JP5580269B2 - Transmission gear device - Google Patents

Description

  The present invention relates to a hollow rotating shaft that is disposed in a power transmission system of a power unit including an internal combustion engine and is provided with a flange portion that projects radially outward, and a cylindrical boss portion that coaxially surrounds the rotating shaft. In addition, a plurality of teeth are provided on the outer periphery, and a disk portion projecting radially outward from the boss portion is integrally provided and supported on the rotating shaft so as to be capable of axial relative movement and relative rotation. Friction is generated between a power transmission gear that rotates in response to rotational power from the internal combustion engine, a damper spring interposed between the rotary shaft and the power transmission gear, and the power transmission gear and the flange portion. And a friction spring that biases the power transmission gear toward the flange portion so as to suppress relative rotation between the rotary shaft and the power transmission gear. On location.

  A part of a clutch mechanism in which a driven gear constituting a part of the primary reduction gear is configured to receive rotational power from a crankshaft of an internal combustion engine and to connect / disconnect power transmission between the driven gear and the rotary shaft And an oil hole for supplying lubricating oil to a contact portion between the clutch outer and a clutch outer side plate disposed between the driven gear and the clutch outer. Patent Document 1 discloses that the driven gear is provided on a cylindrical boss part integrally formed.

Japanese Patent No. 4179694

  In the one disclosed in Patent Document 1 described above, in order to supply lubricating oil to one side facing the clutch mechanism side of a driven gear as a power transmission gear that rotates by receiving rotational power from an internal combustion engine, The oil hole is provided in the boss, but depending on the characteristics of the clutch mechanism, there may be severe wear on the other side of the driven gear that faces away from the clutch mechanism. Similarly, it is necessary to supply lubricating oil to the other side surface of the driven gear. However, if the boss portion of the driven gear is newly provided with an oil hole that guides the lubricating oil to the other side surface of the driven gear, not only the processing time of the oil hole increases, but also the strength of the boss portion may be reduced. .

  The present invention has been made in view of such circumstances, and can ensure lubricity on both sides of the power transmission gear without increasing the number of oil holes provided in the boss portion of the power transmission gear. An object is to provide a transmission gear device.

  In order to achieve the above-described object, the present invention provides a hollow rotary shaft that is provided in a power transmission system of a power unit including an internal combustion engine and that has a flange portion that projects outward in the radial direction, and the rotary shaft is coaxial. A cylindrical boss portion surrounding the boss portion and a disk portion projecting radially outward from the boss portion so that a plurality of teeth are provided on the outer periphery are integrally formed on the rotary shaft and moved relative to each other in the axial direction. A power transmission gear that is supported to be rotatable and rotates by receiving rotational power from the internal combustion engine, a damper spring interposed between the rotary shaft and the power transmission gear, the power transmission gear, and the flange Friction that urges the power transmission gear toward the flange portion side to generate a frictional force between the portions to suppress relative rotation between the rotating shaft and the power transmission gear. In the transmission gear device including a ring, at least a part of the other end of the supply oil hole provided in the rotating shaft with one end being opened on the inner periphery of the rotating shaft is at least partially on the inner peripheral surface near the flange portion of the boss portion. The other end of the boss portion oil hole provided in the boss portion with one end opened on the inner periphery of the boss portion, the disc portion is connected to the flange portion. The first feature is that the boss is opened at the outer periphery of the boss portion.

  In addition to the configuration of the first feature, the present invention provides that the opening portion of the boss portion oil hole on the outer periphery of the boss portion is in contact with the side surface opposite to the flange portion of the disc portion. A second feature is that the spring is disposed at a position corresponding to the friction spring.

  In addition to the configuration of the first or second feature, the present invention provides the boss portion so that a part of the opening to the outer periphery of the rotation shaft of the supply oil hole is exposed from the inner periphery of the boss portion. The flange portion side end portion is formed as a third feature.

  In addition to any of the configurations of the first to third features, the present invention provides an opening to the outer periphery of the rotating shaft of the supply oil hole formed to have a larger diameter than the boss oil hole. A fourth feature is that the boss part oil hole is disposed between the opening part to the inner periphery of the boss part and the flange part.

  In the present invention, in addition to any of the configurations of the first to fourth features, an annular washer is interposed between the flange portion side inner peripheral portion of the power transmission gear and the flange portion, A fifth feature is that an annular gap is formed between the inner peripheral surface of the washer and the outer peripheral surface of the rotating shaft.

  In addition to any of the configurations of the first to fifth features of the present invention, the boss portion oil hole is formed so as to be inclined away from the flange portion as it approaches the outer periphery of the boss portion, The sixth feature is that the friction spring that contacts the side surface of the disc portion opposite to the flange portion is a disc spring that is inclined so as to move away from the flange portion as it goes radially outward.

  According to the present invention, in addition to any of the first to sixth features, the damper spring is held in a receiving hole provided in the disk portion of the power transmission gear. A seventh feature is that the friction spring is interposed between a side plate that is fixed to the rotating shaft so as to face a side surface opposite to the flange portion, and the disc portion.

  Furthermore, the present invention provides the power transmission gear at a position sandwiched between clutch outers respectively provided in a pair of clutch mechanisms arranged coaxially with the rotating shaft, in addition to any of the first to seventh features. It is an eighth feature that it is arranged.

  The primary reduction gear 60 of the embodiment corresponds to the transmission gear device of the present invention, the transmission cylinder shaft 65 of the embodiment corresponds to the rotation shaft of the present invention, and the primary driven gear 68 of the embodiment of the present invention. Corresponding to the power transmission gear, the second side plate 76 of the embodiment corresponds to the side plate of the present invention.

  According to the first feature of the present invention, the supply oil hole provided in the rotating shaft is opened at the outer periphery of the rotating shaft at least partially facing the inner peripheral surface near the flange portion of the boss portion, and is provided in the boss portion. Since the boss part oil hole is opened to the outer periphery of the boss part at a position where the disk part is sandwiched between the flange part, a part of the lubricating oil supplied from the inside of the rotating shaft through the supply oil hole The remaining portion of the lubricating oil supplied to one side facing the flange side of the transmission gear and supplied from the inside of the rotary shaft through the supply oil hole is between the inner circumference of the boss portion of the power transmission gear and the outer circumference of the rotary shaft. After that, it will be supplied to the other side of the power transmission gear from the boss oil hole, and power transmission without increasing the number of boss oil holes by devising the arrangement of the boss oil holes provided in the boss part Lubricating properties can be ensured by supplying lubricating oil to both side surfaces of the gear.

  According to the second feature of the present invention, since the opening of the boss oil hole on the outer periphery of the boss is arranged at a position corresponding to the friction spring, the lubricating oil from the boss oil hole is removed from the friction spring. As a result, the lubricity between the friction spring and the power transmission gear can be ensured.

  According to the third feature of the present invention, since a part of the opening of the supply oil hole to the outer periphery of the rotating shaft is exposed without being covered with the boss part, the lubricating oil is directly applied from the supply oil hole to the flange part side. As a result, the lubricity between the power transmission gear and the flange portion can be improved.

  According to the fourth feature of the present invention, the supply oil hole is formed to have a larger diameter than the boss oil hole, and is rotated between the opening of the boss oil hole to the inner periphery of the boss and the flange. Since the opening portion of the supply oil hole to the outer periphery of the shaft is disposed, the lubricating oil from the supply oil hole can be effectively distributed to both side surfaces of the power transmission gear to improve the lubricity.

  According to the fifth aspect of the present invention, a washer is interposed between the flange portion side inner peripheral portion and the flange portion of the power transmission gear, and an annular gap is formed between the inner peripheral surface of the washer and the outer peripheral surface of the rotary shaft. Therefore, the lubricating performance can be maintained by storing the lubricating oil from the supply oil hole in the annular gap.

  According to the sixth feature of the present invention, the boss portion oil hole is inclined so as to move away from the flange portion as it approaches the outer periphery of the boss portion, and is inclined so as to move away from the flange portion as going outward in the radial direction. Since the friction spring, which is a disc spring, contacts the side surface of the power transmission gear opposite to the flange portion of the disk portion, the lubricating oil supplied from the boss oil hole toward the friction spring side is applied to the friction spring. Accordingly, the friction spring can be supplied to the outer peripheral side.

  According to the seventh aspect of the present invention, since the friction spring is interposed between the side plate that holds the damper spring on the power transmission gear and the disc portion of the power transmission gear, the retainer that receives the friction spring is provided. It is possible to contribute to the reduction of the number of parts.

  Further, according to the eighth feature of the present invention, since the power transmission gear is arranged so as to be sandwiched between the clutch outers respectively provided in the pair of clutch mechanisms supported by the rotating shaft, Lubricating oil can be effectively supplied to both side surfaces of the power transmission gear that cannot be expected to be lubricated by scattered lubricating oil from the surroundings, thereby improving lubricity.

1 is a right side view of a motorcycle. FIG. 2 is an enlarged side view showing a main part of the internal combustion engine as viewed from the same direction as FIG. 1. FIG. 3 is a sectional view taken along line 3-3 in FIG. 2. FIG. 4 is an enlarged view of a portion indicated by an arrow 4 in FIG. 3. FIG. 5 is an enlarged view of a part indicated by an arrow 5 in FIG. 4.

  Embodiments of the present invention will be described with reference to FIGS. In the following description, the front and rear, the top and bottom, and the left and right directions are directions as viewed from the occupant riding the motorcycle.

  1, a motorcycle body frame F includes a head pipe 12 that supports a front fork 11 that pivotally supports a front wheel WF and a pair of left and right main frames 13 that extend rearwardly downward from the head pipe 12. A pair of left and right down frames 14 extending backward and downward at a steeper slope than the main frames 13, and a pair of left and right center frames 15 extending downward from the rear end of the main frame 13. A pair of left and right seat rails 16 extending rearward from the upper part of 15 ... and a rear frame 17 connecting the intermediate part of the center frame 15 ... and the rear part of the seat rail 16 ... are provided.

  In a region surrounded by the main frame 13, the down frame 14, and the center frame 15, a multi-cylinder internal combustion engine E, for example, two cylinders, and a shift partially incorporated in the engine body 18 of the internal combustion engine E are provided. The swing unit is arranged so that the power unit P including the machine M (see FIG. 3) is supported by the vehicle body frame F, and pivotally supports the rear wheel WR driven by the power exhibited by the power unit P at the rear end. A front end portion of 19 is supported on the center frame 15 so as to be swingable up and down. Further, a storage box 20 is mounted on the main frame 13 above the internal combustion engine E, and a tandem-type riding seat 21 is disposed behind the storage box 20 so as to be supported by the seat rails 16. A fuel tank 22 is disposed below the riding seat 21.

  2, the engine body 18 of the internal combustion engine E has a crankcase 26 that rotatably supports a crankshaft 25 having an axis extending in the vehicle width direction, and a cylinder axis C that is inclined forward. A cylinder block 27 coupled to the upper end of the front portion, a cylinder head 28 coupled to the upper end of the cylinder block 27, a head cover 29 coupled to the upper end of the cylinder head 28, and a lower portion of the crankcase 26 The oil pan 30 is provided.

  Referring also to FIG. 3, the crankcase 26 is formed by combining an upper case half 31 and a lower case half 32 that can be vertically divided by a split surface along a horizontal plane passing through the axis of the crankshaft 25. The cylinder block 27 is formed integrally with the upper case half 31.

  The cylinder block 27 has a plurality of, for example, two cylinder bores 33, 33 arranged in parallel in the vehicle width direction, and pistons 34 are slidably fitted to the cylinder bores 33. The pistons 34 are connected to the crankshaft 25 that extends along the arrangement direction, that is, the vehicle width direction and is rotatably supported by the crankcase 26.

  A generator cover 35 that forms a generator chamber 36 between the crankcase 26 and the crankcase 26 is coupled to the left side surface of the crankcase 26, and a rotor 38 of a generator 37 accommodated in the generator chamber 36 is provided. The stator 39 of the generator 37 is fixed to the generator cover 35 so as to be surrounded by the rotor 38. The stator 39 is fixed to the end of the crankshaft 25 that has entered the generator chamber 36.

  Further, as shown in FIG. 2, a starter motor 40 is fixedly arranged on the upper part of the crankcase 26, and a driven gear 42 constituting a part of a reduction gear train 41 that transmits power from the starter motor 40 is provided. The rotor 38 is connected via a one-way clutch 43.

  A clutch cover 45, which forms a clutch chamber 46 with the crankcase 26, is coupled to the right side surface of the crankcase 26. Thus, in the crankcase 26, first and second main shafts 47, 48 having an axis parallel to the crankshaft 25 and rotatably supported by the crankcase 26, a counter shaft 49, A transmission M in which gear trains of a plurality of shift stages that can be selectively established, for example, first to sixth gear trains G1 to G6 are provided is accommodated.

  The first and second main shafts 47 and 48 are coaxially arranged, and one end portion of the first main shaft 47 that rotatably passes through the right side wall of the crankcase 26 has a ball bearing 50 on the left side wall of the crankcase 26. The other end portion of the first main shaft 47 is rotatably supported by the clutch cover 45. The second main shaft 48 coaxially surrounds the first main shaft 47 and rotatably penetrates the right side wall of the crankcase 26. The second main shaft 48 is interposed between the right side wall of the crankcase 26 and the second main shaft 48. Is provided with a ball bearing 51, and a plurality of needle bearings 52, 52... Are interposed between the first and second main shafts 47, 48.

  One end portion of the countershaft 49 protrudes from the rear portion of the left side wall of the crankcase 26 with a ball bearing 53 and an annular seal member 54 interposed between the left side wall of the crankcase 26 and the other end of the countershaft 49. The portion is rotatably supported on the right side wall of the crankcase 26 via a needle bearing 55.

  Thus, a first speed gear train G1, a third gear train G3, and a fifth speed gear train G5 are provided between the first main shaft 47 and the counter shaft 49, and between the second main shaft 48 and the counter shaft 49, A second speed gear train G2, a fourth speed gear train G4, and a sixth speed gear train G6 are provided.

  A drive sprocket 56 is fixed to one end of the countershaft 49 protruding from the left side wall of the crankcase 26, and a transmission M is provided by an endless chain (not shown) wound around the drive sprocket 56. Is transmitted to the rear wheel WR.

  Thus, the power transmission system for transmitting the rotational power output from the crankshaft 25 of the internal combustion engine E to the rear wheel WR is a primary reduction gear 60 as a transmission gear device for transmitting the power from the crankshaft 25, The first clutch mechanism 61, the second clutch mechanism 62, the transmission M, the drive sprocket 56, and the chain are configured to include a primary reduction device 60, a primary reduction device 60, and a first main shaft. A first clutch mechanism 61 interposed between 47 and a second clutch mechanism 62 interposed between the primary reduction gear 60 and the second main shaft 48 are accommodated in the clutch chamber 46.

  Further, a pulsar 63 is fixed to the end of the crankshaft 25 in the clutch chamber 46, and a rotational speed sensor 64 disposed in the clutch chamber 46 so as to face the outer periphery of the pulsar 63 is a clutch. It is fixed to the cover 45.

  In FIG. 4, a hollow transmission cylinder shaft 65 as a rotation shaft disposed in the power transmission system is adjacent to the second main shaft 48 in the axial direction at an intermediate portion near the other end of the first main shaft 47. A large-diameter portion 65a that bulges outward in the radial direction at the axially intermediate portion of the transmission cylinder shaft 65, and radially outward from the outer periphery of the large-diameter portion 65a. A flange portion 65 b that protrudes in the direction is provided integrally with the transmission cylinder shaft 65. The first clutch mechanism 61 is provided on the transmission cylinder shaft 65 and the first main shaft 47 so that the power disconnection / connection between the transmission cylinder shaft 65 and the first main shaft 47 can be switched, and the second clutch mechanism 62 is Provided on the transmission cylinder shaft 65 and the second main shaft 48 so that the power disconnection / connection between the cylinder shaft 65 and the second main shaft 62 can be switched.

  The primary speed reducer 60 includes a primary drive gear 67 that rotates together with the crankshaft 25, and the transmission cylinder shaft that rotates in response to rotational power transmitted from the crankshaft 25 through the primary drive gear 67. A primary driven gear 68 as a power transmission gear supported by the large-diameter portion 65a of the 65 so as to be capable of relative movement and relative rotation in the axial direction; and a plurality of gears interposed between the transmission cylindrical shaft 65 and the primary driven gear 68. In order to suppress relative rotation between the transmission cylinder shaft 65 and the primary driven gear 68 by generating a frictional force between the damper spring 69 and the flange 65b of the primary driven gear 68 and the transmission cylindrical shaft 65. And a friction spring 70 that urges the driven gear 68 toward the flange portion 65b.

  Referring also to FIG. 5, the primary driven gear 68 has a cylindrical boss portion 68 a that coaxially surrounds the large-diameter portion 65 a of the transmission cylinder shaft 65, and projects radially outward from the boss portion 68 a. In addition, a plurality of housings 72, 72... Meshing with the primary drive gear 67 are integrally provided with a disk part 68b provided on the outer periphery, and the disk part 68b is the flange part 65b of the boss part 68a. Are integrally connected to the end of the side. Thus, an annular washer 71 is interposed between the flange 65b-side inner peripheral portion of the primary driven gear 68 and the flange portion 65b, and the inner peripheral surface of the washer 71 and the transmission An annular gap 73 is formed between the outer peripheral surfaces of the large diameter portion 65 a in the cylindrical shaft 65.

  The damper springs 69 are coil springs and are accommodated in a plurality of accommodation holes 74 provided in the flat plate portion 68b of the primary driven gear 68 at equal intervals in the circumferential direction. The disc portion 68b includes a first side plate 75 that faces the side surface of the disc portion 68b on the flange portion 65b side, and a first side plate 75 that faces the side surface of the disc portion 68b opposite to the flange portion 65b. The damper springs 69 are held in the housing holes 74 by the side plates 75 and 76. In addition, cylindrical collars 77 are disposed and arranged at a plurality of positions at equal intervals in the circumferential direction of the first and second side plates 75 and 76, and rivets 78 passing through the collars 77 are disposed. Thus, the first and second side plates 75 and 76 are connected, and the first and second side plates 75 and 76 are fixed to the transmission cylinder shaft 65 and rotate together with the transmission cylinder shaft 65.

  Thus, when no relative rotation occurs between the primary driven gear 68 and the first side plate 75, the second side plate 76, and the transmission cylinder shaft 65, both ends of the damper springs 69 ... are primary driven. When they are in contact with the gear 68 and the first and second side plates 75 and 76 and the relative rotation occurs, the damper springs 69 and so on between the primary driven gear 68 and the first and second damper springs 75 and 76. Is compressed, and a sudden torque change is buffered by the spring force exerted by the damper springs 69.

  Further, a plurality of restricting holes 79 through which the collars 77 are inserted are formed in a long hole shape in the circumferential direction of the transmission cylindrical shaft 65 and provided in the disk portion 68b of the primary driven gear 68, and the primary driven gear 68 and the first and second side plates 75, 76, that is, the transmission cylinder shaft 65, are restricted in the range in which the collars 77 move within the restriction holes 79.

  The friction spring 70 is a disc spring that is inclined so as to move away from the flange portion 65b as it goes outward in the radial direction. The two friction springs 70 and 70 are primarily driven at the small-diameter end on the inner peripheral side. The disc 68 is interposed between the second side plate 76 and the disc portion 68b so as to contact the side surface of the disc portion 68b opposite to the flange portion 65b.

  The first clutch mechanism 61, which is a hydraulic clutch, is disposed on the right side of the primary reduction gear 60, is formed in a bowl shape that opens to the opposite side of the primary reduction gear 60, and is not rotatable relative to the transmission cylinder shaft 65. A first clutch outer 80 coupled to the first main shaft 47, a first clutch inner 81 coupled to the first main shaft 47 in a relatively non-rotatable manner, and a plurality of clutches engaged with the first clutch outer 80 to allow relative movement in the axial direction. A plurality of first drive friction plates 82, 82,... And a plurality of first drive friction plates 82, 82,. Of the first driven friction plates 83, 83... And the first driven friction plates 82, 82... And the first driven friction plates 83, 83. Ring-shaped first receiver The plate 84 and the first pressure receiving plate 84 are attached to the first clutch outer 80 so as to be able to engage with the first drive friction plates 82, 82... And the first driven friction plates 83, 83. The first clutch is provided with a pressing portion 86a between the first retaining ring 85, the first driving friction plates 82, 82... And the first driven friction plates 83, 83. A first piston 86 that is fluid-tightly and slidably fitted to the outer 80 and forms a first hydraulic chamber 87 between the first clutch outer 80 and the first piston 86 is connected to the first hydraulic chamber 87. A first clutch spring 88 that biases the volume of the first clutch spring 88, and a ball bearing 89 is interposed between the first clutch inner 81 and the clutch cover 45. That is, the other end of the first main shaft 47 is rotatably supported by the clutch cover 45 via the first clutch inner 81.

  The first clutch mechanism 61 is in a clutch-off state in which power transmission is interrupted when no hydraulic pressure is applied to the first hydraulic chamber 87, and the first clutch is activated when hydraulic pressure is applied to the first hydraulic chamber 87. The mechanism 61 enters a clutch-on state in which the rotational power transmitted from the crankshaft 25 to the first clutch outer 80 via the primary reduction gear 60, the damper spring 69, and the transmission cylinder shaft 65 is transmitted to the first main shaft 47.

  The second clutch mechanism 62, which is a hydraulic clutch, is disposed closer to the crankcase 26 than the first clutch mechanism 61 so as to sandwich the primary reduction gear 60 between the first clutch mechanism 61 and the crankcase 26. A second clutch outer 90 that is formed in a cylindrical shape that opens toward the side and that is coupled to the transmission cylinder shaft 65 so as not to rotate relative to the first clutch outer 80 so that the primary driven gear 68 is sandwiched between the first clutch outer 80 and a second clutch outer 90. A second clutch inner 91 coupled to the main shaft 48 in a relatively non-rotatable manner, and a plurality of second drive friction plates 92, 92... Engaged with the second clutch outer 90 so as to be capable of relative movement in the axial direction. , The second drive friction plates 92, 92,... Are arranged alternately, and can be moved relative to each other in the axial direction to be engaged with the second clutch inner 91. The two driven friction plates 93, 93..., And the second driven friction plates 92, 92... And the second driven friction plates 93, 93. The second pressure receiving plate 94 and the second pressure receiving plate 94 can be engaged from the opposite side of the second driving friction plates 92, 92... And the second driven friction plates 93, 93. Has a second retaining ring 95, a second driving friction plate 92, 92... And a second driven friction plate 93, 93. A second piston 96 that is fluid-tightly and slidably fitted to the second clutch outer 90 and forms a second hydraulic chamber 97 between the second clutch outer 90 and the second piston 96. The second clutch spring 9 that urges the volume of the hydraulic chamber 97 to reduce the volume Provided with a door.

  Such a second clutch mechanism 62 is in a clutch-off state in which power transmission is interrupted when no hydraulic pressure is applied to the second hydraulic chamber 97, and the second clutch mechanism 62 is operated when hydraulic pressure is applied to the second hydraulic chamber 97. The mechanism 62 enters a clutch-on state in which the rotational power transmitted from the crankshaft 25 to the second clutch outer 90 via the primary reduction gear 60, the damper spring 69, and the transmission cylinder shaft 65 is transmitted to the second main shaft 48.

  The first clutch outer 80 of the first clutch mechanism 61 and the transmission cylinder shaft 65 are provided with a first oil passage 100 communicating with the first hydraulic chamber 87, and the first oil passage 100 is provided on the outer periphery of the first main shaft 47. A first annular recess 101 leading to is provided. The second clutch outer 90 of the second clutch mechanism 62 and the transmission cylinder shaft 65 are provided with a second oil passage 102 communicating with the second hydraulic chamber 97, and a second oil passage is provided on the outer periphery of the first main shaft 47. A second annular recess 103 leading to 102 is provided.

  First and second axial oil passages 104 and 105 that are parallel to each other are provided at the end of the first main shaft 47 on the clutch cover 45 side so as to close the inner end and extend in the axial direction. The directional oil passage 104 communicates with the first hydraulic chamber 87 via the first annular recess 101 and the first oil passage 100, and the second axial oil passage 105 passes through the second annular recess 103 and the second oil passage 102. It communicates with the second hydraulic chamber 97. Moreover, the outer end opening of the first axial oil passage 104 is closed by the plug member 106, and the outer end of the second axial oil passage 105 remains open.

  Further, the end of the first main shaft 48 on the clutch cover 45 side is liquid-tightly fitted into a cylindrical member 107 that is fitted and fixed to the clutch cover 45, and is between the outer periphery of the cylindrical member 107 and the clutch cover 45. The first main shaft 48 and the tubular member 107 are provided with a communication passage 110 that allows the first axial oil passage 104 to pass through the annular first oil chamber 108 formed in the first main shaft 48. A second oil chamber 109 communicating with the second axial oil passage 105 is formed between the first main shaft 47 and the tubular member 107 and the clutch cover 45.

  Paying attention to FIG. 2, a first oil filter 111 is provided at the lower part of the clutch cover 45, and the level gauge insertion cylinder 112 located behind the first oil filter 111 extends upward from the lower part of the clutch cover 45. The clutch cover 45 is provided. Further, control oil discharged from a first oil pump (not shown) built in the engine body 18 so as to pump up the oil in the oil pan 30 is supplied to the first oil filter 111, and this first oil filter 111. A hydraulic pressure control device 113 for controlling the hydraulic pressure of the oil purified by the oil filter 111 for each of the first clutch mechanism 61 and the second clutch mechanism 62 overlaps with a part of the level gauge insertion cylinder 112 in a side view. And disposed on the inner surface side of the clutch cover 45. Moreover, the first oil filter 111 is provided with an oil filter oil pressure sensor 114 for detecting the oil pressure supplied to the first oil filter 111, and the first and second clutch mechanisms 61, 61 controlled by the oil pressure control device 113, First and second hydraulic pressure sensors 115 and 116 that individually detect the hydraulic pressure for each of 62 are disposed on the clutch cover 45.

  The clutch cover 45 includes a first control supply oil passage 117 for guiding the oil for the first clutch mechanism 61 whose hydraulic pressure is controlled by the hydraulic control device 113 to the first oil chamber 108, and the hydraulic control device 113. A second control supply oil passage 118 is provided for guiding the oil for the second clutch mechanism 62 whose hydraulic pressure is controlled to the second oil chamber 109.

  Further, a second oil pump (not shown) different from the first oil pump is built in the engine body 18 so as to discharge lubricating oil. The oil discharged from the pump is purified by a second oil filter 119 attached to the lower part of the front wall of the crankcase 26 in the engine body 18, and the lubricating oil pressure sensor 120 that detects the supply oil pressure of the lubricating oil serves as the crankcase 26. Mounted on the front of the.

  Referring to FIGS. 3 and 4, in the first main shaft 47, the lubricating oil purified by the second oil filter 119 can be supplied to the lubricated portion around the first main shaft 47. An oil passage 123 is provided.

  Lubricating oil is supplied to the lubricating oil passage 123 from the end of the first main shaft 47 opposite to the clutch cover 45, and upstream oil provided coaxially with the first main shaft 47. It comprises a passage 123a and a downstream oil passage 123b having a smaller diameter than the upstream oil passage 123a and extending in parallel with the axis of the first main shaft 47. In this embodiment 1, the downstream oil passage 123b is The first and second axial oil passages 104 and 105 are formed to have the same diameter.

  The upstream oil passage 123a is perforated in the first main shaft 47 so that the outer end is opened at the end of the first main shaft 47 opposite to the clutch cover 45. The inner end of the upstream oil passage 123a is arranged at a position of the first and second hydraulic clutches 61, 62 arranged in the direction along the axis of the shaft 47 so as to overlap the second hydraulic clutch 62 in a side view. On the other hand, the downstream oil passage 123b is perforated from the end of the first main shaft 47 on the clutch cover 45 side so as to communicate with the inner end of the upstream oil passage 123a, and the outer end of the downstream oil passage 123b is The plug 124 is closed.

  Thus, oil holes 125 for supplying lubricating oil between the plurality of locations of the transmission M and the first and second main shafts 47 and 48 are provided at a plurality of locations spaced in the axial direction of the first main shaft 47. 125... Are provided so that the inner end passes through the upstream oil passage 123 a of the lubricating oil passage 123.

  A plurality of communication passages 126 passing through the inner ends of the downstream oil passages 123b of the lubricating oil passages 123 at positions corresponding to the axially intermediate portions of the large-diameter portions 65a of the transmission cylinder shafts 65 are provided. An outer groove is provided in the first main shaft 47 so as to pass through an annular groove 127 provided on the inner periphery of the transmission cylinder shaft, and a transmission cylinder is connected to the large diameter portion 65a of the transmission cylinder shaft 65 so as to communicate with the annular groove 127. A plurality of supply oil holes 128 having one end opened at the inner periphery of the shaft 65 are provided so as to extend in the radial direction of the transmission cylinder shaft 65, and the other end of the supply oil hole 128 is a boss in the primary driven gear 68. An opening is formed on the outer periphery of the large-diameter portion 65a of the transmission cylinder shaft 65 with at least a portion facing the inner peripheral surface of the portion 68a near the flange portion 65b.

  An annular groove 130 is provided on the inner periphery of the boss portion 68a so that lubricating oil can be supplied from the supply oil holes 128, and one end of the annular groove 130 passes through the annular groove 130 to the inside of the boss portion 68a. A plurality of boss oil holes 129 are formed in the boss 68a, and the other ends of the boss oil holes 129 are connected to the disk portion 68b of the primary driven gear 68 with the flange 65b. Is opened to the outer periphery of the boss portion 68a at a position sandwiched between them. In addition, the boss oil holes 129 are inclined so as to move away from the flange 65b as they approach the outer periphery of the boss 68a.

  Moreover, the opening part of the said boss | hub part oil hole 129 ... to the outer periphery of the said boss | hub part 68a is the said friction spring 70 ... which contact | abuts the side surface on the opposite side to the said flange part 65b of the said disk part 68b in the primary driven gear 68. It is arranged at a position corresponding to. Therefore, the friction springs 70 are disc springs that are inclined so as to move away from the flange portion 65b as they go outward in the radial direction, and the small-diameter end on the inner peripheral side of the friction springs 70 ... Since it is in contact with the side surface opposite to the flange portion 65b, the boss on the outer periphery of the boss portion 68a is located at a position corresponding to the contact portion of the small-diameter end of the friction spring 70 with the disc portion 68b. The openings of the partial oil holes 129 are arranged.

  By the way, the diameter D1 of the supply oil hole 128 is set to be larger than the diameter D2 of the boss oil hole 129, and each supply oil hole 128 is connected to the outer periphery of the large diameter portion 65a in the transmission cylinder shaft 65. The opening is disposed between the opening of the boss oil holes 129 to the inner periphery of the boss 68a, that is, between the annular groove 130 and the flange 65b.

  Further, the flange portion of the boss portion 68a is exposed such that a part of the opening to the outer periphery of the large diameter portion 65a of the transmission cylinder shaft 65 of the supply oil hole 128 is exposed from the inner periphery of the boss portion 68a. In this embodiment, a taper chamfer 68c exposes a part of the supply oil hole 128 at the inner peripheral portion of the flange 65b side end of the boss portion 68a. Is formed. As a result, the supply oil holes 128 are formed so that the flange portion 65b side inner peripheral portion of the primary driven gear 68 and the inner peripheral surface of the washer 71 interposed between the flange portions 65b and the large diameter portion of the transmission cylinder shaft 65 are provided. This leads directly to the annular gap 73 formed between the outer peripheral surface of 65a.

  Next, the operation of this embodiment will be described. The transmission cylinder shaft 65 is arranged on a hollow transmission cylinder shaft 65 which is provided in the power transmission system of the power unit P and is provided with a flange portion 65b projecting radially outward. The primary reduction device includes a cylindrical boss portion 68a that coaxially surrounds and a disc portion 68b that projects radially outward from the boss portion 68a and is provided with a plurality of teeth 72 on the outer periphery. A primary driven gear 68 constituting a part of the shaft 60 is supported so as to be capable of relative movement and rotation in the axial direction, and is provided on the transmission cylinder shaft 65 with one end opened on the inner periphery of the transmission cylinder shaft 65. The other end of the oil hole 128 is opened at the outer periphery of the transmission cylinder shaft 65 with at least a part facing the inner peripheral surface of the boss portion 68a near the flange portion 65b, and has one end on the inner periphery of the boss portion 68a. Open The other end of the boss part oil hole 129... Provided in the boss part 68a is opened to the outer periphery of the boss part 68a at a position sandwiching the disk part 68b with the flange part 65b. A part of the lubricating oil supplied from the inside of the cylindrical shaft 65 through the supply oil holes 128... Is supplied to the one side surface facing the flange portion 65 b side of the primary driven gear 68, and the supplied oil hole from the inside of the transmission cylindrical shaft 65. The remaining portion of the lubricating oil supplied through 128... Passes through the inner periphery of the boss portion 68 a of the primary driven gear 68 and the outer periphery of the transmission cylinder shaft 65 from the boss portion oil hole 129. By devising the arrangement of the boss part oil holes 129 provided in the boss part 68a, the both sides of the primary driven gear 68 are lubricated without increasing the number of the boss part oil holes 129. Oil can be supplied to ensure lubricity Rukoto can.

  Further, the opening of the boss oil hole 129 to the outer periphery of the boss 68a is formed on a friction spring 70 that contacts the side surface of the primary driven gear 68 opposite to the flange 65b of the disc 68b. Therefore, the lubricating oil between the friction springs 70 and the primary driven gear 68 can be secured by directing the lubricating oil from the boss oil holes 129 to the friction springs 70.

  Further, the flange 65b side end of the boss 68a is formed so that a part of the opening of the supply oil hole 128 to the outer periphery of the transmission cylinder shaft 65 is exposed from the inner periphery of the boss 68a. Therefore, a part of the opening portion of the supply oil hole 128... To the outer periphery of the transmission cylinder shaft 65 is exposed without being covered by the boss portion 68 a, and lubrication is performed from the supply oil hole 128 to the flange portion 65 b side. The lubricity between the primary driven gear 68 and the flange portion 65b can be improved by supplying oil directly.

  Moreover, the opening part to the outer periphery of the said transmission cylinder shaft 65 of the said supply oil hole 128 ... formed in larger diameter than the said boss part oil hole 129 ... is the inside of the said boss part 68a of the said boss part oil hole 129 .... Since it is disposed between the opening to the periphery and the flange portion 65b, the lubricating oil from the supply oil holes 128 can be effectively distributed to both side surfaces of the primary driven gear 68 to improve lubricity. it can.

  An annular washer 71 is interposed between the flange 65b-side inner peripheral portion of the primary driven gear 68 and the flange portion 65b, and the inner peripheral surface of the washer 71 and the outer peripheral surface of the transmission cylinder shaft 65. Since the annular gap 73 is formed therebetween, the lubricating performance can be maintained by storing the lubricating oil from the supply oil holes 128 in the annular gap 73.

  Further, the boss portion oil holes 129 are formed so as to be inclined away from the flange portion 65b as they approach the outer periphery of the boss portion 68a. What is the flange portion 65b of the disc portion 68b in the primary driven gear 68? The friction springs 70 that are in contact with the opposite side surface are disc springs that are inclined away from the flange portion 65b toward the outer side in the radial direction, so that the boss portion oil holes 129. Lubricating oil supplied toward the outer periphery of the friction springs 70 can be supplied along the friction springs 70.

  The damper spring 69 is held in the receiving hole 74 provided in the disc portion 68b of the primary driven gear 68, and the second side plate 76 is opposed to the side surface of the disc portion 68b opposite to the flange portion 65b. Is fixed to the transmission cylinder shaft 65, and the friction springs 70 are interposed between the second side plate 76 and the disc portion 68b. Therefore, a special retainer for receiving the friction springs 70 is provided. It is possible to contribute to a reduction in the number of parts.

  Further, the primary driven gear 68 is disposed at a position sandwiched between first and second clutch outers 80 and 90 provided in the pair of first and second clutch mechanisms 61 and 62 disposed coaxially with the transmission cylinder shaft 65, respectively. Therefore, the lubrication oil is effectively supplied to both side surfaces of the primary driven gear 68 where the lubrication by the scattered lubrication oil from the surroundings cannot be expected by being sandwiched between the both clutch outers 80 and 90 to improve the lubricity. be able to.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various design changes can be made without departing from the present invention described in the claims. Is possible.

  For example, in the above embodiment, the case where the present invention is applied to the primary reduction device 60 provided between the crankshaft 25 of the internal combustion engine E and the first and second clutch mechanisms 61 and 62 has been described. Without being limited to the reduction gear 60, a power transmission gear is supported on a hollow rotation shaft disposed in a power transmission system of a power unit P including the internal combustion engine E so as to be relatively rotatable, and between the rotation shaft and the power transmission gear 68. It can be widely implemented in connection with a transmission gear device in which a damper spring is interposed and the power transmission gear is urged so as to generate a frictional force between the power transmission gear and the flange portion of the rotary shaft. .

60 ... primary reduction gears 61, 62 as transmission gear devices ... clutch mechanism 65 ... transmission cylinder shaft 65b as rotation shaft ... flange portion 68 ... primary driven gear 68a as power transmission gear ... Boss part 68b ... Disk part 69 ... Damper spring 70 ... Friction spring 71 ... Washer 72 ... Teeth 73 ... Annular gap 74 ... Housing hole 76 ... Second side plates 80, 90 as a side plate ... Clutch outer 128 ... Supply oil hole 129 ... Boss oil hole E ... Internal combustion engine P ... Power unit

Claims (8)

  A hollow rotating shaft (65) provided in a power transmission system of a power unit (P) including the internal combustion engine (E) and provided with a flange portion (65b) projecting radially outward, and the rotating shaft (65 ) And a disc-shaped portion (68b) projecting radially outward from the boss portion (68a) so that a plurality of teeth (72) are provided on the outer periphery. A power transmission gear (68) which is integrally provided and supported by the rotary shaft (65) so as to be capable of relative movement and relative rotation in the axial direction and which receives rotational power from the internal combustion engine (E); A frictional force is generated between the damper spring (69) interposed between the rotating shaft (65) and the power transmission gear (68), and the power transmission gear (68) and the flange portion (65b) to rotate the rotation. Axis (65 And a transmission gear device comprising a friction spring (70) for urging the power transmission gear (68) toward the flange portion (65b) to suppress relative rotation between the power transmission gears (68). One end of the rotation shaft (65) is opened at the inner periphery of the rotation shaft (65), and the other end of the supply oil hole (128) provided in the rotation shaft (65) is located near the flange portion (65b) of the boss portion (68a). A boss oil hole provided in the boss portion (68a) with an opening at the outer periphery of the rotating shaft (65) with at least a part facing the peripheral surface and with one end opened at the inner periphery of the boss portion (68a). The other end of (129) is opened to the outer periphery of the boss | hub part (68a) in the position which pinches | interposes the said disc part (68b) between the said flange parts (65b), The transmission gear apparatus characterized by the above-mentioned.   The friction spring (the opening of the boss oil hole (129) to the outer periphery of the boss (68a) is in contact with the side of the disc (68b) opposite to the flange (65b). 70. The transmission gear device according to claim 1, wherein the transmission gear device is disposed at a position corresponding to 70).   The flange portion (68a) of the boss portion (68a) is exposed so that a part of the opening of the supply oil hole (128) to the outer periphery of the rotating shaft (65) is exposed from the inner periphery of the boss portion (68a). 65b) The transmission gear device according to claim 1 or 2, wherein a side end portion is formed.   The opening to the outer periphery of the rotating shaft (65) of the supply oil hole (128) formed to have a larger diameter than the boss part oil hole (129) is the boss part of the boss part oil hole (129). The transmission gear device according to any one of claims 1 to 3, wherein the transmission gear device is disposed between an opening to the inner periphery of (68a) and the flange portion (65b).   An annular washer (71) is interposed between the flange portion (65b) side inner peripheral portion of the power transmission gear (68) and the flange portion (65b), and the inner peripheral surface of the washer (71). The transmission gear device according to any one of claims 1 to 4, wherein an annular gap (73) is formed between the outer peripheral surfaces of the rotating shaft (65).   The boss oil hole (129) is formed so as to be inclined away from the flange part (65b) as it approaches the outer periphery of the boss part (68a), and the flange part (68b) The friction spring (70) that contacts the side surface opposite to 65b) is a disc spring that is inclined so as to move away from the flange portion (65b) as it goes radially outward. The transmission gear apparatus in any one of -5.   The flange portion (65b) of the disc portion (68b) is held so that the damper spring (69) is held in a receiving hole (74) provided in the disc portion (68b) of the power transmission gear (68). The friction spring (70) is interposed between the side plate (76) fixed to the rotating shaft (65) so as to face the opposite side surface and the disc portion (68b). The transmission gear device according to any one of claims 1 to 6.   The power transmission gear (68) is arranged at a position sandwiched between clutch outers (80, 90) provided in a pair of clutch mechanisms (61, 62) arranged coaxially with the rotation shaft (65). The transmission gear device according to any one of claims 1 to 7.

Images