12b also including the cylinder axis line C1 and connected at a plane crossing at a right angle with an axis line of the crank shaft 16, a ball bearing 18 is installed between one case half member 12a of one of both case half members 12a, 12b and the crank shaft 16, and further a roller bearing 19 and an annular seal member 20 arranged more outside than that of the roller bearing 19 are installed between the other case half member 12b and the crank shaft 16. [0018]
A combustion chamber 23 is formed between the cylinder head 14 and a piston 21 slidably fitted in the cylinder bore 17 . An intake valve 24 for controlling intake gas fed into the combustion chamber 23 and an exhaust valve 25 for controlling exhaust gas discharged out of the combustion chamber 23 are arranged at the cylinder head 14 in such a way that they may be arranged in a substantial V-shape on a projected figure for a top plan surface crossing at a right angle with the rotating axis line of the crank shaft 16. A spark plug 26 adjacent to the combustion chamber 23 is fixed to the side face of the cylinder head 14 in a state where it is faced in a forwarding direction of the motorcycle. [0019]
Between the cylinder head 14 and the head cover 15 is stored a valve train 30 having an axis line in parallel with an axis line of the crank shaft 16, rotatably supported at the

cylinder head 14 and including a cam shaft 27 having an intake cam 28 and an exhaust cam 29 so as to drive to open or close the intake valve 24 and exhaust valve 25. [0020]
To one end of the cam shaft 27 is fixed a driven sprocket 31. In turn, the first driving sprocket 32 is fixed at such a position as one corresponding to the driven sprocket 31 at a more outside than that of the ball bearing 18 at the shaft 16. An endless cam chain 33 is wound around the first driving sprocket 32 and the driven sprocket 31. The cam chain 33 is stored in a chain chamber 34 formed over the cylinder block 13, cylinder head 14 and head cover 15 in such a way that the cam chain can run there. The cam shaft 27 is rotationally driven under the number of rotation of 1/2 of that of the crank shaft 16 by the first driving sprocket 32, the driven sprocket 31 and the cam chain 33. [0021]
Referring now also to Fig. 3, the crank shaft 16 is provided with a pair of crank webs 16a, 16b oppositely faced to each other while being axially spaced apart, and both ends of the crank pin 37 are connected to these crank webs 16a, 16b. In turn, one end of a connecting rod 38 is connected to the piston 21, and the other end of this connecting rod 38, i.e. a large end 38 is connected to the above-mentioned crank pin 37 through a needle bearing 39. [0022]
The second driving sprocket 40 is fixed to the crank shaft 16 at a more outside part than that of the first driving sprocket

31. In turn, an oil pump 41 (refer to Fig. 1) for use in sucking up oil from the lower portion at the crank case 12 and a cooling water pump 42 (refer to Fig. 1) for use in circulating cooling water to a cooling jacket 43 arranged at the cylinder block 13 and the cylinder head 14 are coaxially arranged at the lower portion of the crank case 12 and then a rotating force is transmitted from the second driving sprocket 40 to the oil pump 41 and the cooling water pump 42 through the chain 44. [0023]
At a more outside location than that of the second driving sprocket 40, there is provided a generator 46 comprising a stator 47 fixed to a right cover 45 attached to the right side face of the crank case 12 and an outer rotor 48 fixed to the crank shaft 16 so as to enclose the stator 47. [0024]
A driven gear 49 coaxially enclosing the crank shaft 16 and supported by the crank shaft 16 in such a manner that it can be rotated relatively is arranged between the second driving sprocket 40 and the outer rotor 48, and this driven gear 49 is connected to the outer rotor 48 through one-way clutch 50. In this way, a rotational driving force provided by a starter motor not shown can be inputted to the driven gear 49 and when the engine E starts to operate, a driving force from the crank shaft 16 is not transmitted to the starter motor from the starter motor is transmitted to the crank shaft 16 and the driving force from under an action of the one-way clutch 50 after the engine E starts to operate. [0025]

A cylindrical supporting cylinder 45a enclosing the right end of the crank case 12 is integrally protruded at the central part of an inner surface of the right cover 45, an annular seal member 53 is arranged between the supporting cylinder 45a and the crank shaft 16, an oil chamber 54 into which the right end of the crank shaft 16 protrudes is formed at the central part of an inner surface of the right cover 45, and an oil passage 55 arranged at both crank case 12 and right cover 45 is communicated with this oil chamber 54 in such a way that oil from the oil pump 41 may be guided. [0026]
The crank shaft 16 has coaxially the first oil passage hole 56 with a bottom part having its outer end communicated with the oil chamber 54 in such a way that its inner end is closed at a position substantially corresponding to the ball bearing 18. In addition, the crank pin 37 has coaxially the second oil passage hole 57 with a bottom part released to the ball bearing 18 for its light weight formation and supplying oil. In turn, the outer surface of one crank web 16a of the crank shaft 16 facing against the ball bearing 18 is formed with an annular fixing concave part 58 adjacent to an opening end of the second oil passage hole 57, and the outer circumference of an annular oil delivering plate 59 formed like a dish shape is press fitted and fixed against the fixing concave part 58 so as to cover the opening end of the second oil passage hole 57. [0027]
In addition, the crank shaft 16 has the first

communication hole 60 punched to cause the oil from the first oil passage hole 56 to be fed between the oil delivering plate 59 and the crank web 16a. Further, the crank pin 37 is provided with the second communication hole 61 for feeding the oil in the second oil passage hole 57 to the needle bearing 39. [0028]
Accordingly, the oil fed from the oil pump 41 to the oil chamber 54 through the oil passage 55 is supplied to the needle bearing 39 through the first oil passage hole 56, first communication hole 60, between the oil delivering plate 59 and the crank web 16a, second oil passage hole 57 and second communication hole 61. In addition, the crank shaft 16 is also provided with the third communication hole 62 for use in feeding the oil from the first oil passage hole 56 to between the crank shaft 16 and the driven gear 49. [0029]
Although the oil supplied to the needle bearing 3 9 is used for applying a lubrication between the large end part 38a of the connecting rod 38 and the crank pin 37, the oil splashes as the crank shaft 16 is rotated, the oil hole 63 for use in feeding a part of the splashed oil to the roller bearing 19 has an axis line in parallel with the axis line of the crank shaft 16 and is arranged at the other crank web 16b. [0030]
Also referring to Fig. 4, the other aforesaid crank web 16b is provided with a weight part 16ba at a side opposite to a connected part of the crank pin 37 in regard to the axis line C2 of the crank shaft 16. The inner surface of this crank web

16b comprises an arcuate higher level surface 64 corresponding to the weight part 16ba, a middle level surface 65 extending in parallel with a straight line L passing through an axis line of the crank pin 37 and through an axis line C2 of the crank shaft 16 and further extending in a band-like manner between the connected part of the crank pin 37 and the weight part 16ba, and another low level surface 66. The middle level surface 65 forms a step part 67 between it and the low level surface 66 and is formed to be slightly more inwardly protruded than that of the low level surface 66. The higher level surface 64 forms a step part 68 between the low level surface 66 and the middle level surface 65 and is formed to be protruded more inwardly than that of the middle level surface 65. [0031]
Thus, one end of the oil hole 63 is opened at the low level surface 66 near a location where both the steps 67, 68 are curved and connected to each other, oil splashed from the needle bearing 39 is transmitted along the steps 67, 68 and easily guided to one end of the oil hole 63. [0032]
Also referring to Fig. 5, the outer surface of the other aforesaid crank web 16b oppositely facing against the roller bearing 19 is provided with a cavity 69 formed in an arcuate manner substantially corresponding to the roller bearing 19, and the other end of the oil hole 63 is opened at the cavity 69. Thus, oil fed from the oil hole 63 is easily accumulated at the cavity 69 and splashed from the cavity 69 to the roller bearing 19, thereby oil can be supplied to the roller bearing

19. [0033]
Referring again to Fig. 2, the V-belt type automatic transmission M is stored in a storing chamber 70 in a transmission case 71 covering a part of the engine main body 11 from its side part to be cooperatively arranged at the engine main body 11 and extending to the left side of the rear wheel WR. The transmission case 71 comprises an inner case 72 integrally cooperated with the other case half member 12b of a pair of case half members 12a, 12b constituting the crank case 12, an outer case 73 fastened to the inner case 72 so as to cover the inner case 72 from outside and a gear reducer case 74 fastened to the rear part of the inner case 72 within the outer case 73. The storing chamber 70 is formed among the inner case 72, gear reducer case 74 and outer case 73, and a gear chamber 75 is formed between the inner case 72 and the gear reducer case 74. [0034]
The V-belt type automatic transmission M comprises a driving pulley device 78 installed at the other end of the crank shaft 16 protruded from the crank case 12 into the storing chamber 70, a driven pulley device 79 having an axis line in parallel with the crank shaft 16 and installed at an output shaft 81 rotatably supported by an inner case 72 and a gear reducer case 74, and an endless V-belt 80 for transmitting a driving power from the driving pulley device 78 to the driven pulley device 79. [0035]

The driving pulley device 78 comprises a fixed half-pulley member 81 fixed to the crank shaft 16, a movable half-pulley member 82 that can approach to or spaced apart from the fixed half-pulley member 81 and a centrifugal weight 83 moved in a radial outward direction in response to an increasing in the number of rotation of the crank shaft 16. The movable half-pulley member 82 is biased in such a direction as one in which it approaches to the fixed half-pulley member 81 while the centrifugal weight 83 moves in a radial outward direction in response to an increasing in the number of rotation of the crank shaft 16. [0036]
In Fig. 6, the driven pulley device 79 comprises an inner cylinder 87 coaxially enclosing an output shaft 81 while installing a needle bearing 85 and a ball bearing 86 between it and the output shaft 81, an outer cylinder 88 enabling a relative rotation around an axis line and a relative motion in an axial direction and fitting the inner cylinder 87 in a slidable manner, a fixed half-pulley member 89 fixed to the inner cylinder 87, a movable half-pulley member 90 fixed to the outer cylinder 88 while being oppositely faced against the fixed half-pulley member 89, a torque cam mechanism 91 arranged between the inner cylinder 87 and the outer cylinder 88 while a partial force in an axial direction being applied between both half-pulley members 89, 90 in response to a relative rotational phase difference between the movable half-pulley member 90 and the fixed half-pulley member 89, a spring receiving member 92 fixed to the inner cylinder 87 at a position

where the movable half-pulley member 90 is held between it and the fixed half-pulley member 89, a coil spring 93 enclosing the outer cylinder 88, shrunk and arranged between the movable half-pulley member 90 and the spring receiving member 92, and a centrifugal clutch 94 arranged between the inner cylinder 87 and the output shaft 81 while a power transmitting state is attained as the number of rotation of the engine exceeds a predetermined number of rotation. [0037]
Then, the V-belt 80 is held between the oppositely facing conical surfaces 81a, 82a of the fixed half-pulley member 81 and the movable half-pulley member 82 at the driving pulley device 78 and between the oppositely facing conical surfaces 89a, 90a of the movable half-pulley member 90 at the driven pulley device 79. At the driving pulley device 78, a winding radius of the V-belt 80 to the fixed and movable half-pulley members 81, 82 is increased as the movable half-pulley member 82 approaches to the fixed half-pulley member 81 in response to an increasing in the number of rotation of the crank shaft 16, and correspondingly at the driven pulley device 79, a winding radius of the V-belt 80 to the fixed and movable half-pulley members 89, 90 is decreased. [0038]
The fixed half-pulley member 89 is fixed to one end of the inner cylinder 87 with plural rivets 95 . . . and the spring receiving member 92 is fixed to the other end of the inner cylinder 87. Thus, the spring receiving member 92 also constitutes a part of the centrifugal clutch 94 . The centrifugal

clutch 94 comprises a cup-like clutch outer 96 fixed to the other end of the output shaft 81, centrifugal weights 97 ... enabled to be turned around an axis line in parallel with the output shaft 81 and pivotally supported at plural locations of the spring receiving member 92 and clutch springs 98 ... arranged between each of the centrifugal weights 97 ... and the spring receiving members 92. The inner cylinder 87, i.e. the fixed half-pulley member 89 and the clutch outer 96, i.e. the output shaft 81 are connected to each other by frictionally engaging the centrifugal weights 97 ... with the clutch outer 96 when the centrifugal force acting on each of the centrifugal weights 97 ... in response to a rotation of the spring receiving member 92 exceeds a spring biasing force of each of the clutch springs 98 .... [0039]
The movable half-pulley member 90 is fixed to one end of the outer cylinder 88 with plural rivets 102, ... so as to be oppositely faced against the fixed half-pulley member 89. In addition, the torque cam mechanism 91 is a well-known prior art mechanism comprising cam holes 103 . . . arranged at plural locations of the outer cylinder 88, cam pins 104 . . . implanted into the inner cylinder 87 while being inserted into these cam holes 103 ... and rollers 105 ... pivotally supported at the cam pins 104 ... rolled in the cam holes 103 .... [0040]
Thus, a clearance between the fixed half-pulley member 89 at the driven pulley device 79 and the movable half-pulley member 90 is determined by a balance among an axial force

generated by the torque cam mechanism 91, an axial resilient force generated by the coil spring 93 and a force from the V-belt 80 acted in such a direction as one spaced by the clearance between the fixed half-pulley member 89 and the movable half-pulley member 90. [0041]
The inner circumference of the coil spring 93 at the movable half-pulley member 90 is guided by the guide member 106, and a thrust bearing means 107 is arranged between the spring receiving member 92 and the coil spring 93. [0042]
The guide member 106 has at its one end a flange 106a for receiving one end of the coil spring 93 facing at the movable half-pulley member 90 and is formed into a cylindrical shape by self-lubricating resin. One end of the coil spring 93 is received by the flange 106a of the guide member 106 and further the inner circumference of the coil spring 93 at the movable half-pulley member 90 is guided by the guide member 106. In addition, the guide member 106 is provided with plural slits 108 . . . extending from its one end to the other end and plural slits 109 ... extending from the other end to one end. [0043]
In addition, among the movable half-pulley member 90, the outer cylinder 88 and the guide member 106 having the flange 106a is present a metallic collar 110 receiving a flange 106a of the guide member 106, inserting one end of the coil spring 93, having integrally at one end a receiving part 110a formed into a substantial L-shape in its longitudinal section and

formed into a cylindrical shape. This collar 110 coaxially encloses the outer cylinder 88 while closing from outside the cam holes 103 ... arranged in the outer cylinder 88. [0044]
In regard to this arrangement, grease is filled in each of the cam holes 103 ... and an annular chamber 111 formed between the output shaft 81 and the inner cylinder 87 between the needle bearing 85 and the ball bearing 86 . The inner cylinder 87 is provided with communication holes 112 ... connecting between the annular chamber 111 and each of the cam holes 103 . . . . Annular seal members 113, 113 resiliently contacted with the inner circumference of the collar 110 are installed at both outer circumferential ends in an axial direction of the outer cylinder 88, and the annular seal members 114, 114 slidably contacting with the outer circumference of the inner cylinder 87 are installed at both inner circumferential ends of the outer cylinder 88 in an axial direction. [0045]
The thrust bearing means 107 is made such that a pair of bearing members 115, 116 made of self-lubricating resin and overlapped to each other are held between the coil spring 93 and the spring receiving member 92, wherein one bearing member
115 has integrally a fitted cylindrical part 115a fitted to a circular cavity 117 arranged at the spring receiving member 92 and a flat plate ring-like bearing 115b contacted with a closing end of the cavity 117, and the other bearing member
116 is provided with a flat plate ring-like bearing 116a held between the bearing 115b and the coil spring 93, and a position

setting cylinder 116b integrally cooperated at the inner circumference of the bearing 116a while its relative position with the coil spring 93 is defined by being inserted into the inner circumference at the other end of the coil spring 93. [0046]
Further, referring again to Fig. 2, a wheel shaft 118 of the rear wheel WR is rotatably supported at the gear reducer case 74 and the inner case 72, and the end part of the wheel shaft 118 protruded from the transmission case 71 is rotatably supported at an arm 119 connected to the engine main body 11 and arranged at the right side of the rear wheel WR. [0047]
A row of reduction gears 120 arranged between the output shaft 81 and the wheel shaft 118 is stored in the gear chamber 75, and the row of reduction gears 120 comprises the first gear
121 arranged at the output shaft 81, the second gear 123 arranged
at an intermediate shaft 122 in parallel with the output shaft
81 and the wheel shaft 118 and rotatably supported at the inner
case 72 and the gear reducer case 74 and engaged with the first
gear 121, the third gear 124 arranged at the intermediate shaft
122 and the fourth gear 125 engaged with the third gear 124
and arranged at the wheel shaft 118.
[0048]
The side wall of the outer case 73 at the transmission case 71 opposing against the driving pulley device 78 is provided with a surrounding air intake port 126 for use in taking cooling air into the storing chamber 70, and a cooling fan 127 for dispersing the cooling air taken at the surrounding air

intake port 126 into the storing chamber 70 is integrally-arranged at the outer circumference of the movable half-pulley member 90 at the driving pulley device 78. [0049]
Also referring to Fig. 7, the outer surface of the transmission case 71 is covered by the case cover 128 and the sound-proof cover 129. The case cover 128 includes a portion where the surrounding air intake port 126 is arranged and is fastened to the outer case 73 at the transmission case 71 at plural locations there while covering the outer surface of the front half part of the transmission case 71. The sound-proof cover 129 is fastened to the outer case 73 at the transmission case 71 at plural locations so as to cover the outer surface of the rear half part of the transmission case 71 at a side corresponding to the driven pulley device 79. [0050]
The case cover 128 and the sound-proof cover 129 are fixed to the transmission case 71 so as to cover the front edge of the sound-proof cover 129 at the rear edge of the case cover 128, two hubs 129a ... arranged at the front part of the sound-proof cover 129 are held between the rear part of the case cover 128 and the transmission case 71, and the rear part of the case cover 128 and the front part of the sound-proof cover 129 are fastened together to the transmission case 71 by the screw members 13 0 .... [0051]
Further, an intake port 131 opened at a rear side is formed between the rear edge of the case cover 128 and the front edge

of the sound-proof cover 129, and an air feeding chamber 132 communicated with the intake port 131 is formed between the case cover 128 and the transmission case 71. [0052]
A filter 133 is fixed to the outer surface of the transmission case 71 so as to close the surrounding air intake port 126 from the side of the air feeding chamber 132, the surrounding air fed from the intake port 131 to the air feeding chamber 132 passes through the filter 133 to be purified and then sucked into the storing chamber 70. [0053]
Referring also to Fig. 8, between the transmission case 71 and the sound-proof cover 129 are arranged four sound-proof members 137, 138, 139 and 140, for example, so as to define a space between the transmission case 71 and the sound-proof cover 129 into plural closed spaces, for example, three closed spaces 134, 135 and 136. [0054]
Each of the sound-proof members 137 to 140 is formed into a stripe shape by cutting and forming a urethane sheet, respectively, and a surface of each of these sound-proof members 137 to 140 is adhered to any one of the transmission case 71 and the sound-proof cover 129 with adhesive agent, to the inner surface of the sound-proof cover 129 in this preferred embodiment. [0055]
Then, an action of the preferred embodiment will be described as follows. At least, the inner circumference of the

coil spring 93 is guided by a guide member 106 at the movable half-pulley member 90 in the driven pulley device 79 of the V-belt type automatic transmission M and the thrust bearing means 107 is present between the spring receiving member 92 and the coil spring 93, so that it is possible to rotate the coil spring 93 together with the movable half-pulley member 90 so as to prevent a relative rotation in respect to the movable half-pulley member 90, and further it is also possible to prevent the coil spring 93 from being twisted. Further, the inner circumference of the coil spring 93 at the movable half-pulley member 90 is guided by the guide member 106, so that it is possible to prevent the coil spring 93 from generating a pulsation phenomenon while a centering state of the inner circumference of the coil spring 93 is attained at the inner circumference of the coil spring 93. [0056]
In particular, an amount of work of the half-part of the movable half-pulley member 90 in the coil spring 93 becomes relatively high in response to an axial motion of the movable half-pulley member 90 and the inner circumference of the side where the amount of work becomes high is guided by the guide member 106, so that occurrence of corrugation state can be prevented more effectively. [0057]
In addition, the thrust bearing means 107 is made such that a pair of bearing members 115, 116 overlapped to each other are held between the coil spring 93 and the spring receiving member 92 and the thrust bearing means 107 can be constituted

by a quite simple structure and further both bearing members 115, 116 are made of self-lubricating resin, so that an anti-wearing characteristic against dust can be improved even if cooling air fed into the storing chamber 70 contains dusts. [0058]
In addition, the guide member 106 is also formed by the self-lubricating resin, thereby a sliding between the inner circumference of the coil spring 93 and the guide member 106 at the movable half-pulley member 90 can be improved. As a result, it becomes possible to set a clearance between the coil spring 93 and the guide member 106 as less as possible, occurrence of pulsation phenomenon generated at the coil spring 93 can be prevented as more effectively as possible and its workability can be improved. [0059]
Further, since the metallic collar 110 is arranged among the movable half-pulley member 90, outer cylinder 88 and the guide member 106 receiving the end face of the coil spring 93 at the movable half-pulley member 90, a thickness of the guide member 106 can be set thin to facilitate a management over a clearance between it and the inner circumference of the coil spring 93 as the resin-made guide member 106 is thermally expanded, and additionally, it is possible to maintain a difference of frictional coefficient between it and the spring receiving member 92 and generate a more positive relative rotation between the coil spring 93 and the spring receiving member 92. [0060]

Additionally, a space between the transmission case 71 and the sound-proof cover 129 covering the outer surface of the transmission case 71 and fixed to the transmission case 71 is defined into plural closed spaces 134 to 136 by the sound-proof members 137 to 140. Therefore, noise produced from the transmission case 71 is absorbed and restricted by the sound-proof members 137 to 140 arranged between the transmission case 71 and the sound-proof cover 129, and at the same time the noise is restricted by a sound resonance prevented from being generated by the plurality of closed spaces 134 to 136 formed between the transmission case 71 and the sound-proof cover 129. Accordingly, it is possible to attain a sufficient noise preventing effect with a simple structure in which a space between the transmission case 71 and the sound-proof cover 129 is defined into plural closed spaces 134 to 136 by the sound-proof members 137 to 140. [0061]
In regard to this point, it is apparent that, under an assumption that a state having no sound-absorbing member between the sound-proof cover 129 and the transmission case 71 is defined as A, a state having sound-absorbing member over a front surface between the sound-proof cover 129 and the transmission case 71 is defined as B, and a state having a space between the sound-proof cover 129 and the transmission case 71 divided into plural closed spaces 134 to 136 by the sound-proof members 137 to 140 according to the present invention is defined as C, a test for checking an occurrence of noise at the time of acceleration of the motorcycle at each

of the states A to C shows that a result indicated in Fig. 9 is attained and a superior noise-proof effect can be attained under the state C according to the present invention. [0062]
In addition, the sound-proof members 137 to 140 are formed into a stripe shape by cutting and forming a urethane sheet and one surface of each of these sound-proof members 137 to 140 is adhered to one of the transmission case 71 and the sound-proof cover 129, the sound-proof cover 129 in this preferred embodiment with adhesive agent. Yield when the sound-proof members 137 to 140 are formed can therefore be increased as compared with that of the prior art using a sheet-like sound-proof member with a shape corresponding to the shape of the sound-proof cover 129. In addition, the sound-proof cover 129 can be fixed to the transmission case 71 in a state where the sound-proof cover 129 can be fixed to the transmission case 71 in a state where the sound-proof members 137 to 140 are adhered to any one of the transmission case 71 and the sound-proof cover 129, resulting in that a productivity at the time of assembling the power unit P is improved. [0063]
Although a part of the V-belt type automatic transmission M stored in the storing chamber 70 opposing against the driving pulley device 78, i.e. a side wall of the transmission case 71 is provided with the surrounding air intake port 126 for use in taking the cooling air into the storing chamber 70, the sound-proof cover 129 is formed into such a shape as one covering

a substantial half part of the outer surface of the transmission case 71 at a side corresponding to the driven pulley device 79 at the V-belt type automatic transmission M. The sound-proof members 137 to 140 can therefore be arranged between the transmission case 71 and the sound-proof cover 129 without considering the surrounding air intake port 126 arranged at the transmission case 71 so as to enable a productivity to be increased. [0064]
Although the preferred embodiment of the present invention has been described as above, the present invention is not limited to the aforesaid preferred embodiment, and various modifications in design can be carried out without departing from a scope of the present invention described in the claim.
[Description of Reference Numerals]
[0066]
78: driving pulley device
79: driven pulley device
80: V-belt
87: inner cylinder
88: outer cylinder
89: fixed half-pulley member
89a, 90a: conical surface
90: movable half-pulley member
91: torque cam mechanism
92: spring receiving member
93: coil spring
106: guide member
107: thrust bearing member
110: collar
115, 116: bearina member

We Claim:
1. A driven pulley device of a V-belt type automatic transmission comprising:
an inner cylinder (87) and an outer cylinder (88) slidably fitted to each other while their
relative rotation around an axis line and their relative motion in an axial direction can be
applied;
a fixed half-pulley member (89) fixed to said inner cylinder (87);
a movable half- pulley member (90) fixed to said outer cylinder (88) in opposition to said
fixed half-pulley member (89);
a torque cam mechanism (91) arranged between said inner cylinder (87) and said outer
cylinder (88) so as to cause an axial partial force to act between said both half-pulley members
in response to relative rotational phase difference between said movable half- pulley member
(90) and said fixed half- pulley member (89);
a spring receiving member (92) fixed to said inner cylinder (87) at a position where said
movable half- pulley member (90) is held between it and said fixed half- pulley member (89);
and
a coil spring (93) enclosing said outer cylinder (88), shrunk and arranged between said
movable half-pulley member (90) and said spring receiving member (92),
a V-belt (80) for transmitting a rotational driving force from a driving pulley device (78) being held between oppositely facing conical surfaces (89a, 90a) of said fixed half-pulley member (89) and said movable half-pulley member (90),
characterized in that the same further comprises a guide member (106) for guiding at least the inner circumference of said coil spring (93) at said movable half- pulley member (90); and a thrust bearing means (107) placed between said spring receiving member (92) and said coil spring (93).
2. The driven pulley device of a V-belt type automatic transmission as claimed in claim 1,
wherein said thrust bearing means (107) is made such that a pair of bearing members (115,
116) made of self-lubricating resin and overlapped to each other are held between said coil
spring (93) and said spring receiving member (92).
3. The driven pulley device of a V-belt type automatic transmission as claimed in claim 1 or 2, wherein said guide member (106) is formed of self-lubricating resin.
4. The driven pulley device of a V-belt type automatic transmission as claimed in any one of claims 1 to 3, wherein a metallic collar (110) is installed among said movable half-pulley member (90), said outer cylinder (88) and said guide member (106) for receiving an end face of said coil spring (93) at the side of said movable half-pulley member (90).

Documents:

863-del-2005-Abstract-(16-06-2011).pdf

863-del-2005-abstract.pdf

863-del-2005-Claims-(16-06-2011).pdf

863-del-2005-claims.pdf

863-DEL-2005-Correspondence Others-(08-02-2012).pdf

863-del-2005-Correspondence Others-(16-06-2011).pdf

863-del-2005-correspondence-others.pdf

863-del-2005-Description (Complete)-(16-06-2011).pdf

863-del-2005-description (complete).pdf

863-del-2005-drawings.pdf

863-del-2005-form-1.pdf

863-del-2005-form-18.pdf

863-del-2005-form-2.pdf

863-del-2005-Form-3-(16-06-2011).pdf

863-del-2005-form-3.pdf

863-del-2005-form-5.pdf

863-del-2005-GPA-(16-06-2011).pdf

863-del-2005-gpa.pdf

863-DEL-2005-Petition-137-(08-02-2012).pdf

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Patent Number

251645

Indian Patent Application Number

863/DEL/2005

PG Journal Number

13/2012

Publication Date

30-Mar-2012

Grant Date

27-Mar-2012

Date of Filing

04-Apr-2005

Name of Patentee

HONDA MOTOR CO. LTD

Applicant Address

1-1, MINAMIAOYAMA 2-CHOME, MINATO-KU, TOKYO, JAPAN.

Inventors:

#	Inventor's Name	Inventor's Address
1	HIROKAZU KOMURO	C/O KABUSHIKI KAISHA HONDA GIJUTSU KENKYUSHO, 4-1, CHUO 1-CHOME, WAKO-SHI, SAITAMA, JAPAN.
2	HIDEO ISHIKAWA	C/O KABUSHIKI KAISHA HONDA GIJUTSU KENKYUSHO, 4-1, CHUO 1-CHOME, WAKO-SHI, SAITAMA, JAPAN.
3	KEIICHIRO NIZUMA	C/O KABUSHIKI KAISHA HONDA GIJUTSU KENKYUSHO, 4-1, CHUO 1-CHOME, WAKO-SHI, SAITAMA, JAPAN.
4	MICHIO ASUMI	C/O KABUSHIKI KAISHA HONDA GIJUTSU KENKYUSHO, 4-1, CHUO 1-CHOME, WAKO-SHI, SAITAMA, JAPAN.

PCT International Classification Number

F16H 9/12

PCT International Application Number

N/A

PCT International Filing date

PCT Conventions:

#	PCT Application Number	Date of Convention	Priority Country
1	2004-124481	2004-04-20	Japan