JP4890409B2 - Power unit for small vehicles - Google Patents

Description

The present invention provides a valve operating device that is provided in an engine and opens and closes engine valves of a plurality of cylinders of the engine, and an operation mode of engine valves of some cylinders attached to the valve operating device and an open / close operation state and has a valve operation mode changing mechanism of switchable hydraulically closed rest state, the first and second clutch capable each switching connection and disconnection hydraulically interposed between the crankshaft and the transmission mechanism of the engine It is related with the power unit for small vehicles provided with the twin type clutch apparatus.

The hydraulic device that generates the hydraulic pressure for performing the shift control of the continuously variable transmission mechanism and the hydraulic device that generates the hydraulic pressure that performs the switching operation control of the valve operation mode changing mechanism in the valve operating device are mutually independent, It is known from Patent Document 1.
JP 2000-257453 A

  By the way, in a small vehicle such as a motorcycle, it is desirable to suppress an increase in the bulk of the power unit and downsize a hydraulic system related to a plurality of hydraulic control devices. Since the devices are independent of each other, the bulk of the power unit increases and the hydraulic system becomes larger.

  The present invention has been made in view of such circumstances, and an object thereof is to provide a power unit suitable for a small vehicle by reducing the hydraulic system while avoiding an increase in the bulk of the entire power unit.

In order to achieve the above object, a first aspect of the present invention is a valve operating device provided in an engine for opening and closing engine valves of a plurality of cylinders of the engine, and a part of the valve operating device attached to the valve operating device. comprises a cylinder of the engine valve operation mode capable of switching the opening and closing state and the closed rest state hydraulic valve operation mode changing mechanism, the first and second clutch capable each switching connection and disconnection with a hydraulic , met small vehicle power unit and a twin-type clutch device that is interposed between the crankshaft and the transmission mechanism of the engine, the cross-sectional-of operation mode and the first and second clutches of the valve operation mode changing mechanism A first oil pump that supplies hydraulic pressure for switching contact to these valve operation mode changing mechanisms, and the first and second clutches, and a second oil pump that supplies lubricating oil to each lubricating portion of the engine. And-pumped is said to be driven by power transmission from the crankshaft, are accommodated coaxially in the crankcase, the downstream side of the first oil passage extending from the discharge port of the first oil pump, the first A first branch oil passage connected to the first and second clutches, and a second branch oil passage connected to the valve operation mode changing mechanism, and the second branch oil passage of the first and second branch oil passages. only the pressure reducing valve is interposed, said a discharge port of the second oil pump, between the respective lubricated portions of the engine, characterized Rukoto connected by a second oil passage that is independent from the first oil passage And

  The intake valve 44 and the exhaust valve 45 of the embodiment correspond to the engine valve of the present invention, the rear bank side valve operating device 48R of the embodiment corresponds to the valve operating device of the present invention, and the gear transmission mechanism 103 of the embodiment This corresponds to the speed change mechanism of the present invention.

According to the first aspect of the present invention, the downstream side of the first oil passage extending from the discharge port of the first oil pump branches into the first and second branch oil passages, and the valve operation mode of the valve operating device is changed. because it is connected in common to the first and second clutch mechanisms and the clutch device, suppressing an increase in the bulk of the power unit, it is possible to compact hydraulic system related to the valve operation mode changing mechanism and a clutch device, small It can be set as the power unit suitable for a vehicle.

Also, by interposed only pressure reducing valve in the second branch oil passage leading to the valve operation mode changing mechanism, the hydraulic switchable operate in valve operation mode changing mechanism is lower than the clutch device, the discharge pressure of the oil pump Since the pressure is reduced and supplied, appropriate hydraulic pressures can be applied to the valve operation mode changing mechanism and the clutch device, respectively.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below based on one embodiment of the present invention shown in the accompanying drawings.

  1 to 15 show an embodiment of the present invention. FIG. 1 is a left side view of a motorcycle, FIG. 2 is a left side view of a power unit, FIG. 3 is a right side view of the power unit, and FIG. 4 is a cross-sectional view taken along line 4-4, FIG. 5 is a cross-sectional view taken along line 5-5 in FIG. 4, FIG. 6 is a cross-sectional view corresponding to FIG. 5 on the rear bank side, and FIG. 8 is a longitudinal sectional view of the gear transmission mechanism and the clutch device, FIG. 9 is an enlarged view of a main part of FIG. 8, FIG. 10 is an enlarged sectional view of line 10-10 in FIG. 2, and FIG. 12 is a system diagram showing the configuration of the hydraulic system, FIG. 13 is an enlarged view of the main part of FIG. 3, FIG. 14 is a cross-sectional view taken along the line 14-14 of FIG. 13, and FIG.

  First, in FIG. 1, a body frame F of a motorcycle that is a saddle-ride type vehicle includes a head pipe 26 that supports a front fork 25 that pivotally supports a front wheel WF and a left and right that extends rearwardly downward from the head pipe 26. It has a pair of main frames 27 ... and a pair of left and right pivot plates 28 ... connected to the rear of the main frames 27 ... and extending downward, and the front ends of the pivot plates 28 ... are pivotally supported by the pivot plates 28 ... The rear wheel WR is pivotally supported on the rear portion of the swing arm 29. In addition, a link 30 is provided between the lower part of the pivot plate 28 and the front part of the swing arm 29, and a cushion unit 31 is provided between the upper part of the pivot plate 28 and the link 30.

  A power unit P is suspended from the main frames 27 and the pivot plates 28, and rotational power output from the power unit P is transmitted to the rear wheel WR via a drive shaft 32 extending in the front-rear direction.

  A side stand 34 is attached to the engine main body 33 or the vehicle body frame F of the engine E included in the power unit P. In this embodiment, the side stand 34 is attached to the lower part of the left pivot plate 28 of the vehicle body frame F. Accordingly, when the side stand 34 is parked, the motorcycle is inclined to the left.

  2 and 3, the engine body 33 of the engine E has a front bank BF positioned in the front in a mounted state on the motorcycle and a rear bank BR positioned rearward of the front bank BF. A crankshaft 36 extending in the left-right direction of the motorcycle is rotatably supported by a crankcase 35 common to both banks BF and BR.

  The crankcase 35 is formed by combining an upper case half 35a and a lower case half 35b, and the front and rear cylinder blocks BF and BR are integrally formed with the upper case half 35a so as to form a V shape. The axis of the crankshaft 36 is formed on the coupling surface 37 of the upper case half 35a and the lower case half 35b.

  The front bank BF includes a front cylinder block 38F, a front cylinder head 39F coupled to the front cylinder block 38F, and a front head cover 40F coupled to the front cylinder head 39F. Is composed of a rear cylinder block 38R, a rear cylinder head 39R coupled to the rear cylinder block 38R, and a rear head cover 40R coupled to the rear cylinder head 39R, and an oil pan 41 is disposed below the crankcase 35. Combined.

  The front cylinder block 39F is formed with two cylinder bores 42 aligned in the axial direction of the crankshaft 36. The front cylinder block 39F is suspended from the engine body 33 with respect to the vehicle body frame F. The axis of... Is coupled to the crankcase 35 so as to incline forward. The rear cylinder block 39R is formed with two cylinder bores 42 aligned in the axial direction of the crankshaft 36. The rear cylinder block 39R is suspended from the body frame F of the engine body 33 in the cylinder bores 42. The axis of... Is coupled to the crankcase 35 so as to incline backward. Thus, pistons 43 are slidably fitted to both cylinder bores 42 of the front bank BF, and pistons 43 are slidably fitted to both cylinder bores 42 of the rear bank BR. The crankshaft 36 is connected in common.

  4 and 5, the front cylinder head 39F is provided with a pair of intake valves 44 for each of the cylinder bores 42. The pair of valve springs 46 are urged in the valve closing direction by a pair of valve springs 46 so as to be opened and closed. A pair of exhaust valves 45 are urged in a valve closing direction by valve springs 47 so as to be able to open and close. These intake valves 44 and exhaust valves 45 are arranged in front of each other. It is opened and closed by the part bank side valve operating device 48F.

  The front bank side valve operating device 48F has a shaft parallel to the crankshaft 36 and is rotatably supported by the front cylinder head 39F, and is disposed above the intake valves 44. An intake side that is interposed between a plurality (four in this embodiment) of intake side cams 50 and intake valves 44 provided on the camshaft 49 and is slidably fitted to the front cylinder head 39F. A valve lifter 51... And a plurality of (four in this embodiment) exhaust side cams 52 provided on the camshaft 49 are in rolling contact with one end 53, and the other end of each exhaust valve 45. A tappet screw 54 that abuts on the upper end of the stem 45a is provided with a rocker arm 55 that is screwed so that the advance / retreat position can be adjusted, and the rocker arm 55 is flat with the camshaft 49. Is swingably supported by the rocker shaft 56 fixedly disposed on the front cylinder head 39F have such axis.

6, a pair of intake valves 44 and a pair of exhaust valves 45 are urged in the rear cylinder head 39R for each cylinder bore 42 by a valve spring 280... 281. The intake valves 44 ... And the exhaust valves 45 ... Are opened and closed by a rear bank side valve operating device 48R.

The rear bank side valve operating device 48R has an axis parallel to the crankshaft 36, is rotatably supported by the rear cylinder head 39R, and is disposed above the intake valves 44 . A plurality of exhaust side camshafts 58 that are rotatably supported by the rear cylinder head 39R and have an axis parallel to the crankshaft 36 and disposed above the exhaust valves 45, and a plurality of intake side camshafts 57 are provided. (In this embodiment, four) intake-side cams 59 and intake valves 44 are interposed between the intake-side valve lifters 60 that are slidably fitted to the rear cylinder head 39R, and the exhaust-side camshaft 58. Is provided between a plurality of (four in this embodiment) exhaust-side cams 61 and exhaust valves 45 and is slidable on the rear cylinder head 39R. And an exhaust side valve lifter 62.

In addition, the rear bank side valve operating device 48R includes an intake side valve operating mode changing mechanism 63 that can switch the operating mode of the 2-cylinder intake valves 44 in the rear bank BR between an open / closed operating state and a closed valve closed state. An exhaust side valve operating mode changing mechanism 64 is provided which can switch the operating mode of the cylinder exhaust valves 45 to an open / closed operating state and a closed valve closed state.

  7, the intake side valve operation mode changing mechanism 63 is provided in association with the intake side valve lifters 60..., A pin holder 65 slidably fitted to the intake side valve lifters 60, and the intake side valve lifters 60. A hydraulic pin 66 is formed between the inner surface of the hydraulic chamber 66 and is slidably fitted to the pin holder 65. A spring force is applied to bias the slide pin 67 in a direction to reduce the volume of the hydraulic chamber 66. A return spring 68 that is provided between the slide pin 67 and the pin holder 65 and a stopper pin 69 provided between the pin holder 65 and the slide pin 67 that prevents rotation of the slide pin 67 around the axis line is provided.

An annular groove 71 is provided on the outer periphery of the pin holder 65, and has a bottomed sliding hole having an axis perpendicular to the axis of the intake valve lifter 60 and having one end opened to the annular groove 71 and the other end closed. 72 is provided on the pin holder 65. The pin holder 65 has an insertion hole 73 through which the tip of the stem 44 a of the intake valve 44 urged in the valve closing direction by the valve spring 280 is inserted, and a sliding hole 72 sandwiched between the insertion hole 73. The extension hole 74 is provided coaxially so as to accommodate the tip end portion of the stem 44 a of the intake valve 44 . A disc-shaped shim 75 that closes the end of the extension hole 74 on the closed end side of the intake side valve lifter 60 is fitted into the pin holder 65, and the protrusion 76 that contacts the shim 75 is the central part of the closed end inner surface of the intake side valve lifter 60. Are integrally provided.

  A slide pin 67 is slidably fitted in the slide hole 72 of the pin holder 65. A hydraulic chamber 66 communicating with the annular groove 71 is formed between one end of the slide pin 67 and the inner surface of the intake side valve lifter 60, and is formed between the other end of the slide pin 67 and the closed end of the slide hole 72. A return spring 68 is accommodated in the spring chamber 77.

An accommodation hole 78 that can be coaxially connected to the insertion hole 73 and the extension hole 74 is provided in the intermediate portion in the axial direction of the slide pin 67 so as to accommodate the distal end portion of the stem 44 a. The end on the side is opened to a flat contact surface 79 formed on the lower outer surface of the slide pin 67 so as to face the insertion hole 73. Thus, the contact surface 79 is formed relatively long along the axial direction of the slide pin 67, and the accommodation hole 78 is opened at a portion of the contact surface 79 on the hydraulic chamber 66 side.

Such a slide pin 67 balances the hydraulic pressure acting on one end side of the slide pin 67 by the hydraulic pressure of the hydraulic chamber 66 and the spring force acting on the other end side of the slide pin 67 by the return spring 68. When the hydraulic pressure in the hydraulic chamber 66 is low, the housing hole 78 is shifted from the axis of the insertion hole 73 and the extension hole 74 so that the tip of the stem 44a is abutted. 7 is moved to the right in FIG. 7 so as to contact the contact surface 79, and in the operating state in which the hydraulic pressure in the hydraulic chamber 66 becomes high, the distal end portion of the stem 44a inserted through the insertion hole 73 is accommodated in the accommodation hole 78. And it moves to the left side of FIG.

Thus, when the slide pin 67 moves to a position where the accommodation hole 78 is coaxially connected to the insertion hole 73 and the extension hole 74, the intake side valve lifter 60 slides due to the pressing force acting from the intake side cam 59. pin holder 65 and the slide pin 67 is also moved to the intake valve 44 side along with the intake side valve lifter 60, only the intake-side valve lifter 60 and the distal portion of the stem 44 a is accommodated in the accommodation hole 78 and the extension hole 74 in accordance with the not acting pressing force in the valve opening direction to the intake valve 44 from the pin holder 65, the intake valve 44 will remain dormant. Further, when the slide pin 67 moves to a position where the tip of the stem 44 a comes into contact with the contact surface 79, the intake side valve lifter 60 slides due to the pressing force acting from the intake side valve cam 59. since according the pin holder 65 and the pressing force in the valve opening direction to the intake valve 44 with the movement of the intake valve 44 side of the slide pin 67 acts, the intake valve 44 is opened and closed in response to the rotation of the intake cam 59.

  The rear cylinder head 39R is provided with a support hole 80 for fitting the intake side valve lifter 60 to slidably support the intake side valve lifter 60. An annular recess 81 communicating with the annular groove 71 of the pin holder 65 is provided so as to surround the intake side valve lifter 60, regardless of sliding in the support hole 80 of the side valve lifter 60. Between the intake side valve lifters 60... And the rear cylinder head 39R, springs 82 are provided for urging the intake side valve lifters 60 in a direction to contact the intake side cams 59.

Exhaust valve-operation mode changing mechanism 64, which is provided in connection with the exhaust-side valve lifters 62 ... it is configured similarly to the intake side valve operation mode changing mechanism 63, the exhaust valve when the high hydraulic pressure is applied 45 Can be switched between a state in which the exhaust valve 45 is closed and a state in which the exhaust valve 45 is opened and closed when the acting hydraulic pressure decreases.

That is, the rear bank side valve operating device 48R is controlled by the intake side valve operation mode changing mechanism 63 ... and the exhaust side valve operation mode changing mechanism 64 ..., and the intake valves 44 ... and the exhaust valves 45 of the two cylinders in the rear bank BR. It is possible to switch between a state in which the... Is opened and closed and a state in which the intake valves 44 ... And the exhaust valves 45 .

  In FIG. 4 again, a generator 84 is connected to the left end portion of the crankshaft 36 when the engine body 33 is mounted on the vehicle body frame F. The generator 84 is fixed to the crankshaft 36. Generator 85 including a crankcase 35 and a generator cover 87 coupled to the left side surface of the crankcase 35. The stator 86 is housed in a chamber 88 and is fixed to a generator cover 87.

  In addition, a gear 90 is connected to the rotor 86 via a one-way clutch 89 that enables power transmission to the rotor 86 side, and power from a starter motor (not shown) is transmitted to the gear 90. .

  On the other hand, a clutch cover 92 that forms a clutch chamber 91 with the crankcase 35 is coupled to the right side surface of the crankcase 35 when the engine main body 33 is mounted on the vehicle body frame F. Drive sprockets 93 and 94 are fixed to the crankshaft 36 in the chamber 91. One drive sprocket 93 is a part of the front bank side timing transmission mechanism 95 that transmits the rotational power of the crankshaft 36 at a reduction ratio of 1/2 to the camshaft 49 in the front bank side valve gear 48F. The front bank side timing transmission mechanism 95 is configured by winding an endless cam chain 97 around the drive sprocket 93 and a driven sprocket 96 provided on the camshaft 49. The other drive sprocket 94 is a rear bank side timing transmission mechanism that transmits the rotational power of the crankshaft 36 to the intake side and exhaust side camshafts 57, 58 in the rear bank side valve operating device 48R at a reduction ratio of 1/2. 98, and the rear bank side timing transmission mechanism 98 includes driven sprockets 94 and driven sprockets (not shown) provided on the intake side and exhaust side camshafts 57 and 58, respectively. In addition, an endless cam chain 99 is wound around.

  Thus, the front cylinder block 38F and the front cylinder head 39F are formed with a cam chain chamber 100 for running the cam chain 97, and the rear cylinder block 38R and the rear cylinder head 39R run the cam chain 99. A cam chain chamber (not shown) is formed.

  The power transmission path between the crankshaft 36 and the rear wheel WR includes a primary reduction gear 101, a clutch device 102, a gear transmission mechanism 103, and a drive shaft 32 in order from the crankshaft 36 side. 102 is housed in the clutch chamber 91, and the gear transmission mechanism 103 is housed in the crankcase 35.

  Referring also to FIG. 8, the gear transmission mechanism 103 includes gear trains of a plurality of shift stages that can be selectively established, for example, first to sixth gear trains G1, G2, G3, G4, G5, and G6. The second, fourth, and sixth gear trains G2, G4, and G6 are provided between the first main shaft 105 and the counter shaft 107, and the first main shaft 105 is provided in the crankcase 35. The first, third, and fifth speed gear trains G1, G3, and G5 are provided between the second main shaft 106 that passes through the shaft and the counter shaft 107 so as to be relatively rotatable.

  The crankcase 35 includes a pair of side walls 35c and 35d that are opposed to each other at an interval in the direction along the axis of the crankshaft 36, and has an axis parallel to the crankshaft 36 and is formed in a cylindrical shape. The intermediate portion of the first main shaft 105 penetrates the side wall 35 c in a rotatable manner, and a ball bearing 108 is interposed between the side wall 35 c and the first main shaft 105. The second main shaft 106 having an axis parallel to the crankshaft 36 passes through the first main shaft 105 so as to be relatively rotatable while maintaining a constant axial relative position to the first main shaft 105. A plurality of needle bearings 109 are interposed between the main shaft 105 and the second main shaft 106. The other end of the second main shaft 106 is rotatably supported on the side wall 35d of the crankcase 35 via a ball bearing 110.

  One end of a crankshaft 107 having an axis parallel to the crankshaft 36 is rotatably supported on the side wall 35c via a ball bearing 111, and the other end of the countershaft 107 is provided with a ball bearing 112 and an annular seal member 113. Is interposed between the side wall 35d and the side wall 35d so as to rotate freely. A driving bevel gear 114 is fixed to the protruding end of the countershaft 107 from the side wall 35d. The driving bevel gear 114 is meshed with a driven bevel gear 115 having a rotation axis extending in the front-rear direction of the motorcycle.

  By the way, the driving bevel gear 114 and the driven bevel gear 115 cover a part of the side wall 35d of the crankcase 35 and are detachably coupled to the side wall 35d, and are attached to and detached from the first gear cover 116. The second gear cover 117 that can be coupled and the side wall 35d are meshed with each other in a gear chamber 118, and the shaft portion 115a that the driven bevel gear 115 is coaxial with has a second gear cover 117. And a ball bearing 119 and an annular seal member 120 positioned outside the ball bearing 119 are interposed between the shaft 115a and the second gear cover 117. One end of a support shaft 121 is fitted to the driven bevel gear 115, and the other end of the support shaft 121 is rotatably supported on the first gear cover 116 via a roller bearing 122. Thus, the shaft portion 115a is connected to the drive shaft 32.

  Referring also to FIG. 9, the clutch device 102 has a first and second clutches 124 and 125 provided between the gear transmission mechanism 103 and the crankshaft 36 and is configured in a twin type. The first clutch 124 is provided between one end portions of the crankshaft 36 and the first main shaft 105, and the second clutch 125 is provided between one end portions of the crankshaft 36 and the second main shaft 106. Thus, the power from the crankshaft 36 is input to the clutch outer 126 common to the first and second clutches 124 and 125 via the primary reduction gear 101 and the damper spring 127.

  The primary reduction gear 101 includes a drive gear 128 provided on the crankshaft 36 outside the drive sprocket 94, and a driven gear 129 that is rotatably supported by the first main shaft 105 and meshes with the drive gear 128. The driven gear 129 is connected to the clutch outer 126 via a damper spring 127.

  A pulsar 268 is attached to the shaft end of the crankshaft 36 outside the primary reduction gear 101, and a rotational speed detector 269 that detects the rotational speed of the crankshaft 36 by detecting the pulsar 268 serves as a clutch cover. It is attached to the inner surface of 92. The clutch cover 92 is provided with an inspection hole 270 for inspecting the pulsar 268. The inspection hole 270 is provided in the clutch cover 92 eccentrically from the axis of the crankshaft 36 in order to reduce the diameter as much as possible. The inspection hole 270 is closed with a detachable lid member 271.

  The first clutch 124 is relatively rotated with respect to the clutch outer 126, the first clutch inner 131 that is coaxially surrounded by the clutch outer 126 and is coupled to the first main shaft 105 so as not to rotate relative to the clutch outer 126, and the clutch outer 126. A plurality of first friction plates 132 that are impossiblely engaged and a plurality of second friction plates that are engaged with the first clutch inner 131 so as not to be relatively rotatable and are alternately arranged with the first friction plates 132. .., A first pressure receiving plate 134 provided on the first clutch inner 131 opposite to the first and second friction plates 132, 133, which are arranged to overlap each other, and the first and second friction plates , 133... Are sandwiched between the first pressure receiving plate 134 and a first spring 136 that biases the first piston 135.

  An end wall member 138 that forms a first hydraulic chamber 137 that faces the back surface of the first piston 135 with the first piston 135 is fixedly disposed on the first clutch inner 131, and the first hydraulic chamber 137. The first piston 135 operates to clamp the first and second friction plates 132, 133,... Between the first pressure plate 134 and the first clutch 124 as a clutch outer. In this state, the power transmitted from the crankshaft 36 to 126 is transmitted to the first main shaft 105. In addition, a canceller chamber 139 is formed between the first clutch inner 131 and the first piston 135 so that the front surface of the first piston 135 faces, and the first spring 136 is on the side where the volume of the first hydraulic chamber 137 is reduced. It is accommodated in the canceller chamber 139 so as to exert a spring force.

  In addition, the canceller chamber 139 is provided in a first oil passage 140 provided coaxially with the second main shaft 106 in order to supply oil between the lubricating portions of the gear transmission mechanism 103 and the first and second main shafts 105 and 106. Communicated. Therefore, even if centrifugal force accompanying rotation acts on the oil in the first hydraulic chamber 137 in the reduced pressure state and a force that presses the first piston 135 is generated, the centrifugal force acts on the oil in the canceller chamber 139 as well. It is avoided that the first piston 135 undesirably moves to the side sandwiching the first and second friction plates 132... 133 between the first pressure receiving plate 134.

  The second clutch 125 is arranged so as to be aligned with the first clutch 124 in a direction along the axis of the second main shaft 106 so as to sandwich the first clutch 124 with the primary reduction gear 10. The clutch outer 126, a second clutch inner 141 that is coaxially surrounded by the clutch outer 126 and is coupled to the second main shaft 106 so as not to be relatively rotatable, and is engaged with the clutch outer 126 so as not to be relatively rotatable. A plurality of third friction plates 142 and a plurality of fourth friction plates 143 that are engaged with the second clutch inner 141 in a relatively non-rotatable manner and are alternately arranged with the third friction plates 142. The second pressure receiving plate 144 provided on the second clutch inner 141 is opposed to the third and fourth friction plates 142, 143,. Includes third and fourth friction plates 142 ..., a second piston 145 which sandwich 143 ... to between the second pressure receiving plate 144, a second spring 146 which urges the second piston 145.

  An end wall member 148 that forms a second hydraulic chamber 147 facing the back surface of the second piston 145 with the second piston 145 is fixedly disposed on the second clutch inner 141, and the second hydraulic chamber 147. The second piston 145 operates to clamp the third and fourth friction plates 142, 143,... With the second pressure receiving plate 144 in response to the increase in hydraulic pressure. In this state, the power transmitted from the crankshaft 36 to 126 is transmitted to the second main shaft 106. A canceller chamber 149 is formed between the second clutch inner 141 and the second piston 145 so that the front surface of the second piston 145 faces. The second spring 146 reduces the volume of the second hydraulic chamber 147. It is accommodated in the canceller chamber 149 so as to exert a spring force.

  Moreover, the canceller chamber 149 communicates with a second oil passage 150 described later. Therefore, even if a centrifugal force due to rotation acts on the oil in the second hydraulic chamber 147 in the decompressed state and a force pressing the second piston 145 occurs, the centrifugal force acts on the oil in the canceller chamber 149 as well. It is avoided that the second piston 145 undesirably moves to the side sandwiching the third and fourth friction plates 142, 143,... With the second pressure receiving plate 144.

  First, second, and third partition members 151, 152, and 153 are attached to the inner surface side of the clutch cover 92 that covers the first and second clutches 124 and 125 from the right side toward the front in the traveling direction of the motorcycle. Thus, a first cylinder member 155 is provided between the second main shaft 106 and the first partition member 151 so as to form a first oil passage 154 that communicates with the first hydraulic chamber 137 of the first clutch 124. An annular second oil passage 150 communicating with the canceller chamber 149 of the second clutch 125 is formed between the shaft 106 and the second partition member 152 between the first cylinder member 155 and the first cylinder member 155 coaxially. A surrounding second cylinder member 156 is provided, and an annular second oil passage 157 leading to the second hydraulic chamber 147 is provided between the second main shaft 106 and the third partition wall member 153 between the second cylinder member 156 and the second cylinder member 156. A third cylinder member 158 that is formed and coaxially surrounds the second cylinder member 156 is provided.

  In FIG. 8 again, the fourth gear train G4, the sixth gear train G6, and the second gear train are sequentially arranged between the first main shaft 105 and the counter shaft 107 of the gear transmission mechanism 103 from the side opposite to the clutch device 102. The speed gear train G2 is provided in a line. The second speed gear train G2 is a second speed drive gear 160 provided integrally with the first main shaft 105 and a second speed drive gear 160 that is rotatably supported by the counter shaft 107 and meshes with the second speed drive gear 160. The sixth-speed gear train G6 includes a second-speed driven gear 161, and a sixth-speed drive gear 162 that is rotatably supported on the first main shaft 105 and an axial movement of the countershaft 107. The fourth-speed gear train G4 is moved to the first main shaft 105 in the axial direction. The sixth-speed driven gear 163 is engaged with the sixth-speed drive gear 162 and is supported in a relatively non-rotatable manner. 4th-speed drive gear 164 supported so as not to rotate relative to the 4th-speed drive gear 164, which is supported relative to the countershaft 107 so as to be relatively rotatable and meshed with the 4th-speed drive gear 164. Consisting of.

  Between the second speed driven gear 161 and the fourth speed driven gear 165, the counter shaft 107 is engaged with the second speed driven gear 161, the fourth speed driven gear 165 is engaged, and A first shifter 166 that can be switched between a state in which it is not engaged with either the second speed driven gear 161 or the fourth speed driven gear 165 is supported so as not to be relatively rotatable and axially movable. The shifter 166 is integrally provided with a sixth speed driven gear 163. The fourth speed drive gear 164 is integrally provided with a second shifter 167 that is supported by the first main shaft 105 so as not to rotate relative to the first main shaft 105 and to be movable in the axial direction. The engagement and disengagement with the drive gear 162 can be switched.

  Thus, the second speed gear train G2 is established by engaging the first shifter 166 with the second speed driven gear 161 without engaging the second shifter 167 with the sixth speed driving gear 162, By engaging the first shifter 166 with the fourth-speed driven gear 165 without engaging the second shifter 167 with the sixth-speed drive gear 162, the fourth-speed gear train G4 is established, and the first shifter is established. The sixth gear train G6 is established by engaging the second shifter 167 with the sixth-speed drive gear 162 with the 166 in the neutral state.

  Between the protrusion of the second main shaft 106 from the other end of the first main shaft 105 and the counter shaft 107, the first gear train G1 and the fifth gear train are arranged in order from the side opposite to the clutch device 102. G5 and the third speed gear train G3 are provided so as to be aligned. The third-speed gear train G3 is supported by the second main shaft 106 so as to be axially movable and supported by the third-speed drive gear 168, which is supported so as not to rotate relative to the second main shaft 106, and the countershaft 107, so as to be relatively rotatable. The fifth-speed gear train G5 includes a third-speed driven gear 169 that meshes with the third-speed drive gear 168, and the fifth-speed gear train G5 is supported on the second main shaft 106 so as to be relatively rotatable. And a fifth-speed driven gear 171 that is supported by the countershaft 107 in the axial direction while being relatively non-rotatable and meshes with the fifth-speed drive gear 170. The first-speed gear train G1 includes: The first-speed drive gear 172 provided integrally with the second main shaft 106 and the first-speed driven gear 17 that is rotatably supported by the counter shaft 107 and meshes with the first-speed drive gear 172. Consisting of.

  The third-speed drive gear 168 is integrally provided with a third shifter 174 that is supported by the second main shaft 106 so as not to rotate relative to the second main shaft 106 and to be axially movable. The third shifter 174 is a fifth-speed drive gear. The engagement and disengagement of the gear can be switched. Between the third-speed driven gear 169 and the first-speed driven gear 173, the countershaft 107 is engaged with the third-speed driven gear 169, is engaged with the first-speed driven gear 173, and A fourth shifter 175 that can switch a neutral state that is not engaged with any of the third-speed driven gear 169 and the first-speed driven gear 173 is supported so as to be non-rotatable and axially movable. The fourth shifter 175 is integrally provided with a fifth speed driven gear.

  Thus, by engaging the fourth shifter 175 with the first-speed driven gear without engaging the third shifter 174 with the fifth-speed drive gear, the first-speed gear train G1 is established, By engaging the fourth shifter 175 with the third-speed driven gear 169 without engaging the shifter 174 with the fifth-speed drive gear, the third-speed gear train G3 is established, and the fourth shifter 175 is neutralized. By engaging the third shifter 174 with the fifth-speed drive gear as a state, the fifth-speed gear train G5 is established.

  The first to fourth shifters 166, 167, 174, and 175 are rotatably held by the first to fourth shift forks 176, 177, 178, and 179, and these shift forks 176 to 179 are both main shafts. The first to fourth shifters 166, 167, 174, and 175 operate in the axial direction by being driven in the axial direction of the 105 and 106 and the counter shaft 107.

  In FIG. 10, first to fourth shift forks 176 to 179 are engaged with the outer periphery of a shift drum 180 that has an axis parallel to the axis of the crankshaft 36 and is rotatably supported by the crankcase 35. The shift forks 176 to 179 are slidably supported on shift fork shafts 205 and 206 that are supported by the crankcase 35 and have an axis parallel to the shift drum 180, and the shift forks 176 to 179 shift as the shift drum 180 rotates. The slide operation is performed on the fork shafts 205 and 206.

  The shift drum 180 is rotationally driven by the power exerted by the shift drive electric motor 181 that is a shift actuator. The shift drive electric motor 181 is attached to the side surface of the crankcase 35. In this embodiment, the engine main body 33 is mounted on the left or right side surface of the crankcase 35, for example, the left side surface when the engine body 33 is mounted on the body frame F. In addition, the first and second gear covers 116 and 117 are detachably attached to the left side surface of the crankcase 35 so as to cover the shaft end of the countershaft 107 in the gear transmission mechanism 103. The electric motor 181 is disposed above the first and second gear covers 116 and 117 and inside the outer ends of the first and second gear covers 116 and 117 along the axis of the counter shaft 107. A generator cover 87 is attached to the left side surface of the crankcase 35. The shift driving electric motor 181 is disposed behind the generator cover 87 as shown in FIG. As shown by 10, it is arranged inside the outer end of the generator cover 87 along the axis of the shift drum 180, that is, the axis of the crankshaft 36.

  In addition, as shown in FIG. 2, the shift driving electric motor 181 has its operating axis, that is, the rotational axis C1, disposed in a plane perpendicular to the axial direction of the gear transmission mechanism 103 and inclined in the vertical direction. In this embodiment, it is attached to the left side surface of the crankcase 35 in a state of being inclined upward.

  Referring also to FIG. 11, the power exerted by the shift drive electric motor 181 is shifted through the reduction gear mechanism 182, the barrel cam 183, the disc-shaped transmission rotation member 184, the transmission shaft 185, and the lost motion spring 186. It is transmitted to the drum 180.

  A case member 188 is formed on the left side surface of the crankcase 35. The case member 188 is formed between the crankcase 35 and an operating chamber 187 that accommodates the reduction gear mechanism 182, the barrel cam 183, and the transmission rotation member 184. A lid member 189 is attached to the case member 188 so as to close the open end of the 188. Thus, the shift driving electric motor 181 is attached to the case member 188 so that the motor shaft 190 enters the working chamber 187.

  The gear reduction mechanism 182 includes a drive gear 192 provided on the motor shaft 190 of the shift drive electric motor 181, a first intermediate gear 193 that meshes with the drive gear 192, and a second rotation that rotates together with the first intermediate gear 193. An intermediate gear 194 and a driven gear 195 that is provided on the barrel cam 183 and meshes with the second intermediate gear 194.

  The first and second intermediate gears 193 and 194 are provided on a rotating shaft 196 whose both ends are rotatably supported by the case member 188 and the lid member 189, and both ends of the barrel cam 183 are connected to the case member 188 and The lid member 189 is rotatably supported.

  A spiral cam groove 197 is provided on the outer periphery of the barrel cam 183. On the other hand, the transmission rotation member 184 is disposed opposite to the outer periphery of the barrel cam 183 so as to be able to rotate about the same axis as the shift drum 180, and selectively engages with the cam groove 197 on the transmission rotation member 184. A plurality of engaging pins 198, 198... That can be provided are provided at equal intervals in the circumferential direction. Thus, the plurality of engaging pins 198, 198... Are sequentially engaged with the cam groove 197 in accordance with the rotation of the barrel cam 183, whereby the rotational power is transmitted to the transmission rotating member 184.

  One end of a transmission shaft 185 that passes through the shift drum 180 coaxially and relatively rotatably is coupled to the transmission rotation member 184 coaxially and in a relatively non-rotatable manner. The other end of the transmission shaft 185 and the shift drum A lost motion spring 186 is provided between the other end portions of 180, and the rotational force generated by the rotation of the transmission shaft 185 is transmitted to the shift drum 180 via the lost motion spring 186.

  A shift sensor 199 is attached to the case member 188 in order to detect the rotational position of the shift drum 180, and the detection shaft 200 of the shift sensor 199 is rotatably supported by the case member 188.

  Thus, the third intermediate gear 202 is engaged with the drive gear 201 that rotates together with the shift drum 180, and the driven gear 204 provided on the detection shaft 145 is engaged with the fourth intermediate gear 203 that rotates together with the third intermediate gear 202. Is done.

  2, a water pump 208 is attached to the left side surface of the crankcase 35 below the generator cover 87, and the first and second oil pumps 209, 210 are installed in the crankcase 35. The scavenging pump 211 is accommodated coaxially with the water pump 208, and the first and second oil pumps 209, 210 and the scavenging pump 211 rotate together with the water pump 208. Thus, the rotational power from the driven gear 129 of the primary reduction gear 101 is transmitted to the water pump 208, the first and second oil pumps 209 and 210, and the scavenging pump 211 via the endless chain 212. As shown in FIGS. 8 and 9, a drive sprocket 213 engaged with the driven gear 129 is rotatably supported by the first main shaft 105, and a water pump 208, first and second oils are supported. The chain 212 is wound around a driven sprocket 214 connected in common to the pumps 209 and 210 and the scavenging pump 211 and the drive sprocket 213.

In FIG. 12, the first oil pump 209 switches between connection and disconnection of the first and second clutches 124 and 125 in the clutch device 102, and the intake side valve operation mode changing mechanism 63 and the exhaust side in the rear bank side valve operating device 48R. The hydraulic pressure for switching the valve operating mode changing mechanism 64 is discharged. The oil pumped up from the oil pan 41 and discharged from the first oil pump 209 passes through the oil passage 215 of the first oil passage 234 . To the first oil filter 216, and a relief valve 217 is connected to the oil passage 215. The purified oil in the first oil filter 216 flows divided into first and second branched oil passages 218 and 219 branched into two on the downstream side of the first oil passage 234, the first branched oil passage 218 is connected to a clutch control device 220 for switching between connection and disconnection of the clutch device 102, and the second branch oil passage 219 is an intake side valve operation mode change mechanism 63 and an exhaust side valve operation mode in the rear bank side valve operating device 48R. It is connected to a valve operating hydraulic control device 221 that performs switching operation of the change mechanism 64, and a pressure reducing valve 222 is interposed in the second branch oil passage 219.

The second oil pump 210 is for supplying lubricating oil to each lubricating portion of the engine E, and the oil pumped up from the oil pan 41 and discharged from the second oil pump 210 is a second oil passage. 223 is connected to the second oil filter 225, and a relief valve 224 is connected to the second oil passage 223. The oil purified by the first oil filter 225 is guided to an oil passage 228 provided with an oil cooler 226, and a pressure sensor 227 is connected to the oil passage 228.

  Oil from the oil passage 228 is supplied to the lubricating portion 229 around the first and second main shafts 105 and 106 in the gear transmission mechanism 103, the lubricating portion 230 around the counter shaft 107 in the gear transmission mechanism 103, and the engine body 33. It is supplied to the plurality of lubrication units 231. In addition, oil from the lubricating portion 229 around the first and second main shafts 105 and 106 is guided to the first oil passage 140 that communicates with the canceller chamber 137 in the first clutch 124. The oil from the lubrication part 231 is supplied to the second oil passage 150 leading to the canceller chamber 149 in the second clutch 125 through the throttle 232, and is used to quickly supply oil to the canceller chamber 149. An electromagnetic on-off valve 233 is connected in parallel to the throttle 232.

  Referring to FIGS. 13 and 14 together, the clutch control device 220 includes a first electromagnetic control valve 235 for switching the action and release of the hydraulic pressure to the first hydraulic chamber 137 in the first clutch 124, and the second clutch 125. And a second electromagnetic control valve 236 that switches between the action and release of the hydraulic pressure to the second hydraulic chamber 147 and is arranged on the right side of the front cylinder block 38F of the front bank BF and is arranged on the outer surface of the clutch cover 92. The clutch device 102 is attached and disposed outward from the clutch device 102 as viewed from the direction along the axis of the clutch device 102. That is, the clutch cover 92 has a protruding portion 92a protruding outward so as to accommodate the clutch device 102 at a position corresponding to the clutch device 102, and from the protruding portion 92a to the right side of the front cylinder block 38F. An extending portion 92b is provided, and the clutch control device 220 is attached to the extending portion 92b.

  Moreover, the first and second electromagnetic control valves 235 and 236 constituting the clutch control device 220 are arranged at different positions in the front-rear direction and the vertical direction as clearly shown in FIG. In addition, of the first and second electromagnetic control valves 235 and 236, the second electromagnetic control valve 236 is disposed above the first electromagnetic control valve 235, above the crankshaft 36, and below the first electromagnetic control valve 235. At least a portion of the control valve 235, in this embodiment, most is disposed in front of the crankshaft 36.

  Further, as shown in FIG. 15, the clutch device 102 is attached to the outer surface of the extension portion 92b in the clutch cover 92 so as to be positioned on the innermost side of the outermost end of the clutch cover 92, that is, the tip end of the protruding portion 92a. .

  The clutch cover 92 includes an oil passage 237 connecting the first oil passage 154 communicating with the first hydraulic chamber 137 of the first clutch 124 and the first electromagnetic control valve 235, and a second hydraulic chamber 147 of the second clutch 125. A second oil passage 157 that communicates with an oil passage 238 that connects the second electromagnetic control valve 236 is provided.

  Paying attention to FIG. 14, the first oil filter 216 is disposed on the side opposite to the side stand 34 in the width direction of the vehicle body frame F, and includes the axis C2 of the crankshaft 36 and the axis of the clutch device 102. The clutch cover 92 is disposed below the axes C2 and C3 with respect to C3.

  The filter case 239 of the first oil filter 216 protrudes outward from the crankcase 35 of the engine body 33, and is formed into a cylindrical shape that forms a bottomed accommodation hole 240 with the outer end open. A lid member 241 that is integrally formed and closes the outer end opening of the accommodation hole 240 is fastened to the filter case 239.

  A cylindrical filter medium 243 is supported on a support frame 242 that is sandwiched between the inner end blocking portion of the accommodation hole 240 and the lid member 241 and accommodated in the filter case 239. Thus, an annular unpurified chamber 244 is formed around the filter medium 243, and a purified chamber 245 is formed in the filter medium 243.

  Such a first oil filter 216 has at least a part of the filter medium 243 that is a component of the first oil filter 216 projecting outward from the outer surface of the clutch cover 92 in a direction along the axis of the crankshaft 36 and in the clutch cover 92. The protrusion 92a is located on the inner side of the outermost end of the projection 92a, and is located below the crankshaft 36 and outside the clutch device 102 as viewed from the direction along the axis of the clutch device 102, in this embodiment in FIG. As shown in FIG.

  As clearly shown in FIG. 13, the first oil filter 216 has a clutch cover so that a part thereof overlaps the water pump 208, the first and second oil pumps 209 and 210, and the scavenging pump 211 in a side view. 92.

  By the way, when viewed in a direction orthogonal to the axis of the crankshaft 36 and the clutch device 102, the first oil filter 216 is from a vertical line L1 passing through the axially outer end 102a of the clutch device 102 as shown in FIGS. 13 and the vertical line L2 passing through the foremost end 102b of the clutch device 102 passes through the first oil filter 216 in a side view in the direction along the axis of the crankshaft 36 and the clutch device 102 as shown in FIG. Be placed. As a result, the first oil filter 216 is disposed inward of the axially outer end 102a of the clutch device 102 so as to overlap a part of the clutch device 102 in plan view.

  A connection member 246 is fastened to the inner surface of the clutch cover 92 at a portion corresponding to the first oil filter 216. On the other hand, an oil passage forming member 247 is fastened to the inner surface of the clutch cover 92 in the vicinity of the clutch control device 220 with a flat partition wall member 248 sandwiched between the oil cover forming member 247 and the oil passage forming member 247. An oil passage 249 is formed between the partition wall member 248 and the partition wall member 248. Thus, the connection member 246 forms a connection oil passage 250 that communicates with the purification chamber 245 of the first oil filter 216, and one end of a connection pipe 251 that extends toward the oil passage formation member 247 is connected to the connection oil passage 250. Closely fitted. The other end of the connection pipe 251 is fitted to a joint member 252, and the joint member 252 is fluid-tightly fitted to a cylindrical fitting cylinder portion 248 a provided on the partition wall member 248. Also, oil passages 253 and 254 that connect the oil passage 249 between the oil passage forming member 247 and the partition member 248 and the first and second electromagnetic control valves 235 and 236 are provided in the clutch cover 92.

  Therefore, the purification chamber 245 of the first oil filter 216 is connected to the connection oil passage 250, the connection pipe 251, the joint member 252, the oil passage 249, and the oil passages 253 and 254. 251, the joint member 252, the oil passage 249, and the oil passages 253 and 254 constitute the first branch oil passage 218 described with reference to FIG.

  An oil passage 215 connecting the unpurified chamber 244 of the first oil filter 216 and the discharge port of the first oil pump 209 is connected to an oil passage 255 provided in the crankcase 35 through the discharge port of the first oil pump 209, and The connecting pipe 256 connects the oil passage 255 and the unpurified chamber 244, and both ends of the connecting pipe 256 are liquid-tightly fitted to the end of the oil passage 255 and the clutch cover 92.

  The valve housing 257 of the pressure reducing valve 222 is coupled to the clutch cover 92 together with the connection member 246 so as to sandwich the connection member 246 between the inner surface of the clutch cover 92. The pressure reducing valve 222 is slidably fitted with a valve body 259 so as to form an oil chamber 258 between one end of the valve housing 257, and a spring receiving member provided on the other end side of the valve housing 257. A spring 260 for biasing the valve body 259 is provided between the valve body 267 and the valve body 259 on the side of reducing the volume of the oil chamber 258.

  Thus, the connecting member 246 and the valve housing 257 are provided with a passage 261 connecting the oil passage 250 in the connecting member 246 and the oil chamber 258, and this passage 261 is the first and second branch oil passages. It becomes a branch point of 218,219.

  The pressure reducing valve 222 is configured to reduce the oil pressure of the oil chamber 258 uniformly by reciprocally sliding the valve body 259 so that the oil pressure by the oil pressure of the oil chamber 258 and the spring force of the spring 260 are balanced. The hydraulic pressure reduced by the pressure reducing valve 222 is guided to the valve operating hydraulic control device 221 side.

  With the arrangement of the pressure reducing valve 222, the pressure reducing valve 222 is arranged in the immediate vicinity of the first oil filter 216. Moreover, as clearly shown in FIG. At least a part of the pressure reducing valve 222 is disposed so as to overlap the first oil filter 216.

  The valve operating hydraulic control device 221 includes a pair of electromagnetic control valves 262 and 262 individually corresponding to the two cylinders in the rear bank BR. The left side surface of the rear cylinder head 39R in the rear bank BR. Mounted on.

  Thus, one electromagnetic control valve 262 controls the hydraulic pressure of the intake side and exhaust side valve operation mode changing mechanisms 63 and 64 in one of the two cylinders, and the other electromagnetic control valve 262 is the intake side in the other cylinder. And the hydraulic pressure of the exhaust side valve operation mode changing mechanisms 63 and 64 is controlled.

  The oil decompressed by the pressure reducing valve 222 is connected to the valve housing 257 at one end and extending to the side away from the clutch cover 92, and is connected to the other end of the connecting tube 264 and to the left side of the crankcase 35. An oil passage 265 provided in the crankcase 35 so as to extend to the surface, and provided on the left side of the crankcase 35, the rear cylinder block 38R and the rear cylinder head 39R. The second branch oil passage 219, which is led to the valve operating hydraulic control device 221 through the oil passage 266 connecting the two 221, is provided with the connecting pipe 264 and the oil passage. 265, 266.

  The second oil filter 225 is attached to the right side surface of the crankcase 35 in front of the first oil filter 216.

  Next, the operation of this embodiment will be described. The shift drive electric motor 181 that drives and controls the shift operation of the gear transmission mechanism 103 is attached to the left side surface of the crankcase 35 and is disposed around the crankcase 35. The degree of freedom in layout of the functional components can be increased, and the shift drive electric motor 181 can be easily accessed from the outside of the power unit P, so that the maintainability of the shift drive electric motor 181 can be improved. Further, since the operation axis C1 of the shift drive electric motor 181 is disposed on a plane orthogonal to the axial direction of the gear transmission mechanism 103, the shift drive electric motor 181 is attached to the left side surface of the crankcase 35. Regardless, it is possible to minimize the amount of shift drive electric motor 181 protruding outward from crankcase 35 as much as possible.

  The shaft end of the counter shaft 107 of the gear transmission mechanism 103 is covered with first and second gear covers 116 and 117 that are detachably attached to the left side surface of the crankcase 35, and the shift driving electric motor 181 is Since it is attached to the left side surface of the crankcase 35 so as to be positioned above the first and second gear covers 116 and 117 and inside the first and second gear covers 116 and 117 along the axis of the countershaft 107. The first and second gear covers 116 and 117 can protect the shift drive electric motor 181 actuator from stepping stones, muddy water, etc. from below, and no special parts are required to protect the shift drive electric motor 181. As a result, the number of parts can be reduced. In addition, since there is no need to provide a boss or the like for attaching a protective cover around the shift drive electric motor 181, restrictions on the layout of other parts due to the boss or the like are eliminated, and the degree of freedom in layout of other parts is increased. be able to.

  Further, a generator cover 87 is attached to the left side surface of the crankcase 35, but the shift drive electric motor 181 is located behind the generator cover 87 and along the axis of the crankshaft 36. The shift drive electric motor 181 can be disposed by effectively utilizing the space around the generator cover 87 protruding from the left side surface of the crankcase 35 because it is located inside the outer end of the 87. The arrangement of the electric motor 181 can prevent the power unit P from becoming large in the direction along the axis of the crankshaft 36. In addition, the generator cover 87 can protect the shift drive electric motor 181 from flying stones, muddy water, and the like from the front, eliminating the need for dedicated parts for protecting the shift drive electric motor 181 and reducing the number of parts. it can. In addition, since there is no need to provide a boss or the like for attaching a protective cover around the shift drive electric motor 181, restrictions on the layout of other parts due to the boss or the like are eliminated, and the degree of freedom in layout of other parts is increased. be able to.

  Further, since the operating axis C1 of the shift drive electric motor 181 is inclined in the vertical direction, the generator cover 87 located in the front does not get in the way when the shift drive electric motor 181 is attached and detached. Maintenance can be improved.

  A clutch cover 92 that accommodates the clutch device 102 is coupled to the right side surface of the crankcase 35, and the clutch control device 220 that switches and controls the connection / disconnection operation of the clutch device 102 is a front cylinder block in the front bank BF. Since it is attached to the outer surface of the clutch cover 92 so as to be disposed on the right side of the 38F, it is easy for the traveling wind to hit the clutch control device 220, improving the cooling performance and increasing the longitudinal length of the engine body 33. It can be avoided. Moreover, since it is relatively rare for vehicle components such as the intake system parts and the vehicle body frame F to be disposed in the portion corresponding to the outer surface of the clutch cover 92, the clutch control device 220 is attached to the outer surface of the clutch cover 92. As a result, the degree of freedom in designing the intake system parts, the body frame F, and the like can be improved.

  Moreover, the clutch device 102 is configured in a twin type having the first and second clutches 124 and 125, and the clutch control device 220 controls the first and second clutches 124 and 125 separately. The first and second electromagnetic control valves 235 and 236 are provided. In addition, since the first and second electromagnetic control valves 235 and 236 are arranged at different positions in the front-rear direction and the vertical direction, the first and second electromagnetic control valves 235 and 236 are easy to hit the traveling wind and have excellent cooling performance. Obtainable.

  In addition, of the first and second electromagnetic control valves 235 and 236, the second electromagnetic control valve 236 is disposed above the first electromagnetic control valve 235 and above the crankshaft 36, and at least of the first electromagnetic control valve 235. Since a part (most part in this embodiment) is arranged in front of the crankshaft 36, the clutch is held in a space from above the crankshaft 36 to the front where there is a larger space between the crankshaft 36 and the clutch device 102. The control device 220 can be arranged, and the crankshaft 36 and the clutch device 102 can be arranged close to each other, and the traveling wind can easily hit the first and second electromagnetic control valves 235 and 236.

  Since the clutch control device 220 is disposed on the inner side of the outermost end of the clutch cover 92, the protrusion of the clutch control device 220 to the right side of the crankcase 35 can be suppressed as much as possible. You don't have to worry about corners.

  Furthermore, since the clutch control device 220 is disposed outward from the clutch device 102 when viewed from the direction along the axis of the clutch device 102, the clutch control device 220 is avoided by avoiding the clutch device 102 that protrudes most to the right side of the crankcase 35. By attaching 220 to the outer surface of the clutch cover 92, it is possible to prevent the power unit P from increasing in size in the left-right direction as much as possible.

  In addition, oil passages 237 and 238 that connect the clutch device 102 that is a hydraulic type and the clutch control device 220 that controls the hydraulic pressure that acts on the clutch device 102 are provided in the clutch cover 92, so the oil passages 237 and 238 are provided. Can be shortened and simplified, and the maintainability of the mechanism for controlling the clutch device 102 can be improved.

  By the way, the clutch cover 92 is provided with a first oil filter 216, and the first oil filter 216 is between the axis line of the crankshaft 36 and the axis lines C2 and C3 of the clutch device 102. It is arranged below. Accordingly, the first oil filter 216 can be disposed by effectively utilizing the space generated between the crankshaft 36 and the clutch device 102, and the inner diameter and timing transmission of the cylinder bore 42 above the crankshaft 36 can be arranged. The degree of freedom in designing the parts above the crankshaft 36 such as the arrangement of the mechanisms 95 and 98 can be ensured. In addition, since the lower position between the axis C2 of the crankshaft 36 and the axis C3 of the clutch device 102 has a space on the inner side of the engine body 33, there is no restriction on the degree of freedom in arrangement of other parts. Protrusion of the first oil filter 216 in the direction along the axis of the crankshaft 36 can be suppressed. Further, since the first oil filter 216 is below the crankshaft 36, the center of gravity of the motorcycle can be lowered.

  Further, since the first oil filter 216 is disposed inward of the outer end 102a in the axial direction of the clutch device 102 so as to overlap a part of the clutch device 102 in a plan view, the first oil filter 216 The attachment can prevent the power unit P from becoming larger in the axial direction of the crankshaft 36, and the influence of the protrusion of the first oil filter 216 from the clutch cover 92 can be prevented from affecting the bank angle.

  Further, the first oil filter 216 projects at least a part of the filter medium 243 that is a component of the first oil filter 216 outward from the outer surface of the clutch cover 92 in a direction along the axis of the crankshaft 36. Since it is disposed below the shaft 36 and outside the clutch device 102 as viewed from the direction along the axis of the clutch device 102, traveling air can easily hit the first oil filter 216, and the first oil filter 216 is cooled. Can increase the sex.

  In addition, since the first oil filter 216 is disposed so as to partially overlap the water pump 208, the first and second oil pumps 209, 210, and the scavenging pump 211 in a side view, the first oil pump 209 and the first oil filter 216 The oil path 215 connecting the first oil pump 209 and the first oil filter 216 by arranging the one oil filter 216 close to each other can be shortened and simplified.

  In addition, since the clutch cover 92 is provided with oil passages 237 and 238 that connect the clutch device 102 and the clutch control device 220 that controls the hydraulic pressure applied to the clutch device 102, the clutch control device 220, the clutch device 102, By arranging oil passages 237 and 238 connecting the clutch control devices 220 together in the clutch cover 92, the oil passages 237 and 238 can be shortened and simplified, and the clutch device 102 is controlled. The workability of the mechanism maintenance can be improved.

In addition, since the first oil filter 216 is disposed on the side opposite to the side stand 34 in the width direction of the vehicle body frame F, work such as maintenance of the first oil filter 216 in a parked state of the motorcycle with the side stand 34 upright. Can increase the sex.

  Further, a pressure reducing valve 222 is interposed in the second branch oil passage 219 connecting the first oil filter 216 and the valve operating hydraulic control device 221, and this pressure reducing valve 222 is disposed in the immediate vicinity of the first oil filter 216. Therefore, it is possible to arrange the pressure reducing valve 222 and the first oil filter 216 in a compact manner while efficiently using the necessary hydraulic pressure.

  A substantially cylindrical filter case 239 of the first oil filter 216 is attached to the crankcase 35 so as to protrude outward from the crankcase 35, and at least the pressure reducing valve 222 is viewed from the axial direction of the filter case 239. Since a part of the first oil filter 216 is disposed so as to overlap, the pressure reducing valve 222 and the first oil filter 216 can be disposed closer to each other, and the power unit P can be made more compact.

  Further, since the first oil filter 216 and the pressure reducing valve 222 are provided in the clutch cover 92 attached to the crankcase 35, the assembling property can be improved. Further, using the same engine body 33, it is easy to make a separate power unit P having the pressure reducing valve 222 and the first oil filter 216 and a power unit not having the pressure reducing valve and the oil filter.

In addition, the downstream side of the first oil passage 234 extending from the discharge port of the first oil pump 209 branches into the first and second branch oil passages 218 and 219, and the intake side and exhaust side valve operation mode changing mechanisms 63 and 64. In addition, since the first and second clutches 124 and 125 of the clutch device 102 are connected in common, an increase in the bulk of the power unit P is suppressed, and the intake side and exhaust side valve operation mode changing mechanisms 63 and 64 and the clutch device 102 are suppressed. The hydraulic system related to can be made compact, and a power unit P suitable for a motorcycle can be obtained.

Branched from the first oil pump 209 was or clutch control device 220 and of the first and second branched oil passages 218 and 219 connected to the valve-moving hydraulic pressure control device 221 the pressure reducing valve in the middle of the second branch oil channel 219 Since 222 is interposed, the hydraulic system can be combined appropriately and efficiently by applying appropriate hydraulic pressure to the clutch control device 220 and the valve operating hydraulic control device 221.

  In addition, the intake side and exhaust side valve operation mode changing mechanisms 63 and 64 can be switched at a lower hydraulic pressure than the clutch device 102, and the discharge hydraulic pressure of the first oil pump 209 is reduced by the pressure reducing valve 222 and supplied. Therefore, it is possible to apply appropriate hydraulic pressures to the intake side and exhaust side valve operation mode changing mechanisms 63 and 63 and the clutch device 102, respectively.

  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. It is.

1 is a left side view of a motorcycle. It is a left view of a power unit. It is a right view of a power unit. FIG. 4 is a cross-sectional view taken along line 4-4 of FIG. FIG. 5 is a sectional view taken along line 5-5 of FIG. FIG. 6 is a cross-sectional view corresponding to FIG. 5 on the rear bank side. It is a principal part expanded sectional view of FIG. It is a longitudinal cross-sectional view of a gear transmission mechanism and a clutch apparatus. It is a principal part enlarged view of FIG. FIG. 10 is an enlarged sectional view taken along line 10-10 of FIG. It is the 11-11 line sectional view of FIG. It is a systematic diagram which shows the structure of a hydraulic system. It is a principal part enlarged view of FIG. FIG. 14 is a cross-sectional view taken along line 14-14 of FIG. FIG. 15 is a view taken along arrow 15 in FIG. 13.

35 ... Crankcase 36 ... crankshaft 44 ... engine valve in which an intake valve 45 ... engine exhaust valves 48R ··· valve gear 63, 64 ··· valve operation mode changing device Structure
102 ... twin clutches 103 ... transmission structure
124 ... 1st clutch
125 ... second clutch 209 ... first oil pump
210 ... second oil pump 21 8 - ... first branched oil passage
219: Second branch oil passage 222: Pressure reducing valve
223 ... Second oil passage
234 ... first oil passage
E ... Engine P ... Power unit

Claims (1)

A valve operating device (48R) provided on the engine (E) for opening and closing the engine valves (44, 45) of a plurality of cylinders of the engine (E), and a part of the valve operating device (48R) attached to the valve operating device (48R) engine valves of the cylinders and switchable hydraulic actuation embodiments the opening and closing state and the closed rest state of the valve operation mode changing mechanism (44, 45) (63,64), each switchable connection and disconnection with a hydraulic And a twin clutch device (102) interposed between the crankshaft (36) of the engine (E ) and the transmission mechanism (103). A power unit for a small vehicle,
The valve operating mode changing mechanism (63, 64) and the hydraulic pressure for switching the connection and disconnection of the first and second clutches (124, 125) are set to the valve operating mode changing mechanism (63, 64) and the first. A first oil pump (209) that supplies the first and second clutches (124, 125), respectively, and a second oil pump (210) that supplies lubricating oil to each lubricating part of the engine (E), It is accommodated coaxially in the crankcase (35) so as to be driven by power transmission from the crankshaft (36) ,
A downstream side of the first oil passage (234) extending from the discharge port of the first oil pump (209) includes a first branch oil passage (218) connected to the first and second clutches (124, 125), The second branch oil passage (219) branches to the second branch oil passage (219) connected to the valve operation mode changing mechanism (63, 64), and the second branch oil passage (219, 219) out of the first and second branch oil passages (218, 219). ) Is provided only at the pressure reducing valve (222),
A discharge port of the second oil pump (210) and each lubrication part of the engine (E) are connected by a second oil passage (223) independent of the first oil passage (234). A power unit for a small vehicle.

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