CN101469639A - Internal combustion engine - Google Patents

Abstract

The invention relates to an internal combustion engine, which harbors a crankshaft and a transmission in a crank case; wherein the transmission is provided with a plurality of gears for gear shift; furthermore, the transmission is provided with an input shaft for inputting the rotary power of an input crankshaft and an output shaft for transmitting the rotary power of the crankshaft through the gear from the input shaft and further transmitting the rotary power to a driving wheel. Rotation detection devices (401, 402) for detecting the rotating speed of the transmission and the gears (49c, 49d) with fixed axial position which are linked with the input shaft (28) oppositely configure detection parts (401a, 402a) of the rotation detection devices. Hence, the internal combustion engine with the rotation detection devices can detect the rotating speed of the transmission gear without increasing the axial width dimension of the gear, applying expensive sensors with high detection sensitivity or restricting the degree of freedom of the configuration of a variable-speed drum.

Description

Internal-combustion engine

Technical field

The present invention relates to a kind of internal-combustion engine with rotation detecting of the gear rotational speed of returning to detect speed changer.

Background technique

Known such rotation detecting (for example with reference to patent documentation 1), the speed changer that has a plurality of gears (solid of rotation) on the axle is set at the rear of crankcase, towards axially movable gear turn-sensitive device is set accordingly in a plurality of gears of this rotation detecting and speed changer, by the rotating speed of this turn-sensitive device measuring gear, detect the rotating speed of the axle of speed changer thus.

[patent documentation 1] TOHKEMY 2000-87780 communique

Yet, in formation in the past, owing to turn-sensitive device is set at axially movable gear towards speed changer, so, must increase the axial width dimension of gear, or use the sensor etc. of the high costliness of detection sensitivity, even but so that this gear moves the also rotating speed of measuring gear.

Summary of the invention

Therefore, the object of the present invention is to provide a kind of internal-combustion engine with rotation detecting, this rotation detecting can be eliminated the problem that above-mentioned prior art exists, do not increase the axial width dimension of gear, do not use the high expensive sensor of detection sensitivity, just can detect the gear rotational speed of speed changer.

In order to achieve the above object, internal-combustion engine of the present invention is accommodated bent axle and speed changer in crankcase, this speed changer has the gear that a plurality of speed changes are used, and, this speed changer has the input shaft of the rotating power of importing bent axle and also this rotating power is delivered to the output shaft of driving wheel from this input shaft by the rotating power of gear transmission bent axle; It is characterized in that: have the rotation detecting of the rotating speed of the gear that detects above-mentioned speed changer, and with the rotation interlock of above-mentioned input shaft and dispose the detection unit of this rotation detecting opposite to each other at the gear that axially is positioned.

The detection unit of rotation detecting and the relative axial position of gear relation in the present invention, the detection unit of rotation detecting be configured to the gear of having fixed axial position opposite to each other, so can not change.For this reason, do not increase the facewidth of gear, can detect rotating speed, so, can be in the increase of the width dimensions of the axial inhibition internal-combustion engine of speed changer.In addition, owing to detect rotating speed with the gear of the rotation interlock of input shaft, so, can detect input shaft rotational speed.

For this reason, for example undertaken to detect the switching of speed change in the self-shifting vehicle by drive unit like that, can hold the self-shifting state by good precision as AMT (Automated Mannual Transmission, mechanical automatic gearbox).

In this occasion, the gear that is detected rotating speed by rotation detecting also can be near the gear of the axial arrangement central authorities of the axle of above-mentioned speed changer.

Generally speaking, the axle head of speed changer is supported on crankcase by bearing, so, during near the gear that rotating speed is detected is set at axle head gear,, must outer side dispose this bearing in order to ensure the space that rotation detecting is set, corresponding therewith, big, internal-combustion engine maximization that axial length becomes.

In this formation and since the gear that rotating speed is detected in axial arrangement near the axle central authorities of speed changer, so rotation detecting is configured to the position of leaving from bearing, do not need to increase axial length, the maximization of internal-combustion engine is suppressed.

Also above-mentioned rotation detecting can be disposed at above-mentioned crankcase.

By above-mentioned rotation detecting is disposed at crankcase, can not be provided for the other housing of turn-sensitive device etc.

Also above-mentioned rotation detecting can be disposed at the back of above-mentioned crankcase.

For example, in the occasion that rotation detecting is disposed at above the crankcase, can apply restriction to the configuration of components degrees of freedom that is positioned at exhaust system above the crankcase or air inlet system, and in this formation, owing to rotation detecting is disposed at the back of crankcase, so, can improve the configuration of components degrees of freedom of exhaust system or air inlet system.

The gear that detects rotating speed by above-mentioned rotation detecting also can be and is arranged at the gear that more is in the output shaft at rear than input shaft, in this gear and the gear of being located at input shaft, diameter is meshed than the big gear of gear in the diameter minimum of input shaft.

Generally speaking, with the gear on the output shaft of being in, because diameter is bigger than other gear that is on the output shaft in the gear engagement of the diameter minimum of input shaft, so, when detecting this gear, rotation detecting is outstanding more towards the rear of internal-combustion engine, and the front and back length of internal-combustion engine is elongated.

In this formation, since with the gear of being located at input shaft in, diameter is provided with rotation detecting than on the gear of the big gear engagement of the gear of the diameter minimum on the input shaft, so, can suppress the overhang of rotation detecting towards the internal-combustion engine rear, realize the miniaturization of internal-combustion engine.

Above-mentioned input shaft has first input shaft and second input shaft, on the axle of above-mentioned first input shaft, dispose first clutch, and on the axle of above-mentioned second input shaft, dispose second clutch, can make the rotating power of above-mentioned bent axle cut off and connect to the transmission of above-mentioned input shaft by the action of this a pair of clutch, above-mentioned rotation detecting can detect first input shaft rotational speed and second input shaft rotational speed ground respectively corresponding to the gear of the rotation interlock of first input shaft be provided with a plurality of with the gear of the rotation interlock of second input shaft.

This formation is applicable to the vehicle of the clutch device that has carried double-clutch type.In this vehicle, because the detection unit of rotation detecting is configured to the gear that axial position has been fixed respectively opposite to each other, so the detection unit of rotation detecting concerns with the relative axial position of gear and can not change.For this reason, the facewidth that does not increase gear can detect rotating speed, so, can increase at the width dimensions of the axial inhibition internal-combustion engine of speed changer.In addition, because the rotating speed of the gear of the rotation interlock of detection and input shaft, so, input shaft rotational speed can be detected.For this reason, for example as AMT, undertaken to detect the switching of speed change in the self-shifting vehicle, can hold the self-shifting state by good precision by drive unit.

In addition, detecting the gear of rotation of first input shaft and the gear that detects the rotation of second input shaft also can be at axial adjacent gear.

In this formation, the gear that detects the rotation of input shaft is made as at axial adjacent gear, so, can concentrate the distribution of the rotation detecting of answering, the operation that can improve the distribution of these rotation detectings with each gear mesh.

In the present invention, because the detection unit of rotation detecting is configured to gear in axially locating opposite to each other, so, the detection unit of rotation detecting and the relative axial position of gear relation can not change, the width that does not increase gear can detect rotation, so, can be in the increase of the width dimensions of the axial inhibition internal-combustion engine of speed changer.In addition, because the rotating speed of the gear of the rotation interlock of feasible detection and input shaft, so, input shaft rotational speed can be detected.For this reason, AMT for example like that by drive unit self-shifting vehicle in, can detect the switching of speed change, can hold the self-shifting state by good precision.

In addition, the gear that is detected rotating speed by rotation detecting is as be near the gear the axle of speed changer central in axial arrangement, then the rotation detecting of answering with this gear mesh is configured to the position of leaving from the bearing of the axle head of supporting speed changer, do not need to increase the axial length of speed changer, can suppress the maximization of internal-combustion engine.

As rotation detecting is disposed at crankcase, then also can not be provided for the other housing of this turn-sensitive device etc.

As rotation detecting being disposed at the back of crankcase, compare with the occasion of configuration rotation detecting on crankcase, can improve the top exhaust system that is positioned at crankcase or the configuration of components degrees of freedom of air inlet system.

As the gear by rotation detecting detection rotating speed is the gear of being located at than the output shaft at the more past rear of input shaft, gear in this gear and the gear of being located at input shaft, that diameter is bigger than the gear of the diameter minimum on input shaft is meshed, then the diameter of this gear is smaller, so, can suppress the overhang of rotation detecting, realize miniaturization towards the internal-combustion engine rear.

In addition, even in the occasion that this formation is applicable to the vehicle of the clutch device that has carried double-clutch type, also can obtain the effect same with above-mentioned effect.

In this occasion, as detect the gear of rotation of first input shaft and the gear of rotation that detects second input shaft, then can concentrate the distribution of the rotation detecting of answering, the operation that improves distribution with gear mesh at axial adjacent gear.

Description of drawings

Fig. 1 is two-wheeled left surface figure.

Fig. 2 is the left surface figure of power unit.

Fig. 3 is the right hand view of power unit.

Fig. 4 is the 4-4 line sectional view of Fig. 2.

Fig. 5 is the 5-5 line sectional view of Fig. 4.

Fig. 6 is the sectional view corresponding with Fig. 5 on cylinder side side, rear portion.

Fig. 7 is the system diagram that the formation of hydraulic system is shown.

Fig. 8 is the longitudinal section of gear shift and clutch device.

Fig. 9 is the major component enlarged view of Fig. 8.

Figure 10 is the 10-10 line amplification sectional view of Fig. 2.

Figure 11 is the 11-11 line sectional view of Figure 10.

Figure 12 is the figure of axle and the rotation speed change of outer shaft in illustrating, A be from one grade to the upgrading of second gear, B is second gear upgrading to third gear.

Figure 13 is that the X of Fig. 2 is to view.

Figure 14 is the 14-14 line sectional view of Figure 13.

Figure 15 is the 15-15 line sectional view of Figure 13.

Embodiment

Below, a form of implementation of the present invention is described with reference to the accompanying drawings.

Fig. 1 is two-wheeled left surface figure.

In Fig. 1, symbol F represents two-wheeled 1 vehicle frame, and this vehicle frame F has head pipe 326, pairing left and right main frame 327,327, reaches pairing left and right pivot plate 328,328; This pipe 326 can support the front fork 325 with axle supporting front-wheel WF with turning to; This pairing left and right main frame 327,327 extends down backwards from this head pipe 326; This pairing left and right pivot plate 328,328 is connected with in the ground, rear portion of two main frames 327,327 and extends towards the below; At pivot plate 328,328 front end of support arm 329 joltily, trailing wheel WR is bearing in the rear portion of rocking arm 329.Symbol 325a is for turning to handgrip.Between the front portion of the bottom of pivot plate 328 and rocking arm 329, connecting rod 330 is set, damping device 331 is set on the top of connecting rod 330 and pivot plate 328.

On main frame 327,327 and pivot plate 328,328, hang power unit P.Power unit P has motor E and speed changer M, and the rotating power of exporting from speed changer M is delivered to trailing wheel WR by the live axle 332 before and after extending to.At the bottom installation side support 334 of the left side pivot plate 328 of the engine main body 333 of motor E or vehicle frame F, when erecting side support 334 when stopping, two-wheeled 1 becomes the state towards left side.

Fig. 2 is the left surface figure of power unit, and Fig. 3 is its right hand view.

In Fig. 2 and Fig. 3, motor E constitutes the water-cooled of V-type, the engine main body 333 of motor E has by the state that carries two-wheeled 1 and is positioned at the anterior bank BF in the place ahead and is positioned at the rear portion bank BR that more is positioned at the rear than this front portion bank BF, but at the bent axle 336 to the left and right directions of shared crankcase 335 free rotary ground supportings of two bank BF, BR along two-wheeled 1.Crankcase 335 is by constituting in conjunction with upper tank halfbody 335a and lower tank halfbody 335b, and front and rear cylinder block 338F, 338R constitute V-arrangement, are integrally formed at upper tank halfbody 335a.The axis of bent axle 336 is configured on the junction plane 337 of upper tank halfbody 335a and lower tank halfbody 335b.

Anterior bank BF is made of anterior cylinder block 338F, the anterior cylinder front cover 340F that is incorporated into the front cylinder head 339F of anterior cylinder block 338F and is incorporated into front cylinder head 339F, rear portion bank BR is made of rear portion cylinder block 338R, the rear portion cylinder front cover 340R that is incorporated into the rear portion cylinder head 339R of rear portion cylinder block 338R and is incorporated into rear portion cylinder head 339R equally, in the bottom of above-mentioned crankcase 335 in conjunction with food tray 341.Forwardly cylinder block 339F forms 2 cylinder holes 342,342 of arranging along the axial direction of bent axle 336, anterior cylinder block 339F by engine main body 333 the suspended state of vehicle frame F make cylinder hole 342,342 axis forward square neck tiltedly be incorporated into crankcase 335.

Form 2 cylinder holes 342,342 of arranging along the axial direction of bent axle 336 at rear portion cylinder block 338R, rear portion cylinder block 338R is hanging at engine main body 333 under the state of vehicle frame F and makes the axis in each cylinder hole 342,342 be incorporated into crankcase 335 obliquely to the back upper place.Make piston 343,343... jointly be connected in bent axle 336 with constituting V-arrangement, the piston 343,343 that square neck is oblique forward is fitted to the two cylinder holes 342,342 of anterior bank BF respectively slidably, and the piston 343,343 of Qing Xieing is fitted to the two cylinder holes 342,342 of rear portion bank BR respectively slidably towards the rear.

Fig. 4 is the 4-4 line sectional view of Fig. 2, and Fig. 5 is the 5-5 line sectional view of Fig. 4.In Fig. 4 and Fig. 5, forwardly cylinder head 339F goes up each cylinder hole 342,342 respectively is provided with a pair of intake valve 344,344 and exhaust valve 345,345.Intake valve 344,344 each by a pair of valve spring 346,346 towards closing the valve direction application of force, can carry out the configuration of on-off action ground, outlet valve 345,345, can be carried out on-off action ground and dispose towards closing the valve direction application of force by valve spring 347,347.These intake valves 344,344 and exhaust valve 345,345 carry out driven for opening and closing by the anterior cylinder side side valve gear 348F of single cam mode.

The anterior cylinder side side valve gear 348F of single cam mode has camshaft 349 as shown in Figure 4, and this camshaft 349 has the axis parallel with bent axle 336, but free rotary ground supporting is in front cylinder head 339F.Camshaft 349 is disposed at the top of intake valve 344,344 as shown in Figure 5, at camshaft 349 configuration a plurality of (being 4 in this embodiment) air inlet side cams 350,350.Air inlet side valve tappet 351,351 is contacted with air inlet side cam 350,350, and air inlet side valve tappet 351,351 is located at the end of intake valve 344,344, is fitted to front cylinder head 339F slidably.

At camshaft 349, with air inlet side cam 350,350 side by side, towards axially disposing a plurality of (being 4 in the present embodiment) exhaust side cams 352,352 with staggering.Roller 353,353 rolls and is contacted with exhaust side cams 352,352, and roller 353 can be supported on an end of rocking arm 355,355 with rotating freely with axle.Rocking arm 355,355 is supported swingably by pitman arm shaft 356, and pitman arm shaft 356 has the axis parallel with camshaft 349, and fixed configurations is to front cylinder head 339F.In the other end can regulate of rocking arm 355,355 advance and retreat position fixing valve tappet screw 354,354, valve tappet bolt 354,354 is contacted with the valve stem 345a of exhaust valve 345,345, the upper end of 345a.

Right-hand end at camshaft 349 is provided with driven sprocket 396, and at the cam chain 397 of driven sprocket 396 volume link shapes, cam chain 397 volumes are suspended to the driving sprocket wheel 393 of the right-hand end of bent axle 336.They are contained in cam chain chamber 100.

At the right-hand end of bent axle 336 and driven sprocket 393 fixed drive sprocket wheel 394 side by side.Driving sprocket wheel 394 constitutes the regularly part of driving mechanism 398 of cylinder side side, rear portion, the rotating power of bent axle 336 is delivered to air inlet side and the exhaust side camshaft 357,358 (with reference to Fig. 6) of rear portion described later cylinder side side valve gear 348R by 1/2 reduction speed ratio.At the cam chain 399 of driving sprocket wheel 394 volume link shapes, these cam chain 399 volumes are suspended to the driven sprocket (not shown on the figure) of being located at air inlet side and exhaust side camshaft 357,358 respectively.

Speed reducer 101 of right-hand end configuration at bent axle 336.No. one time speed reducer 101 has the main actuation gear 58a that is located at bent axle 336 in the position that more is in foreign side than driving sprocket wheel 394, main actuation gear 58a and main driven gear described later 58 (with reference to Fig. 8) engagement.

Left end at bent axle 336 connects generator 384.Stator 386 in rotor 385 constitutes generator 384 by rotor 385 that is fixed in bent axle 336 and fixed configurations, accommodates the generator containing room 388 of generating hood 387 inboards.Stator 386 is fixed in generating hood 387.Connect overrunning clutch 389 at rotor 386, in overrunning clutch 389 connection gear 390, unshowned starter motor in gear 390 connection diagrams.

Fig. 6 is the sectional view corresponding with Fig. 5 on cylinder side side, rear portion.

In Fig. 6, each cylinder hole 342,342 is provided with a pair of intake valve 371,371 and exhaust valve 372,372 at rear portion cylinder head 339R.Intake valve 371,371 each by a pair of valve spring 381,381 towards closing the valve direction application of force, can carry out the configuration of on-off action ground, simultaneously, exhaust valve 372,372 each by a pair of valve spring 382,382 towards closing the valve direction application of force, can carry out on-off action ground and dispose.These intake valves 371,371 and exhaust valve 372,372 carry out driven for opening and closing by cylinder side side, rear portion valve gear 348R.

Cylinder side side, rear portion valve gear 348R is the double-cam mode, have intake-side camshaft 357 and exhaust side camshaft 358, this intake-side camshaft 357 and exhaust side camshaft 358 have the axis parallel with bent axle 336, but free rotary ground supporting is in rear portion cylinder head 339R.

Intake-side camshaft 357 is disposed at the top of intake valve 371,371, exhaust side camshaft 358 is disposed at the top of exhaust valve 372,372,357,358 disposes a plurality of (being 4 in the present embodiment) air inlet side cams 359 and a plurality of (being 4 in the present embodiment) exhaust side cams 361 respectively at each.At air inlet side cam 359 contact air inlet side valve tappets 360, air inlet side valve tappet 360 is located at the end of intake valve 371, is embedded in rear portion cylinder head 339R slidably.At exhaust side cams 361 contact exhaust side valve tappets 362, exhaust side valve tappet 362 is located at the end of exhaust valve 372, is embedded in rear portion cylinder head 339R slidably.In addition, set up at cylinder side side, rear portion valve gear 348R and the operating state of the intake valve 371,371 of 2 cylinders can be switched to the on-off action state and close the air inlet side valve operating state change mechanism 363 of valve dormant state and the operating state of the exhaust valve 372,372 of 2 cylinders can be switched to the on-off action state and close the exhaust side valve events Status Change mechanism 364 of valve dormant state.Intake-side camshaft 357 and exhaust side camshaft 358 are similarly driven by annular cam chain 399 with Fig. 4.

Below, speed changer M is described.Speed changer M is dual clutch transmission as shown in Figure 7, constitute twin clutch type speed change control system two-wheeled 1, this twin clutch type speed change control system mainly comprise the dual clutch transmission 23 that is connected with in motor E, with driving mechanism 39 be located at gear 24 speed change gear 41, and dual clutch transmission 23 and speed change gear 41 moved the electric control device (ECU) 42 of control.

In the lump with reference to Fig. 8, dual clutch transmission 23 has the main shaft 28 of the duplex that is made of interior outer shaft 43,44, countershaft 29 with these main shaft 28 parallel configuration, stride the speed change gear group 45 of main shaft 28 and countershaft 29 configurations, be disposed at the double clutch 26 of the right part of main shaft 28 coaxially, and will work with the hydraulic supply unit 46 of hydraulic pressure supply to this double clutch 26.Below, with main shaft 28, countershaft 29, and the aggregate that constitutes of speed change gear group 45 as gearbox 47.

Main shaft 28 as shown in Figure 8 in axle 43 right side can insert with the relative rotation and lead in outer shaft 44, in this axle 43 across the gearbox casing 22 of the part of formation crankcase 335 about.Should in axle 43 be rotatably supported in outer shaft 44 by bearing.Dispose the actuation gear 48a～48f of six grades of scopes among the speed change gear group 45 dividually in the periphery of interior outer shaft 43,44.On the other hand, the driven gear 49a～49f of six grades of scopes in the periphery configuration speed change gear group 45 of countershaft 29.Each actuation gear 48a～48f and driven gear 49a～49f are meshing with each other at the gear of correspondence, constitute the speed change gear corresponding with each gear respectively to 45a～45f.Each speed change gear to 45a～45f by make reduction speed ratio diminish (becoming high gear) from one grade to six grades order.

The left part of interior axle 43 arrives the left side wall 22a of gearbox casing 22, is rotatably supported in this left side wall 22a by ball bearing 73.On the other hand, the right side of interior axle 43 connects the right side wall 22b of gearbox casing 22, reach in the clutch containing room 25, left and right sides intermediate portion of axle 43 is by the left and right sides intermediate portion of the outer shaft 44 of perforation right side wall 22b and the right side wall 22b that ball bearing 77 is rotatably supported in gearbox casing 22 in this.

Outer shaft 44 is than interior axle 43 weak points, and the end of its left part is at the left and right sides of gearbox casing 22 intermediate portion.More be positioned at the position of left at the above-mentioned right side wall 22b of the ratio of outer shaft 44, from the left side by fourth gear with, the order supporting speed change gear group 45 that uses of six grades of usefulness, second gears with corresponding actuation gear 48b, 48d, the 48f of even number gear (two, four, six grades).On the other hand, more be positioned at the position of left in the left part of the ratio outer shaft 44 of interior axle 43, from the order supporting speed change gear group 45 that the left side is used by one grade of usefulness, five grades of usefulness, third gear with corresponding actuation gear 48a, 48c, the 48e of odd number gear (, three, five grade).

The left and right end portions of countershaft 29 is rotatably supported in left and right sides sidewall 22a, the 22b of gearbox casing 22 respectively by ball bearing 82,86.

The left part of countershaft 29 is projected into the left of left side wall 22a, at this left part fixed drive umbrella gear 114, has the driven bevel pinion 115 of the spin axis that extends towards two-wheeled 1 fore-and-aft direction in 114 engagements of this driving umbrella gear.Drive umbrella gear 114 and driven bevel pinion 115 and in the gear chamber 118 of the inboard of the 1st gear cover 116, be meshing with each other, at the 1st gear cover 116 by bolt dismantledly in conjunction with the 2nd gear cover 117.At an end of driven bevel pinion 115 chimeric supporting axles 121, but the other end of this supporting axle 121 passes through ball bearing 122 free rotary ground supportings in the projection of the 1st gear cover 116.In addition, driven bevel pinion 115 has axial region 115a on coaxial, but this axial region 115a passes through ball bearing 119 free rotary ground supportings in the 2nd gear cover 117, connects the 2nd gear cover 117, is connected to above-mentioned live axle 332 (with reference to Fig. 1).At above-mentioned the 1st gear cover 116, with driven bevel pinion 115 vehicle speed sensor 405 is set opposite to each other, vehicle speed sensor 405 is obtained the speed of a motor vehicle by the rotating speed that detects driven bevel pinion 115.

Position in the inboard that is positioned at gearbox casing 22 of countershaft 29, by with the same order supporting speed change gear group 45 of each actuation gear 48a～48f in the driven gear 49a～49f corresponding with each gear.

Inside at main shaft 28 (interior axle 43) and countershaft 29, form respectively and can send the main oil pump (not shown) of usefulness to supply with oil circuit 71,72 toward the master that interior each one of motor E supplies with hydraulic pressure from oil pressure, each main supply oil circuit 71,72 suitably supplies to engine oil speed change gear group 45 by this.

At the right part of main shaft 28 arranged coaxial double clutch 26.Double clutch 26 has mutually first and second plate clutches (the following clutch that also is called for short sometimes) 51a, the 51b of the hydraulic type of adjacency configuration coaxially, outer shaft 43,44 in these each clutch 51a, 51b connect coaxially.At the total clutch external member 56 of each clutch 51a, 51b the main driven gear 58 that the main actuation gear 58a with bent axle 336 meshes is set coaxially, by these each gears 58,58a, will be input to clutch external member 56 from the rotary driving force of bent axle 336. Outer shaft 43,44 in the rotating power that is input to clutch external member 56 is delivered to respectively corresponding to the cut-out of each clutch 51a, 51b and on-state.

The cut-out of each clutch 51a, 51b and on-state were controlled according to the having or not respectively of hydraulic pressure supply from hydraulic supply unit 46, and details illustrates in the back.

Make each clutch 51a, the side of 51b is a coupled condition, and to make the opposing party be dissengaged positions, use is connected to interior outer shaft 43, arbitrary speed change gear of a side of 44 is to carrying out the transmission of power in the gearbox 47, simultaneously, from being connected to interior outer shaft 43, the gear mesh that next the opposing party of 44 speed change gear centering chosen in advance is used, from this state at each clutch 51a, the clutch that makes coupled condition among the 51b is a dissengaged positions, the clutch that makes dissengaged positions is a coupled condition, thereby the transmission of power of gearbox 47 is switched to the right transmission of power of the previously selected speed change gear of use, carry out upgrading or lowering category of gearbox 47 thus.

As shown in Figure 7, hydraulic supply unit 46 has the clutch oil pump 32 that the source takes place as the hydraulic pressure of double clutch 26 usefulness, give oil circuit 35 from this clutch with what the exhaust port of oil pump 32 extended, be connected to the first and second clutch actuator 91a, the 91b in this downstream side of giving oil circuit 35, and the first and second supply oil circuit 92a, the 92b of connection side hydraulic chamber 54a, 54b (with reference to Fig. 8) from this each clutch actuator 91a, 91b to each clutch 51a, 51b.

Clutch is provided with respectively with oil pump 32 and main oil pump, and the engine oil in the food tray under the crankcase 335 341 is sucked, and is discharged to and gives in the oil circuit 35.Giving the oil strainer 89 that oil circuit 35 is provided with this oil circuit special use.Symbol S6, S7 represent to detect hydraulic pressure and warm hydrostatic sensor and the oil temperature sensor of giving in the oil circuit 35 of oil among the figure, symbol R represents to control the safety valve that the hydraulic pressure given in the oil circuit 35 rise, and symbol S8, S9 represent to detect the hydraulic pressure respectively supplied with in oil circuit 92a, the 92b promptly to the hydrostatic sensor of the supply hydraulic pressure of each clutch 51a, 51b.

Giving oil circuit 35 and first and second supplies with oil circuit 92a, 92b and can be communicated with respectively by the action of each clutch actuator 91a, 91b, when giving oil circuit 35 and first and supply with oil circuit 92a and be communicated with by first clutch actuator 91a, supply with connection side hydraulic chamber 54b that oil circuit 92a supply to second clutch 51b with the higher hydraulic pressure of oil pump 32 by first from clutch, this second clutch 51b becomes coupled condition.On the other hand, when giving oil circuit 35 and second and supply with oil circuit 92b and be communicated with by second clutch actuator 91b, supply with connection side hydraulic chamber 54a that oil circuit 92b supply to first clutch 51a with the hydraulic pressure of oil pump 32 by second from clutch, this first clutch 51a becomes coupled condition.

From giving the overflow oil circuit 96 that oil circuit 35 branches have relief valve 95.Relief valve 95 switches opening, disconnecting of overflow oil circuit 96 by valve actuator 95a action.Valve actuator 95a moves control by electric control device 42, for example, and when engine start, open overflow oil circuit 96, will turn back to food tray 341 with the supply hydraulic pressure of oil pump 32 from clutch, after engine start, disconnect overflow oil circuit 96, can will supply with hydraulic pressure supply to double clutch 26.Be provided with when disconnection is given oil circuit 35 and supplied with being communicated with of oil circuit 92a, 92b and turn back to oil circuit 93a, 93b in the food tray from clutch with the hydraulic pressure of oil pump 32 at each clutch actuator 91a, 91b.

As Fig. 7 and shown in Figure 10, the gear 24 that constitutes speed change gear 41 is moving axially the fork 24b of a plurality of (being four in this embodiment) by the rotation with the speed-changing drum 24a of each 28,29 parallel configuration, and the speed change gear that switches the transmission of power that is used for 29 of main shaft 28 and countershafts is to (gear).

Each fork 24b has fork that extends to main shaft 28 sides and the fork that extends to countershaft 29 sides, and their terminal side can be supported on a pair of fork bar 24c respectively with moving axially.At the terminal side of each fork 24b any slip teat 24e that engages with a plurality of cam path 24d of speed-changing drum 24a periphery is set respectively.Each fork 24b is sticked in sliding gear described later among the speed change gear group 45 in main shaft 28 sides and countershaft 29 sides with its front end.When speed-changing drum 24a rotates, along the figure of each cam path 24d each fork 24b is being moved axially, above-mentioned sliding gear is being moved axially, change the gear of gearbox 47.

Distolateral driving mechanism 39 that is provided with at speed-changing drum 24a.Driving mechanism 39 has the coaxial pin gear 39a that is fixed in the speed-changing drum 24a of gear 24, is sticked in the barrel cam 39b of the worm of this pin gear 39a, and this tubular gear 39b is applied the electric motor 39c of rotary driving force, driving by electric motor 39c is suitably rotated speed-changing drum 24a, changes the gear of gearbox 47.

Electric motor 39c is installed on the side of crankcase 335, in this embodiment, is installed on the left and right sides either party's of crankcase 335 side by engine main body 333 at the lift-launch state of vehicle frame F, and Zuo Ce side for example is disposed at the rear of generating hood 387.

Symbol S1 among Fig. 7 represents to detect for the gear that detects gearbox 47 sensor of the actuating quantity of driving mechanism 39, and symbol DS represents to detect the angular sensor of angle of swing of the reality of speed-changing drum 24a.

As shown in figure 11, at crankcase 335 connecting box members 188, at the fixing electric motor 39c of case member 188.Motor drive shaft 190 at this electric motor 39c forms actuation gear 192, at actuation gear 192 engagements the 1st intermediate gear 193.The 1st intermediate gear 193 is supported on running shaft 196, supports the 2nd intermediate gear 194, the 2 intermediate gears 194 side by side at running shaft 196 and is engaged in driven gear 195.Driven gear 195 is fixed in barrel cam 39b, by the action by above-mentioned a group gear row of the driving force of electric motor 39c, drives barrel cam 39b rotation.Periphery at barrel cam 39b is provided with spiral helicine cam path 197, is engaged to the engagement pin 198 of above-mentioned pin gear 39a at cam path 197.Engagement pin 198 has many, and corresponding to the rotation of barrel cam 39b, a plurality of engagement pins 198,198... engage with cam path 197 successively and transferred, thereby rotating power is delivered to pin gear 39a.

As shown in Figure 8, gearbox 47 form corresponding to the actuation gear 48a～48f of each gear and driven gear 49a～49f mesh often engagement type often.Each gear be divided into substantially can with respect to the fixed gear of its supporting axle (each 28,29) one rotation, with respect to supporting axle can rotate relatively and also axial irremovable free gear and relatively the axle one rotate and can be at axially movable sliding gear.

Specifically, actuation gear 48a, 48b are fixed gear, and actuation gear 48c, 48d are sliding gear, and actuation gear 48e, 48f are free gear.In addition, driven gear 49a～49d is free gear, and driven gear 49e, 49f are sliding gear.Below, each gear 48c, 48d, 49e, 49f are called sliding gear, each gear 48e, 48f, 49a～49d are called free gear.Make arbitrarily by above-mentioned gear 24 that sliding gear suitably slides (moving axially), thereby can use the speed change gear corresponding carrying out transmission of power with arbitrary gear.

In the side of sliding gear 48c, 48d, be provided with integratedly respectively with them and similarly can relative supporting axle one rotate and can be at axially movable slip ring Sc, Sd.Each slip ring Sc, Sd axially are being adjacent to free gear 48e, the setting of 48f ground respectively.At each slip ring Sc, Sd slip side claw (dowel) D1c, D1d are set respectively, free side claw (dowel) D1e, the D1f corresponding with each slip side claw D1c, D1d are set respectively at each free gear 48e, 48f.

In addition, in the side of sliding gear 49e, 49f, be provided with integratedly with them and similarly can relative supporting axle one rotate and can be at axially movable slip ring Se, Sf.Each slip ring Se, Sf axially are being adjacent to free gear 49c, the setting of 49d ground respectively.At each slip ring Se, Sf slip side claw (dowel) D2e, D2f are set respectively, free side claw (dowel) D2c, the D2d corresponding with each slip side claw D2e, D2f are set respectively at each free gear 49c, 49d.

In addition, opposite side at each sliding gear 49e, 49f is provided with slip side claw (dowel) D3e, D3f respectively, free gear 49a, 49b are adjacent in the axial direction, at free gear 49a, 49b free side claw (dowel) D3a, the D3b corresponding with each slip side claw D3e, D3f are set respectively.

Each slide side claw and free side claw the sliding gear (containing slip ring) of correspondence and free gear mutually near the time can not engage with the relative rotation mutually, when above-mentioned sliding gear and free gear leave mutually, remove above-mentioned engaging.Make any of each sliding gear and the corresponding relative not engaging revolvably of free gear by each claw, thereby can selectively use arbitrary speed change gear to transferring power at main shaft 28 and 29 of countershafts.Under the state (state shown in Figure 8) that the engaging between each sliding gear and free gear is disengaged fully, 28,29 of diaxons can not transferring power, and this state becomes the neutral state of gearbox 47.

As shown in Figure 7, electric control device 42 is except the information from above-mentioned each sensor, also according to from the wheel speed sensors WS of retractable sensor (switch) SS of the jaw opening sensor TS of the closure of throttle body 16, side support 334 (or intermediate support), front-wheel 2, for example be located at the mode switch SW1, the gear selector switch SW2 that turn to handgrip 325a, and neutral gear drive the information of diverter switch SW3 etc., the action of control dual clutch transmission 23 and speed change gear 41, the gear (shift position) of change gearbox 47.

The speed change pattern of being selected by above-mentioned mode switch SW1 has the fully automatic mode and the semi-automatic pattern that can only be switched the gear of gearbox 47 according to driver's will by the operation of above-mentioned selector switch SW2 that automatically switches the gear of gearbox 47 according to vehicle information such as the speed of a motor vehicle (wheel velocity) and engine speed.Present speed change pattern and gear for example are shown in to be located at and turn to handgrip 325a metering device MU nearby.In addition, can between can be, switch gearbox 47 by the operation of NDS Neutral Drive Switch SW3 by the state of predetermined gear transferring power and neutral state.In Fig. 7, symbol S3 represents to detect for detection of engine rotating speed (rotating speed of bent axle 336) speed probe of the rotating speed of main actuation gear 58a.The total ECU42a that uses from fuel injection system of electric control device 42 and the information of each sensor.

As shown in Figure 9, the right side (the overall width direction outside) of clutch 26 in clutch containing room 25 disposes the first clutch 51a of speed change gear to being connected that uses with the odd number gear, and the left side in clutch containing room 25 (overall width direction inboard) disposes the second clutch 51b of speed change gear to being connected that uses with the even number gear.Each clutch 51a, 51b have the many friction disk clutchs of wet type that axially replace overlapping a plurality of clutch friction plate (each clutch plate 61a, 61b and each clutch friction plate 66a, 66b) at it.

Serve as reasons supply hydraulic pressure from the outside of each clutch 51a, 51b makes pressing plate 52a, 52b move and the hydraulic type of the engaging power that obtains to be scheduled in the axial direction, have towards clutch and cut off Returnning spring 53a, the 53b of side above-mentioned pressing plate 52a, the 52b application of force, pressing plate 52a, 52b are connected connection side hydraulic chamber 54a, the 54b that side applies pushing force towards clutch, and pressing plate 52a, 52b are applied pushing force and it is returned cut-out side hydraulic chamber 55a, the 55b that power is assisted towards clutch cut-out side.Often supply with hydraulic pressure cutting off side hydraulic chamber 55a, 55b, select and supply with respectively hydraulic pressure from the elevated pressures of hydraulic supply unit 46 (clutch with oil pump 32) to connecting side hydraulic chamber 54a, 54b from the lower pressure of above-mentioned main oil pump.

Each clutch 51a, 51b have single clutch external member 56, constitute roughly same diameter.Clutch external member 56 be towards right-hand opening the round-ended cylinder shape arranged, its bottom center portion can be supported on the left and right sides intermediate portion of outer shaft 44 with the relative rotation.Clutch intermediate member 57a in that the right inner side configuration first clutch 51a of clutch external member 56 uses disposes the clutch intermediate member 57b that second clutch 51b uses in the inboard, a left side of clutch external member 56.The right part of axle 43 in but clutch intermediate member 57a one is supported on rotatably, but clutch intermediate member 57b one is supported on the right part of outer shaft 44 rotatably.

In the bottom left of clutch external member 56, by spring buffer 59 main driven gear 58 is installed, at the main actuation gear 58a of these main driven gear 58 engagement bent axles 336.

That is, at the rotating power of clutch external member 56 by spring buffer 59 input bent axles 336.Clutch external member 56 is along with the rotation and the main shaft 28 of bent axle 336 rotate respectively.

But the position one in the ratio main driven gear 58 more past left sides of clutch external member 56 is provided with the driving sprocket wheel 56b that each oil pump drives usefulness rotatably.

But one supports a plurality of clutch friction plate 61a that first clutch 51a uses rotatably week in clutch external member 56 right, but in clutch external member 56 left week one support a plurality of clutch friction plate 61b that second clutch 51b uses rotatably.Interior week formation a plurality of engagement grooves vertically at clutch external member 56, simultaneously, periphery at each clutch friction plate 61a, 61b forms a plurality of engaging teats corresponding with each engagement groove, each engages teat can not be sticked in each engagement groove with the relative rotation, thereby but each clutch friction plate 61a, 61b one is supported on clutch external member 56 rotatably.

Lip part 64a on the left of the clutch intermediate member 57a of first clutch 51a is provided with the inner wall part 65a that erects towards right-hand, but supports a plurality of clutch plates (friction plate) 66a rotatably in the periphery one of this inner wall part 65a.Form vertically a plurality of engagement grooves in the periphery of the inner wall part 65a of clutch intermediate member 57a, simultaneously, the interior week formation a plurality of engaging teats corresponding at each clutch plate 66a with above-mentioned engagement groove, can not engage the above-mentioned teat that respectively engages with the relative rotation at above-mentioned each engagement groove, thereby but each clutch plate 66a one is supported on clutch intermediate member 57a rotatably.

At the right-hand pressing plate 52a that disposes in opposite directions of lip part 64a, between the outer circumferential side of the outer circumferential side of pressing plate 52a and lip part 64a by axially replacing each clutch friction plate 61a of overlapping stacked state configuration and clutch plate 66a.

Form between interior all sides of the interior all sides of pressing plate 52a and lip part 64a and cut off side hydraulic chamber 55a, simultaneously, configuration is towards right-hand (side, the clutch that leave from lip part 64a cut off side) the Returnning spring 53a to the pressing plate 52a application of force.Be located at the 67a of support lug portion of periphery of the tube 62a of portion of central authorities on clutch intermediate member 57a right side in the right-hand configuration in opposite directions of interior all sides of pressing plate 52a, formation is connected side hydraulic chamber 54a between interior all sides of the 67a of this support lug portion and pressing plate 52a.

On the other hand, the lip part 64b on the left of the clutch intermediate member 57b of second clutch 51b is provided with the inner wall part 65b that erects towards right-hand, but supports a plurality of clutch plate 66b rotatably in the periphery one of this inner wall part 65b.Form vertically a plurality of engagement grooves in the periphery of the inner wall part 65b of clutch intermediate member 57b, simultaneously, the interior week formation a plurality of engaging teats corresponding at each clutch plate 66b with engagement groove, respectively engage teat by not engaging with the relative rotation, but each clutch plate 66b one is supported on clutch intermediate member 57b rotatably at each engagement groove.

At the right-hand pressing plate 52b that disposes in opposite directions of lip part 64b, between the outer circumferential side of the outer circumferential side of pressing plate 52b and lip part 64b by axially replacing each clutch friction plate 61b of overlapping stacked state configuration and each clutch plate 66b.

Form between interior all sides of the interior all sides of pressing plate 52b and lip part 64b and cut off side hydraulic chamber 55b, simultaneously, configuration is towards right-hand (from the side that lip part 64b leaves, clutch cuts off side) the Returnning spring 53b to the pressing plate 52b application of force.Be located at the 67b of support lug portion of periphery of the tube 62b of portion of central authorities on clutch intermediate member 57b right side in the right-hand configuration in opposite directions of interior all sides of pressing plate 52b, formation is connected side hydraulic chamber 54b between interior all sides of the 67b of this support lug portion and pressing plate 52b.

Clutch cover 69 on the right side that constitutes clutch containing room 25 is provided with the first supply oil circuit 92a, second respectively and supplies with oil circuit 92b, reaches the 3rd supply oil circuit 92c.In addition, in the right hollow part 43a of interior axle 43, suitably form the oil circuit that is communicated with each oil circuit 92a, 92b, 92c respectively.

Can supply with oil circuit 92a etc. by first will be from clutch with the hydraulic pressure supply of the oil pump 32 connection side hydraulic chamber 54b to second clutch 51b, can supply with oil circuit 92c etc. by the 3rd will be from the hydraulic pressure supply of the main oil pump cut-out side hydraulic chamber 55a to first clutch 51a, can will be from the hydraulic pressure supply of the clutch usefulness oil pump 32 connection side hydraulic chamber 54a to first clutch 51a by the second supply oil circuit 92b etc.Can supply with oil circuit 92c etc. by the 3rd will be from the hydraulic pressure supply of the main oil pump cut-out side hydraulic chamber 55b to second clutch 51b.

Each clutch 51a, 51b make pressing plate 52a, 52b move towards right-hand by the elastic force of each Returnning spring 53a, 53b under engine stop-state (halted state of each oil pump), become the clutch dissengaged positions of the friction apply of removing each clutch friction plate 61a, 61b and each clutch plate 66a, 66b.In addition, even be engine operating state, under the state that stops from the hydraulic pressure supply of hydraulic supply unit 46, the elastic force of Returnning spring 53a, 53b and the hydraulic pressure that respectively cuts off side hydraulic chamber 55a, 55b also act on pressing plate 52a, 52b, with the above-mentioned clutch dissengaged positions that similarly becomes.

On the other hand, in first clutch 51a, engine operating state and from hydraulic supply unit 46 with the hydraulic pressure supply of elevated pressures under the state that connects side hydraulic chamber 54a, the hydraulic pressure of pressing plate 52a resistance cut-out side hydraulic chamber 55a and the elastic force of Returnning spring 53a are towards left (lip part 64a side, clutch connects side) move, each clutch friction plate 61a and each clutch plate 66a are subjected to cramping, they carry out friction apply, thereby become the clutch coupled condition that can carry out transmission of torque between clutch external member 56 and clutch intermediate member 57a.

Equally, in second clutch 51b, engine operating state and from hydraulic supply unit 46 with the hydraulic pressure supply of elevated pressures under the state that connects side hydraulic chamber 54b, the hydraulic pressure of pressing plate 52b resistance cut-out side hydraulic chamber 55b and the elastic force of Returnning spring 53b are towards left (lip part 64b side, clutch connects side) move, each clutch friction plate 61b and each clutch plate 66b are subjected to cramping, they carry out friction apply, thereby become the clutch coupled condition that can carry out transmission of torque between clutch external member 56 and clutch intermediate member 57b.

When the clutch coupled condition from each clutch 51a, 51b stops when connecting side hydraulic chamber 54a, 54b supply hydraulic pressure, elastic force by the hydraulic pressure that cuts off side hydraulic chamber 55a, 55b and Returnning spring 53a, 53b makes pressing plate 52a, 52b move towards right-hand, remove the friction apply of each clutch friction plate 61a, 61b and each clutch plate 66a, 66b, become the clutch dissengaged positions that can not transmit the torque between clutch external member 56 and clutch intermediate member 57a, 57b.

Supply to the cut-out side hydraulic chamber 55a of each clutch 51a, 51b, the engine oil of 55b is directed to outside the hydraulic chamber by the oil circuit that suitably is formed at inner wall part 65a, 65b etc., suitably supplies to clutch friction plate 61a, 61b and each clutch plate 66a, the 66b of inner wall part 65a, 65b periphery.Escape by making the working oil of cutting off in side hydraulic chamber 55a, the 55b like this, the hydraulic pressure that cuts off in side hydraulic chamber 55a, the 55b is remained predetermined low-pressure state, and make each clutch friction plate 61a, 61b and the lubricity of each clutch plate 66a, 66b and the property cooled off raising among each clutch 51a, the 51b that is in dissengaged positions.

In above-mentioned dual clutch transmission 23, even after two-wheeled 1 engine start, the occasion that is judged as vehicle stop state such as erecting according to side support, both remain the clutch dissengaged positions with each clutch 51a, 51b.For example at side support by folding and unfolding or each switch SW 1, the operated occasion of SW2, SW3, starting as two-wheeled 1 is prepared, gearbox 47 becomes one grade of state that can use one grade of gear (starting gear, speed change gear are to 45a) transferring power from neutral state, from this state engine speed is risen, thereby make first clutch 51a through the half-clutch clutch coupled condition that becomes, make two-wheeled 1 starting.

When two-wheeled 1 walked, only the corresponding side of the shift position with present among each clutch 51a, 51b became coupled condition, and the opposing party keeps dissengaged positions.Like this, a side and each speed change gear by interior outer shaft 43,44 carries out transmission of power to the arbitrary gear mesh among 45a～45f.At this moment, when carrying out speed change, electric control device 42 according to information of vehicles pre-formation can use the speed change gear corresponding to carrying out the state of transmission of power with next shift position, simultaneously, control dual clutch transmission 23 action.

Specifically, as present shift position (gear) for example is odd number shelves (or even number shelves), then next shift position becomes even number shelves (or odd number shelves), so pre-formation can use the speed change gear of even number shelves (or odd number shelves) to carrying out the state of transmission of power.At this moment, first clutch 51a (or second clutch 51b) is a coupled condition, and second clutch 51b (or first clutch 51a) is a dissengaged positions, and it is right motor output (rotating power of bent axle 336) not to be delivered to the outer shaft 44 (or interior axle 43) and the speed change gear of even number shelves (or odd number shelves).After this, when electric control device 42 judgements reach the speed change moment, only be to make first clutch 51a (or second clutch 51b) become dissengaged positions, simultaneously, make second clutch 51b (or first clutch 51a) become coupled condition, use the speed change gear right transmission of power corresponding with previously selected next shift position thereby switch to.Like this, carrying out rapidly discontinuously and speed change stably of the time lag in the time of can not producing speed change, transmission of power.

In this form of implementation, as shown in Figure 8, at the back of gearbox casing 22 (suitable) 22c turn-sensitive device 401,402 is installed with the back of crankcase, and make its detection unit 401a, 402a and free gear (driven gear) 49c, 49d tooth top in opposite directions. Free gear 49c, 49d are adjacent to configuration, axial fixed-site near the central authorities of countershaft 29. Free gear 49c, 49d are located at the countershaft 29 that more is in the rear than main shaft 28, actuation gear 48c, the 48d engagement big with actuation gear 48a among the actuation gear 48a～48f that is located at main shaft 28, diameter diameter group minimum.In addition, as described above, the double-layer structural that outer shaft 43,44 constituted in main shaft 28 was served as reasons, one side's turn-sensitive device 401 disposes opposite to each other with the tooth top of free gear 49c, this free gear 49c and the actuation gear 48c engagement of being located at interior axle 43, the opposing party's turn-sensitive device 402 disposes opposite to each other with the tooth top of free gear 49d, this free gear 49d and the actuation gear 48d engagement of being located at outer shaft 44.

Above-mentioned turn-sensitive device 401,402 detects to be located at and the free gear 49c of the countershaft 29 of the rotation interlock of main shaft 28, the rotating speed of 49d, so, can detect the rotating speed of main shaft 28.Owing to detected the rotating speed of main shaft 28, so, utilize it, can be in the self-shifting vehicle with the switching of good accuracy detection speed change, but precision is held the self-shifting state well.

The interior axle 43 when Figure 12 A represents automatic speed changing from one grade (odd number shelves) to second gear (even number shelves) and the change in rotational speed of outer shaft 44.The rotating speed of axle 43,44 can be obtained by the rotating speed that is detected free gear (49c or 49d) by turn-sensitive device (401 or 402).

In the time of one grade, with reference to Fig. 8, action by fork 24b makes the driven gear 49e of countershaft 29 move towards the left among the figure, slip side claw D3e is fitted to free side claw D3a, under this state, connect first clutch 51a, make outer shaft follow the rotation of clutch external member and apply at least rotatably this is followed the required MIN hydraulic pressure of rotation, connect second clutch 51b.But, the speed change gear of outer shaft 44 to become can not transferring power state, become neutral state completely.That is, according to this control, interior axle 43 and outer shaft 44 all press roughly the same rotating speed rotation, but transmission of power is specially by interior axle 43 enforcements, and it only is the state (state of the L5 of Figure 12 A) of following rotation that outer shaft 44 becomes.Like this, by first clutch 51a, interior axle 43, and one grade speed change gear 45a is carried out one grade transmission of power to countershaft 29.

When electric control device 42 judges to arrive the speed change moment, carry out automatic speed changing from one grade to second gear.In this occasion, preparation as second gear, stop to put on second clutch 51b, the above-mentioned needed hydraulic pressure of rotation of following is after the supply of second clutch 51b, right-hand move of the sliding gear 49f that makes countershaft 29 by the action of fork 24b in Fig. 8, slip side claw D3f is fitted to the free side claw D3b of free gear 49b, and the speed change gear of establishing second gear is to 45b.When this speed change gear is established 45b, press rotating speed (state of the L6 of Figure 12 A) sharply decline roughly point-blank of the outer shaft 44 that rotates with interior 43 roughly the same rotating speed before this.The rotating speed of end point B1 is the rotating speed with the corresponding second gear of the speed of a motor vehicle.

The rotation speed change of this moment detects the rotating speed of the free gear 49d of 45d by detected the speed change gear that constitutes outer shaft 44 left ends by above-mentioned turn-sensitive device 402.This change in rotational speed and mean the chimeric establishment of slip side claw D3f and free side claw D3b at the rotating speed of end point B1, promptly the preparation of second gear finishes.

Turn-sensitive device 402 is connected to electric control device 42, and electric control device 42 cuts off first clutch 51a after being ready to complete to second gear according to the input from turn-sensitive device 402, connect second clutch 51b.After this, with reference to Fig. 8, the driven gear 49e that makes countershaft 29 by the action of fork 24b right-hand moving in the figure, axle all speed change gears of 43 are to being state that can not transferring power in making, after forming substantially completely neutral state, the rotation that makes interior axle follow the clutch external member applies this with being rotated at least and follows the needed MIN hydraulic pressure of rotation, connects first clutch 51a.After this, implemented the transmission of power of second gear specially by outer shaft 44, interior axle 43 only is to follow rotation (state of the L7 of Figure 12 A).Under second gear, the speed change gear by second clutch 51b, outer shaft 44, second gear carries out transmission of power to 45b to countershaft 29.

In this form of implementation, interior axle 43 and outer shaft 44 carry out automatic speed changing by the state of " rotation is followed in existence " shown in Figure 12 A, so, during this automatic speed changing, the rotating speed of outer shaft 44 from interior 43 roughly the same rotation speed change to the rotating speed of the corresponding second gear of the speed of a motor vehicle.Like this, the scope jumpy of rotating speed diminishes, the generation of the sound in the time of can suppressing automatic speed changing.

Phenomenon shown in Figure 12 A present shift position be odd number shelves (, three, five grade), next shift position be even number shelves (two, four, six grades) comprise all automatic speed changings that upgrade and lower category the time occur in the same manner.Therefore, in the process of the preparation of carrying out speed change, the rotating speed of outer shaft 44 must change, so, as detect the rotating speed that this has changed by turn-sensitive device 402, then can go out the slip side claw corresponding and the chimeric establishment of free side claw by good accuracy detection with each grade.In this occasion, the rotating speed of putting B1 the end of at is the arbitrary rotating speed in two, four, six grades corresponding with the speed of a motor vehicle, so, can carry out speed change reposefully from the odd number shelves to the even number shelves.

The interior axle 43 when Figure 12 B represents automatic speed changing from second gear (even number shelves) to third gear (odd number shelves) and the change in rotational speed of outer shaft 44.

When second gear, implement transmission of power by outer shaft 44 specially as described above, interior axle 43 only is to follow rotation (state of the L8 of Figure 12 B).When from the second gear to the third gear, carrying out automatic speed changing, after cutting off first clutch 51a (stopping to follow the condition of supplying of the needed hydraulic pressure of rotation), make right-hand move of sliding gear 49e in Fig. 8 by the action of fork 24b, the slip side claw D2e of slip ring Se is fitted to the free side claw D2c of free gear 49c, and the speed change gear of establishing third gear is to 45c.

When this speed change gear was established 45c, before the rotating speed that reaches with the corresponding third gear of the speed of a motor vehicle, the rotating speed of interior axle 43 (state of the L9 of Figure 12 B) roughly point-blank sharply descended.At the rotating speed of end point B2 is rotating speed with the corresponding third gear of the speed of a motor vehicle.The change in rotational speed of this moment detects the rotating speed of free gear 49c by above-mentioned turn-sensitive device 401 and detects.This change in rotational speed means the chimeric establishment of slip side claw D2e and free side claw D2c, and promptly the preparation of third gear finishes.

Turn-sensitive device 401 is connected to electric control device 42, electric control device 42 according to from the input of turn-sensitive device 401 after being ready to complete of third gear, cut off second clutch 51b, connection first clutch 51a.After this, action by fork 24b makes the sliding gear 49f of countershaft 29 move towards the left among Fig. 8, all speed change gears that make outer shaft 44 are to being state that can not transferring power, form substantially completely neutral state after, supply with following the MIN necessary hydraulic pressure of rotation to second clutch 51b.After this, implemented the transmission of power of third gear specially by interior axle 43, outer shaft 44 only is to follow rotation (state of the L10 of Figure 12 B).Under third gear, by first clutch 51a, interior axle 43, and speed change gear 45c is carried out transmission of power to countershaft 29.

In this form of implementation, interior axle 43 and outer shaft 44 carry out automatic speed changing by the state of " rotation is followed in existence " shown in Figure 12 B, so the rotation speed change that takes place during automatic speed changing is little.The generation of the sound in the time of therefore, can suppressing automatic speed changing.

Above-mentioned phenomenon to present shift position be even number shelves (two, four, six grades), next shift position be odd number shelves (, three, five grade) comprise all automatic speed changings that upgrade and lower category the time occur in the same manner.Therefore, in the process of the preparation of carrying out speed change, the rotating speed of interior axle 43 must change, so, as detecting this variation, then can go out the slip side claw corresponding and the chimeric establishment of free side claw by good accuracy detection with each grade by turn-sensitive device 401.In this occasion, the rotating speed of putting B2 the end of at is the arbitrary rotating speed in, three, five grade corresponding with the speed of a motor vehicle, so, can carry out speed change reposefully from the even number shelves to the odd number shelves.

The following describes the fixation arrangement of above-mentioned turn-sensitive device 401,402.

Turn-sensitive device 401,402 is fixed in the back 22c of gearbox casing 22 as shown in Figure 2 side by side, is hidden in the configuration of the 2nd gear cover 117 or live axle 332 back ground under the vehicle body side-looking.Like this,, also cover, can protect turn-sensitive device 401,402 by the 2nd gear cover 117 or live axle 332 even slungshot etc. is arranged.Figure 13 is the subsequent figures of gearbox casing 22, and Fig. 2 schemes to looking X.At the back of gearbox casing 22 22c, integrally formed vertical four, horizontal two, oblique totally 7 root 22e, 22f, 22g, 22h, 22i, 22j, a 22k, this back 22c is strengthened by each rib.Cross part at the rib 22k of the rib 22i of the horizontal expansion of this reinforced back 22c and oblique extension forms two opening 22l, 22m transversely arrangedly, at the fixing turn-sensitive device 401,402 of this opening.

One side's turn-sensitive device 401 and free gear 49c are inserted into a side opening 22l in opposite directions as shown in Figure 14.Turn-sensitive device 401 is by being incorporated into the back 22c that turn-sensitive device 401 is fixed to gearbox casing 22 with screw 401c with the supporting slice 401b spiral card of one.Symbol 401d is a connector.

In addition, the opposing party's turn-sensitive device 402 and free gear 49d are inserted into the opposing party's opening 22m in opposite directions as shown in Figure 15.Turn-sensitive device 402 is by being sticked in the back 22c that turn-sensitive device 402 is fixed to gearbox casing 22 with screw 402c with the supporting slice 402b spiral of one.Symbol 402d is a connector.

In this formation, even form two opening 22l, 22m transversely arrangedly at the back of gearbox casing 22 22c, this back 22c is also strengthened by each rib, two opening 22l, 22m are owing to be positioned at the rib 22i of horizontal expansion and the cross part of the rib 22k of oblique extension, so the intensity of back 22c is kept.In addition, the parts of general exhaust system or air inlet system be positioned at gearbox casing 22 above, and in this formation, turn-sensitive device 401,402 is configured to the back 22c of gearbox casing 22, so, these configuration of components degrees of freedom are not produced restriction, the configuration of components degrees of freedom of exhaust system or air inlet system improves.

In addition, as described above, in this form of implementation, free gear 49c, 49d fix owing to axial position, dispose turn-sensitive device 401,402 in opposite directions at this free gear 49c, 49d, so the axial relative position relation of turn-sensitive device 401,402 and free gear 49c, 49d does not change.For this reason, the facewidth that does not increase free gear 49c, 49d can detect rotating speed, so, can suppress motor E and increase at the axial width dimensions of speed changer M.In addition, free gear 49c, the 49d that is fixed at axial position do not engage fork 24b.For this reason, the position of speed-changing drum 24a is not restricted, and the configuration degrees of freedom of speed-changing drum 24a improves.

In addition, free gear 49c, 49d are adjacent to be disposed near the central authorities of countershaft 29, so, can concentrate the distribution of the turn-sensitive device 401,402 of answering with each gear mesh, improve the wiring operation of each turn-sensitive device 401,402.Owing to detect and the free gear 49c of the rotation interlock of main shaft 28, the rotating speed of 49d, so, the rotating speed of main shaft 28 can be detected.

In this form of implementation, free gear 49c, 49d are located at the countershaft 29 that more is in the rear than main shaft 28, actuation gear 48c, the 48d engagement big with the actuation gear 48a of diameter diameter group minimum among the actuation gear 48a～48f that is located at main shaft 28.Generally speaking, bigger with the diameter of gear on the countershaft 29 of the gear engagement of the diameter minimum on the main shaft 28 than other gear that is on the countershaft 29, so, as form the formation that detects this gear, then turn-sensitive device 401,402 is outstanding more towards the rear of motor E, and the front and back length of motor E becomes big.

In this formation, owing to turn-sensitive device 401,402 is set at free gear 49c, 49d, in this free gear 49c, 49d and the gear of being located at main shaft 28, diameter is than the big gear engagement of gear of the diameter minimum on the main shaft 28, so, turn-sensitive device 401,402 overhangs can be suppressed, the miniaturization of motor E can be realized towards motor E rear.

The double-layer structural that outer shaft 43,44 constituted in main shaft 28 was served as reasons, one side's turn-sensitive device 401 disposes opposite to each other with the tooth top of the free gear 49c that is engaged to the actuation gear 48c that is located at interior axle 43, and the opposing party's turn-sensitive device 402 disposes opposite to each other with the tooth top that is engaged to the free gear 49d of the actuation gear 48d that is located at outer shaft 44.This formation is applicable to the vehicle of the clutch device that has carried double-clutch type, but also applicable to the vehicle of in addition clutch-type, is for example undertaken by drive unit like that in all vehicles of self-shifting at AMT, and it is suitable for also may.

The axle head of general speed changer M is supported on crankcase 335 by bearing etc.For this reason, during near the gear that rotating speed is detected is set at axle head gear, in order to ensure the space that turn-sensitive device is set, must outer this bearing of side configuration, corresponding therewith, it is big that axial length becomes, motor E maximization.In this formation, the gear that rotating speed is detected is made as near free gear 49c, the 49d of the axial arrangement central authorities of the axle of speed changer M, so turn-sensitive device 401,402 is disposed at the position of leaving from bearing, do not need to increase axial length, can suppress the maximization of motor E.

A form of implementation of the present invention more than has been described, but has the invention is not restricted to above-mentioned form of implementation, can carry out various design alterations not breaking away under the prerequisite of the present invention of claim.

Claims (7)

1. an internal-combustion engine is accommodated bent axle and speed changer in crankcase,

This speed changer has the gear that a plurality of speed changes are used,

And this speed changer has the input shaft of the rotating power of importing bent axle and also this rotating power is delivered to the output shaft of driving wheel from this input shaft by the rotating power of gear transmission bent axle; It is characterized in that:

Rotation detecting with rotating speed of the gear that detects above-mentioned speed changer,

The detection unit of this rotation detecting with disposing opposite to each other with the rotation interlock of above-mentioned input shaft and at the gear that axially is positioned.

2. internal-combustion engine according to claim 1 is characterized in that: the gear that is detected rotating speed by above-mentioned rotation detecting is near the gear of the axial arrangement central authorities of the axle of above-mentioned speed changer.

3. internal-combustion engine according to claim 1 is characterized in that: above-mentioned rotation detecting is configured on the above-mentioned crankcase.

4. internal-combustion engine according to claim 1 is characterized in that: above-mentioned rotation detecting is configured in the back of above-mentioned crankcase.

5. according to claim 3 or 4 described internal-combustion engines, it is characterized in that: the gear that detects rotating speed by above-mentioned rotation detecting is to be arranged on than input shaft more to be in gear on the output shaft at rear, this gear be arranged on input shaft on gear in, gear that diameter is bigger than the gear of the diameter minimum on the input shaft is meshed.

6. internal-combustion engine according to claim 1 is characterized in that: above-mentioned input shaft has first input shaft and second input shaft,

On the axle of above-mentioned first input shaft, dispose first clutch, and on the axle of above-mentioned second input shaft, dispose second clutch, can make the rotating power of above-mentioned bent axle cut off and connect by the action of this a pair of clutch to the transmission of above-mentioned input shaft,

Above-mentioned rotation detecting can detect first input shaft rotational speed and second input shaft rotational speed ground respectively corresponding to the gear of the rotation interlock of first input shaft be provided with a plurality of with the gear of the rotation interlock of second input shaft.

7. internal-combustion engine according to claim 6 is characterized in that: detect the gear of rotation of first input shaft and the gear of rotation that detects second input shaft at axial adjacent gear.

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