CN101839312B - Vehicular automatic transmission with planetary gear mechanism - Google Patents

Abstract

The present invention discloses a vehicular automatic transmission with planetary gear mechanisms. Engine braking can be realized at all gears of the vehicular automatic transmission, wherein the vehicular automatic transmission is equipped with a plurality of speed changing units with planetary gear mechanisms. The transmission is equipped with a unidirectional clutch which prevents the rotation of sun gears of planetary gear mechanisms to a direction and the rotation of gear ring of planetary gear mechanisms in a direction. An output shaft rotates with an output rotation speed which is obtained after performing speed changing to the input rotation speed of the input shaft through the planetary gear mechanisms. Furthermore an output shaft rotates a driving wheel of the vehicle and transfers the rotation of the output shaft to the unidirectional clutch of the input shaft when the output rotation speed exceeds the input rotation speed. Additionally, in the vehicular automatic transmission which is equipped with the speed changing units with the planetary gear mechanisms, a transmission mechanism which is equipped with an output introducing-out shaft and a neutral clutch is configured to the output side compactly.

Description

Be equipped with the automatic transmission for vehicles of planetary gears

The cross reference of related application

The application requires the Japanese patent application of the No.2009-069030 that submits on March 19th, 2009 and the preference of the Japanese patent application of the No.2009-069031 that submits on March 19th, 2009, and the full content of above-mentioned application is contained in this by reference.

Technical field

The present invention relates to a kind of automatic transmission that is equipped with planetary gears that is installed on the vehicle.

Background technique

Known be equipped with a plurality of variable-speed units and wherein each variable-speed unit be equipped with planetary gears and according to the automatic transmission for vehicles of the gear ratio control unit of transfer input shaft speed control gear ratio processed.For example, see US5514043, JP-A No.2001-165250 and JP-ANo.2000-283251.

In being equipped with the automatic transmission for vehicles of a plurality of planetary gears, because the gear ratio control unit of each variable-speed unit is equipped with an element gear stoping planetary gears to the rotation of a direction and allows the overrunning clutch of its rotation round about, so the gear ratio the gear ratio when overrunning clutch allows that each planetary pinion is driven directly with except engine braking the time is rotated and can't be realized engine braking.

In addition, known to be equipped with to be passed to output for the rotation with output shaft and to derive axle and be used for disconnecting output shaft and the automatic transmission for vehicles of the neutral gear clutch of the transmission between the axle is derived in output that output is derived axle the rotation of output shaft is passed to wheel.For example see JP-ANo.H11-270641.

Summary of the invention

One embodiment of the present invention are equipped with a plurality of variable-speed units and thereby each variable-speed unit is equipped with planetary gears is implemented in the operation of engine braking under all gears with simple structure automatic transmission for vehicles for a kind of.According to one embodiment of the present invention, make things convenient for the connection of overrunning clutch/separation to realize the operation of engine braking.

According to a kind of mode of execution of the present invention, automatic transmission for vehicles is equipped with: by the input shaft (20) of prime mover (E) rotation; Be equipped with each planetary gears (P1, P2) and each gear ratio control unit (C1, C2) variable-speed unit (M1, M2), each planetary gears (P1, P2) have by sun gear (30,130), gear carrier (40,140) and the support planetary gears (41 of support planetary gears (41,141), 141) gear ring (50,150) three element gears that consist of, each gear ratio control unit (C1, C2) is by each planetary gears (P1, P2) control gear ratio (r1, r2); And output shaft (23), it passes through variable-speed unit (M1 with the input speed (Ni) with input shaft (20), the driving wheel (98) of the output speed that M2) obtains after the speed change (No) rotation and rotation vehicle, it is characterized in that: each gear ratio control unit (C1, C2) be equipped with each the specific element gear (30 that stops in corresponding three element gears, 150) overrunning clutch (80 of using to the speed change of the rotation of a direction, 180), and only be equipped with the transmission control member (25) that when output speed (No) surpasses input speed (Ni), the rotation of output shaft (23) is passed to input shaft (20) between input shaft (20) and the output shaft (23).

According to one embodiment of the present invention, input shaft (20) and planetary gears (P1, P2) by output shaft (23) rotatably support and radially be positioned at its outside, and the end (21a) of input shaft (20) is equipped with the enlarged-diameter part of axially open, and transmission control member (25) is for radially being arranged in the transmission overrunning clutch (25) in the enlarged-diameter part.

According to one embodiment of the present invention, in the vehicle deceleration process, the rotation of driving wheel is by the output shaft rotation input shaft, and the rotation of output shaft is walked around planetary gears by the transmission control member and is passed to input shaft.Thus, under the gear ratio the gear ratio that is driven directly except speed changer, also can realize engine braking, and therefore engine braking can be realized under all gear ratio.

According to one embodiment of the present invention, because be equipped in the end of input shaft and be connected to the enlarged-diameter part of axially open as the overrunning clutch of transmission control member, so make things convenient for the dismounting of overrunning clutch.

In addition, can't obtain to disconnect neutral state to wheel transmission power because be equipped with the structure of the planetary gears in the automatic transmission for vehicles of planetary gears, thus be desirable to provide for power transmission to wheel and disconnect the neutral gear clutch of this transmission.

When speed changer is installed on various types of vehicles, may wish that further speed change derives axle will be adjusted to by the input speed that planetary gears obtains output.

From the angle of speed changer miniaturization, in the time of on speed changer is installed in as the motorcycle of dilly, wish that neutral gear clutch and output derives axle and arrange compactly.

According to one embodiment of the present invention, in the automatic transmission for vehicles that is equipped with the variable-speed unit with planetary gears, the driving mechanism that is equipped with output derivation axle and neutral gear clutch is arranged on the outlet side compactly.

According to one embodiment of the present invention, a kind of automatic transmission for vehicles is equipped with: by the input shaft (20) of prime mover (E) rotation; Variable-speed unit (M1, M2), the gear ratio control unit (C1, C2) that it is equipped with planetary gears (P1, P2) and controls each gear ratio (r1, r2) by each planetary gears (P1, P2); Output shaft (23), it is with output speed (No) rotation of input speed (Ni) by obtaining after variable-speed unit (M1, the M2) speed change with input shaft (20); And be equipped with the driving mechanism (90) on the outlet side of being positioned at that axle (91) is derived in the output of being rotated by output shaft (23), it is characterized in that, output shaft (23) is equipped with from the axially extended outrigger shaft of variable-speed unit (M1, M2) (27).Driving mechanism on outlet side (90) is equipped with and drives rotor (92), it is interior in the formed space of outrigger shaft (27) (S2) that it is located at outrigger shaft (27) axial prespecified range (W) upper and that be located between driving mechanism and the variable-speed unit (M1, M2).Driven rotor (93) is arranged on output, and to derive axle (91) upper and drive by driving rotor (92) and neutral gear clutch (95), and wherein neutral gear clutch (95) rotation that will drive rotor (92) is passed to and exports derivation axle (91) and disconnect this transmission.Output is derived axle (91) and is arranged and see in the axial direction with overlapping position and the neutral gear clutch (95) of variable-speed unit (M2) and be arranged in the prespecified range (W).

According to one embodiment of the present invention, planetary gears (P1, P2) is for the elementary planetary gears (P1) that is equipped with three primary element gears that are made of the gear carrier (40) of sun gear (30), support planetary gears (41) and gear ring (50) and be equipped with secondary planetary gears (P2) by three secondary element gears of the gear carrier (140) of sun gear (130), support planetary gears (141) and gear ring (150) formation; Gear ratio (r1, r2) is elementary gear ratio (r1) and secondary gear ratio (r2); Gear ratio control unit (C1, C2) is elementary gear ratio control unit (C1) and secondary gear ratio control unit (C2); Variable-speed unit (M1, M2) comprises the elementary variable-speed unit (M1) that is equipped with elementary planetary gears (P1) and elementary gear ratio control unit (C1) and is equipped with secondary planetary gears (P2) and the secondary variable-speed unit (M2) of secondary gear ratio control unit (C2).Elementary gear ratio control unit (C1) is controlled elementary gear ratio (r1) by the elementary planetary gears (P1) that receives input shaft (20) rotation input.Secondary gear ratio control unit (C2) is controlled secondary gear ratio (r2) by the secondary planetary gears (P2) of the rotation input of the elementary output rotor (44b) of the elementary variable-speed unit of reception (M1).The rotation of the secondary output rotor (175) of secondary variable-speed unit (M2) inputs to output shaft (23), and elementary gear ratio control unit (C1) is equipped with the second primary element gear (30) of three primary element gears of prevention to the elementary overrunning clutch (80) of a direction rotation.Secondary gear ratio control unit (C2) is equipped with the second subprime element gear (150) of three secondary element gears of prevention to the secondary overrunning clutch (180) of a direction rotation.Elementary overrunning clutch (80) and secondary overrunning clutch (180) are equipped with the total rotation adjusting member (T) between the secondary engagement part (H2) of the elementary anastomosis part (H1) that axially is arranged in elementary planetary gears (P1) and secondary planetary gears (P2).

According to one embodiment of the present invention, the space that is formed at the radial outside of outrigger shaft by utilization can see that in the axial direction deriving axle with the output of the overlapping position of variable-speed unit is arranged on radially position near output shaft with being set up, and the neutral gear clutch can be set to radially close output shaft, and the driving mechanism that is positioned on the outlet side that is equipped with output derivation axle and neutral gear clutch can be radially near output shaft ground compact Layout.Therefore, can make in the radial direction miniaturization of speed changer.

According to one embodiment of the present invention, because the utilization of primary and secondary overrunning clutch is formed at the axially total rotation of the equipment of the space between the primary and secondary anastomosis part in the primary and secondary variable-speed unit with primary and secondary planetary gears and primary and secondary gear ratio control unit adjusting member, the speed changer that is arranged in vertically each primary and secondary planetary gears outside with the primary and secondary overrunning clutch that is equipped with independent rotation adjusting member is compared, and two variable-speed units all can be arranged in the axial direction compactly.Therefore, being arranged in basis can arrange in the axial direction compactly from the neutral gear clutch in the prespecified range of the length of the extended outrigger shaft of variable-speed unit.

In addition, the primary and secondary overrunning clutch can common components, and can reduce cost by the quantity that reduces parts.

Specify according to following, further application area of the present invention will be more clear.But although should be appreciated that and indicated the preferred embodiment of the present invention, specific description and specific example will very clear various changes and modification in spirit and scope of the invention according to specific description those skilled in the art only as example.

Description of drawings

According to following specify and only as example but not the accompanying drawing that limits the invention invention will be more fully understood.Wherein:

Fig. 1 is the sectional view that the power unit that is equipped with automatic transmission and internal-combustion engine that the present invention is suitable for is shown, and wherein the part of internal-combustion engine is schematic representation;

Fig. 2 is the enlarged view of automatic transmission shown in Figure 1, and the overrunning clutch that wherein is used for regulating rotation illustrates with the sectional view along Fig. 4 II-II line;

Fig. 3 is the enlarged view that the major component of automatic transmission shown in Figure 2 is shown;

Fig. 4 is the sectional view of IV-IV line in Fig. 2;

Fig. 5 (a) is to the schematic representation of Fig. 5 (d) for the operation of explanation automatic transmission shown in Figure 1, Fig. 5 (a) is for reaching the state of one grade of gear ratio, Fig. 5 (b) is for reaching the state of second gear gear ratio, Fig. 5 (c) is for reaching the state of three class gear shift ratio, and Fig. 5 (d) is for reaching the state of four-speed gear shift ratio.

Fig. 6 is the conceptual illustration figure of the resulting gear ratio of automatic transmission shown in Figure 1.

Embodiment

Below with reference to Fig. 1 to Fig. 6 one embodiment of the present invention are described.

As shown in Figure 1, applicable automatic transmission M of the present invention and internal-combustion engine E as prime mover consist of power unit jointly, and this power unit is installed on the motorcycle as vehicle.

In this embodiment, lateral is consistent with lateral and the longitudinal direction of the motorcycle of installation power unit with longitudinal direction, and vertical direction is orthogonal direction.

In specification or in the scope of claims, axial direction is the direction with the rotating center line parallel of the input shaft of speed changer or output shaft, and radial direction and circumferential direction are with the direction of rotation centerline as the center.When a direction in the left or right expression axial direction, another direction in another left or right expression axial direction.

The gear ratio of speed changer is reduction speed ratio.

Internal-combustion engine E is air cooling single-cylinder four-stroke internal-combustion engine, and it is equipped with the master unit that comprises cylinder block 1, and cylinder block 1 has cylinder 1a, but piston 4 to-and-fro motion be installed in the cylinder 1a.Cylinder head 2 is connected to the upper end of cylinder block 1 and the lower end that crankcase 3 is connected to cylinder block 1.

In cylinder head 2, be equipped with firing chamber 7, will from the air that is used for burning of the gas handling system 8 that is connected with cylinder head 2 and the fuel air mixture from the fuel of Fuelinjection nozzle 9 guide to firing chamber 7 the suction port (not shown), with waste gas 7 guide to the relief opening (not shown) of the vent systems that is connected with cylinder head 2 from the firing chamber, 7 the spark plug 10a and driven respectively and for the suction valve and the outlet valve (all not shown) that open and close respectively suction port and relief opening by the valve train 11 that is equipped with camshaft 11a towards the firing chamber.

Pressure-driven and the to-and-fro motion of the combustion gas that piston 4 is produced by the burning of the fuel air mixtures in the firing chamber 7, and make bent axle 6 rotations by connecting rod 5.The dynamic rotation of the bent axle 6 that the timing drive mechanism 12 of camshaft 11a by being equipped with chain 12a transmits.

The rotation of the bent axle 6 that internal-combustion engine E equips (this rotation also can be called as power or torque in this manual) is input to speed changer M.The chain 97b of the power of deriving axle (output deriving shaft) 91 from the output of speed changer M by the driving mechanism 97 that is configured for driving drives the trailing wheel 98 as driven object, and this trailing wheel 98 is driving wheel.

The air throttle 8a control air inflow that gas handling system 8 is equipped, air inflow is the flow that enters the air that is used for burning in the firing chamber 7.Fuelinjection nozzle 9 is the fuel air mixture generation unit, its control spray into for the burning airborne fuel delivery volume with control fuel air mixture air fuel ratio.Be equipped with the ignition mechanism 10 control ignition timing of spark plug 10a.

Air throttle 8a, Fuelinjection nozzle 9 and ignition mechanism 10 are respectively upper and can come according to the serviceability of the serviceability of internal-combustion engine E and speed changer M the output-controlling device of controller 13 controls of the output of controlling combustion engine E by being equipped in internal-combustion engine E, also are respectively the revolution speed control device of rotational speed N i (seeing Fig. 6) of the input shaft 20 of the rotating speed of control bent axle 6 in the whole control procedure of the output of combustion motor E and speed changer M in addition.

Controller 13 is equipped with state detection unit and control unit 13a, and state detection unit detects the serviceability of internal-combustion engine E and the serviceability of speed changer M, is input to control unit 13a from the testing signal of state detection unit.The time detecting unit 13c of the endurance that state detection unit comprises the clutch 70, the 170 half clutch jointing state detection unit 13b that engage that detect to be used for speed changer M speed change, detect half jointing state that is detected by clutch jointing state detection unit 13b and the serviceability detection unit that detects the load of engine speed and internal-combustion engine E.

Clutch jointing state detection unit 13b by will before the actual speed No of the setting gear ratio that sets according to the input speed Ni of the input shaft 20 of speed changer M and the output shaft 23 of the speed changer M that detects based on rotation speed detection unit and the actual gear ratio that actual input speed Ni that rotation speed detection unit detects calculates compare to detect half jointing state.For example, because actual gear ratio is less than setting gear ratio when in two clutches 70,170 at least one slided, so when definite actual gear ratio during less than the setting gear ratio, clutch jointing state detection unit 13b detects half jointing state.

When the detected endurance of time detection unit 13c surpassed the scheduled time, the operation of at least one in control unit 13a control air throttle 8a, Fuelinjection nozzle 9 and the ignition mechanism 10 was with at least one the output controlled variable in control air inflow, fuel duty and the ignition timing.Increase or reduce input speed Ni by control and make each clutch 70,170 the rotating speed that engages fully to reach.

Crankcase 3 is made of a pair of half casing 3a, 3b and a pair of case lid 3c, 3d, half casing 3a, 3b be connected to each other by a plurality of bolts and can be on the direction of vehicle width (being lateral) be separated, case lid 3c, 3d are connected on separately half casing 3a, the 3b by a plurality of bolts.Bent axle 6 is rotatably supported by a pair of main bearing 14a, 14b by this double casing 3a, 3b.

Crankcase 3 forms the housing 15 that holds bent axle 6 and speed changer M.Case of transmission 16 as the partition wall in the housing 15 is divided into the 15a of crankshaft room and speed changer chamber 15b with housing 15, is arranged among the 15a of crankshaft room as drive chamber as the bent axle 6 of live axle, and speed changer M is arranged among the 15b of speed changer chamber.In this embodiment, case of transmission 16 is partly separated housing 15 in the bottom of housing 15, so that the 15a of crankshaft room and speed changer chamber 15b are communicated with on the top of housing 15 and the diapire of half casing 3a, 3b and case lid 3d formation speed changer chamber 15b.In another example, case of transmission 16 also can be separated housing 15, so that the 15a of crankshaft room and speed changer chamber 15b are mutual space independently.

The end 6a of bent axle 6 passes main bearing 14a and extends to the right, be equipped with the centrifugal clutch 17 as starting clutch at end 6a place, this centrifugal clutch is according to the rotating speed as the bent axle 6 of engine speed, the rotation of bent axle 6 is passed to speed changer M and disconnects transmission to the rotation of bent axle 6.Centrifugal clutch 17 is equipped with the centrifugal weight 17a of the joint of controlling centrifugal clutch 17 in response to the variation of engine speed.

Power unit is equipped with the reducing gear 18 as the input side driving mechanism, and it is passed to the rotation of bent axle 6 input shaft 20 of speed changer M by the centrifugal clutch 17 that engages fully.Reducing gear 18 comprises actuation gear 18a and driven gear 18b, actuation gear 18a receives the rotation of centrifugal clutch 17, driven gear 18b and input shaft 20 rotate integratedly and input bent axle 6 rotation of transmitting through the centrifugal clutch 17 as the input side clutch, and centrifugal clutch 17 controls are to the rotation transmission of input shaft 20 and be disconnected to the transmission of speed changer M.

As depicted in figs. 1 and 2, speed changer M is equipped with: the input shaft 20 that is passed through driven gear 18b rotation by the bent axle 6 of internal-combustion engine E; Variable-speed unit U with planetary gears P 1, P2; The output shaft 23 that the output speed No that reaches through variable-speed unit U speed change with input speed Ni rotates; Has the outlet side driving mechanism 90 of being derived axle 91 by the output of output shaft 23 rotations; And the case of transmission 16 that holds input shaft 20, variable-speed unit U and output shaft 23.

Case of transmission 16 and crankcase 3 are the members that are not included in following rotating parts and the rotating member, for example are different from such as the rotating parts of planetary gears P1, P2 among the variable-speed unit U and the member of non-rotary fixed side of rotating member of deriving the gearbox M of axle 91 such as input shaft 20, output shaft 23 and output.

Input shaft 20 is rotatably supported by case of transmission 16 and is rotatably supported by output shaft 23 by half casing 3b.Input shaft 20 axially is arranged in and is positioned at the outside 15a of crankshaft room of speed changer chamber 15b (or case of transmission 16), and be equipped with the first input shaft 21 and the second input shaft 22, the first input shaft 21 becomes one with driven gear 18b, the moving axially relevant with output shaft 23 and regulated by thrust bearing B1 of the second input shaft 22.The interior week of the second input shaft 22, the periphery by output shaft 23 rotatably supported, and the periphery of the second input shaft is rotatably supported by bearing B2 by housing 16.

Connect with the periphery of the second input shaft 22 and have end 21a with coaxial the first input shaft 21 of the second input shaft 22 by key, end 21a forms axially towards the open opening 21b of the 15a of crankshaft room.End 21b is the part of expanded in diameter, and its diameter is larger than the second input shaft 22 of input shaft 20.

Output shaft 23 is rotatably supported by bearing B3 by half casing 3b at 23b place, an end, and is rotatably supported by bearing B4 and the second input shaft 22 by case of transmission 16 at the part place near the other end 23a.Output shaft 23 arranges coaxially with input shaft 20 and its rotation centerline L2 overlaps with the rotation centerline L 1 of input shaft 20, and output shaft 23 extends into the 15a of crankshaft room, axially passes variable-speed unit U, input shaft 20 and housing 16.Rotation centerline L1, L2 all are parallel to the rotation centerline of bent axle 6.

Speed changer M is equipped with and is arranged between input shaft 20 and the output shaft 23 as the transmission of transmission control member with overrunning clutch 25.Output shaft 23 connects with the end 21a of input shaft 20 by overrunning clutch 25 at end 23a place.Overrunning clutch 25 is equipped with clutch inner piece 25a, clutch Outside spare 25b and a plurality of clutch element 25c, wherein, clutch inner piece 25a is equipped in 23a place, end as input link and rotates integratedly with output shaft 23, clutch Outside spare 25b is equipped in 21a place, end as output link and self is made of end 21a in this embodiment, a plurality of clutch element 25c (for example spring and roller) and upwards arrange in week radially between clutch inner piece 25a and clutch Outside spare 25b at certain intervals.In another example, clutch Outside spare 25b is made of the parts that separate with end 21a, and also can be provided at 21a place, end, and clutch inner piece 25a also can self be made of end 23a.

When the rotational speed N o of output shaft 23 surpasses input speed Ni, clutch element 25c cooperates with clutch inner piece 25a and clutch Outside spare 25b, the rotation of output shaft 23 is passed to input shaft 20, and when output speed No is equal to or less than input speed Ni, clutch element 25c does not cooperate with clutch inner piece 25a and clutch Outside spare 25b, and the rotation of input shaft 20 can not be passed to output shaft 23 by overrunning clutch 25.

Therefore, when among the gear ratio R1 to R3 (seeing Fig. 6) that has set in the speed reduction of motorcycle process speed changer M is in the state that the is driven directly minimum gear ratio R4 constantly that hereinafter will describe any one, overrunning clutch 25 enters mated condition, so that the motivational drive that internal-combustion engine E is not only transmitted by variable-speed unit U by output shaft 23 by trailing wheel, and when trailing wheel during by internal combustion engine drive, overrunning clutch 25 enters not mated condition.

Variable-speed unit U comprises a plurality of variable-speed units that begin tandem arrangement during will rotating the path that is delivered to output shaft 23 from input shaft 20 from input shaft 20 sides, is elementary variable-speed unit M1 and two variable-speed units of secondary variable-speed unit M2 in the present embodiment.Variable-speed unit M1, M2 also are that the output shaft 23 of back shaft rotatably supports by the main shaft that is speed changer M, and variable-speed unit M1, M2 axially are arranged in the axial direction from beginning the order for variable-speed unit M1 and variable-speed unit M2 near reducing gear 18 1 sides (or end 23a of output shaft 23).

As shown in Figures 2 and 3, each variable-speed unit M1, M2 are equipped with respectively planetary gears P1, P2 and gear ratio control unit C1, C2, planetary gears comprises by sun gear 30,130, rotatably support a plurality of planetary pinions 41,141 gear carrier 40,140 and gear ring 50,150, and gear ratio control unit C1, C2 control separately the gear ratio R of planetary gears P1, P2 (seeing Fig. 6).

Sun gear 30,130, planetary pinion 41,141 and gear ring 50,150 be helical gear.Sun gear 30,130, gear carrier 40,140 are identical rotation centerline L1, L2 with gear ring 50,150 rotation centerline separately.

The gear ring 50 of the elementary planetary gears P1 of variable-speed unit M1 has axle 51, flange 52 and dish shape annular primary gear sidewall 54 in the tubulose, wherein axle 51 connects with the second input shaft 22 by key in the tubulose, flange 52 is that the tubular outer shaft and its inboard that are positioned at axle 51 radial outsides have the wheel tooth 53 that engages with the tooth 42 of each planetary pinion 41, dish shape annular primary gear sidewall 54 extend in the radial direction and within it the edge be connected with axle 51 in the tubulose and be connected with flange 52 in its outer edge.Gear ring 50 is the elementary input gear of input that receives the rotation of input shaft 20 among the planetary gears P1, and is the first primary element gear in three primary element gears among the planetary gears P1.

The gear carrier 40 of planetary gears P1 comprises back shaft 43 interconnected the first and second gear carriers 44,45 by rotatably supporting each planetary pinion 41.The first gear carrier 44 has axle 44b in annular element 44a and the tubulose, wherein annular element 44a is the annular wall of supported axle 43, and the interior axle 44b of tubulose is connected with the inward flange of annular element 44a and is rotatably supported by the sun gear 130 of output shaft 23 by interior axle 51 and secondary planetary gears P2.The second gear carrier 45 has annular element 45a and tubular outer shaft 45b, and annular element 45a is the annular wall of supported axle 43, and tubular outer shaft 45b is connected with the outward edge of annular element 45a.Gear carrier 40 is for exporting the rotation of input shaft 20 the elementary output gear of planetary gears P2 to after through planetary gears P1 speed change, and is the 3rd primary element gear in three primary element gears among the planetary gears P1.

The interior axle 44b of gear carrier 40 is elementary output rotor, and the rotation of input shaft 20 is inputed to planetary gears P2 by variable-speed unit M1.Outer shaft 45b has fixed wall 45c as the joining portion that can connect with clutch Outside spare 72 rotatably integratedly by key near the end place of planetary gears P1 in the axial direction, and have the supported parts 45d that provides a pair of thrust bearing B5 at the other end place, be furnished with in the axial direction the first adjusting member 61 between the thrust bearing B5.Therefore, the first adjusting member 61 stops gear carrier 40 moving axially with respect to output shaft 23 and case of transmission 16.

As the second primary element gear in three primary element gears of planetary gears P1, sun gear 30 has tubular shafts 31 and annular element 33, wherein has tooth 32 on the periphery of tubular shafts 31 to engage with the tooth 42 of each planetary pinion 41, annular element 33 be in the radial direction from axle 31 outward extending annular wall as supporting part, and provide hereinafter the ratchet 81,82 that will describe; 181,182.The axle 31 that rotatably is supported on the periphery of interior axle 44b of gear carrier 40 has elementary compressing parts 34, and elementary compressing parts 34 are for respect to the annular element 33 that is fixed to axle 31 end at more close planetary gears P2 place in the axial direction.Compressing parts 34 are urged on the periphery of interior axle 44b by the thrust bearing 46 that thrust bearing B6 will be arranged to rotate integratedly with interior axle 44b in the axial direction.Therefore, thrust bearing 46 stops sun gear 30 with respect to gear carrier 40 movement (or movement left) towards planetary gears P2 owing to the first elementary axial force F 1b left that engages generation with planetary pinion 41.

The tooth 32,42 of planetary gears P1,53 consists of elementary anastomosis part H1, wherein three primary element gears among the planetary gears P1 are engaged, namely consist of the gear ring 50 of a pair of primary element gear and each planetary pinion 41 of gear carrier 40 and engage one another, and consist of another sun gear 30 of primary element gear and each planetary pinion 41 of gear carrier 40 are engaged one another.

In addition, the sun gear 130 of the planetary gears P2 of secondary variable-speed unit M2 has axle 131, tubular outer shaft 132 and secondary gears sidewall 133 in the tubulose, wherein, axle 131 connects by the interior axle 44b of key with the gear carrier 40 of planetary gears P1 in the tubulose, tubular outer shaft 132 is being positioned at axle 131 outsides in the radial direction, secondary gears sidewall 133 is in the dish shape annular wall of extending in the radial direction, and it is connected with interior axle 131 and its outer edges is connected with outer shaft 132 at inward flange.Have tooth 131a with the tooth 142a of each planetary pinion 141 to engage by the interior axle 131 that bearing B7 rotatably supports in its periphery by output shaft 23.

Interior axle 131 has push mechanism 134 and stopper 135, push mechanism 134 is axially extended towards the interior axle 51 of the gear ring 50 of planetary gears P1 in the inner radial of the interior axle 44b of gear carrier 40, stopper 135 stops sun gears 130 moving axially to the right, and interior axle 131 connects with interior axle 44b by the key in the push mechanism 134.When sun gear 130 moves right and push mechanism 134 as hereinafter will pressing member 75,175 be pushed away to the right the time with describing, stopper 135 is by contacting to stop sun gear 130 to move right with interior axle 44b in the axial direction, and regulates sun gear 130 axially movable amounts.

Sun gear 130 is to receive the secondary input gear of input of the rotation of variable-speed unit M1 among the planetary gears P2 by interior axle 44b, and is the first secondary element gear in three secondary element gears among the planetary gears P2.

The gear carrier 140 of planetary gears P2 is provided with the back shaft 144 that rotatably supports each planetary pinion 141.Gear carrier 140 is provided with annular element 145 and tubular outer shaft 146, and wherein annular element 145 is the annular wall of supported axle 144, and tubular outer shaft 146 is connected with the circumferential edge of annular element 145.Gear carrier 140 is for exporting the rotation of interior axle 44b the secondary output gear of output shaft 23 to after through planetary gears P2 speed change, and be for the third time grade element gear in three secondary element gears among the planetary gears P2.

Outer shaft 146 is with the rotation speed change of interior axle 44b and export output shaft 23 to, and is the final output shaft of speed changer M all planetary gears P1, the P2 that equip.But outer shaft 146 has fixed wall 146c as the joining portion that connects with clutch Outside spare 172 rotatably by the key one near the place, end of planetary gears P2 in the axial direction, and have the supported parts 146d that provides a pair of thrust bearing B8 at another place, end, this is to being furnished with the second adjusting member 62 between the thrust bearing in the axial direction.Therefore, the second adjusting member 62 stops gear carrier 140 moving axially with respect to output shaft 23 and case of transmission 16.

As the second subprime element gear in three secondary element gears among the planetary gears P2, gear ring 150 has tubular outer shaft 151, annular element 152 and secondary compressing parts 153, wherein has tooth 151a in the tubular outer shaft 151 to engage with the tooth 143a of each planetary pinion 141, annular element 152 is the annular wall as supporting part that extend internally from outer shaft 151 in the radial direction, and be provided with ratchet 81,82,181,182, secondary compressing parts 153 are interior axles that the periphery by interior axle 44b rotatably supports.Compressing parts 153 with respect to annular element 152 in the axial direction near planetary gears P1, and with in the axial direction with the direction of the opposite direction of compressing parts 34 compressings by thrust bearing B9 compressing thrust bearing 46.Therefore, thrust bearing 46 stop gear rings 150 since engages with planetary pinion 141 generation first level axial force F 2b to the right and away from the movement (or to the right movement) of gear carrier 140 towards planetary gears P 1.

Each planetary pinion 141 comprises that the first gear 142 with the first tooth 142a that engages with the tooth 131a of sun gear 130 and diameter are larger and have the second gear 143 of the second tooth 143a that engages with the tooth 151a of gear ring 150 than the diameter of the first gear 142.Because planetary pinion 141, be equipped with the planetary gears P2 that gear ring 50 with planetary gears P1 has the gear ring 150 of basic identical external diameter and can obtain the secondary gear ratio r2 larger than the elementary gear ratio r1 of planetary gears P1, the structure of planetary pinion 141 so that speed changer M in the radial direction size decreases.

The angle of inclination (with respect to axial direction) of the first tooth 142a and the second tooth 143a and the angle of inclination of thus each tooth 131a, 151a are set to larger than the angle of inclination (with respect to axial direction) of the tooth 42 of each planetary pinion 41 of planetary gears P1 and each tooth 32 thus, 53 angle of inclination.

Therefore, when applying onesize torque to planetary pinion 41 and planetary pinion 141, sun gear 130 and gear ring 150 engage respectively each elementary axial force F 1a, F1b of producing and each secondary axial force F 2a, F2b of producing engage with elementary planetary pinion 41 respectively than gear ring 50 and sun gear 30 with secondary planetary pinion 141 larger.

As another example, all teeth 32,42,53,131a, 142a, 143a, 151a among two planetary gears P1, the P2 also can be set to has identical angle of inclination.

Tooth 131a, the 142a of planetary gears P2,143a, 151a consist of secondary engagement part H2, wherein three of planetary gears P2 secondary element gears are engaged, namely consist of the gear ring 150 of a pair of secondary element gear and each planetary pinion 141 of gear carrier 140 and engage, and consist of another to the sun gear 130 of secondary element gear and each planetary pinion 141 joint of gear carrier 140.

Two gear sidewalls 54,133 form in the whole or substantially whole radial extension separately comprising primary and secondary anastomosis part H1, H2 during from axial direction when each sidewall.

As shown in Figure 1 to Figure 3, the speed changer M adjusting member 60 of equipping is regulated among each planetary gears P1, P2 gear carrier 40 separately, 140 move axially.Adjusting member 60 is arranged between anastomosis part H1 and the anastomosis part H2 in the axial direction, and has the second adjusting member 62 of the position of first adjusting member 61 of position of regulating tooth wheel carrier 40 and regulating tooth wheel carrier 140.Two adjusting member 61,62 are connected respectively to and support overrunning clutch 80,180 supporting member 65, overrunning clutch 80,180 regulate respectively two among planetary gears P1, the P2 sun gear 30 and the sense of rotation of gear ring 150.

Each adjusting member 61,62 has: axially extended cylindrical part 61a, 62a; Corresponding the first and second supporting lip 61b, the 62b of the first and second supporting parts that radially extend as the axial end portion from each cylindrical part 61a, 62a; And as base flange 61c, the 62c of the standing part that on the axial base side of each cylindrical part 61a, 62a, radially extends. Base flange 61c, 62c are fixed in the case of transmission 16 a plurality of assembly parts 16a (seeing Fig. 1) that upwards arrange at certain intervals in week, and supporting member 65 between base flange and base flange and supporting member 65 be bolted.

A thrust bearing 46 of speed changer M equipment is disposed between the compressing parts 153 of the compressing parts 34 of sun gear 30 and gear carrier 140 in the axial direction, and is used to interior axle 44b.Thrust bearing 46 is assembled among the annular recess 44c on the interior axle 44b outer surface by snap ring.

Therefore, sun gear 30 and gear carrier 140 are disposed in the both sides of thrust bearing 46 in the axial direction, and are disposed in diametrically the outside of interior axle 44b, and are rotatably supported by bearing B 10 by interior axle 44b.Thrust bearing 46 is arranged in the space that overrunning clutch 80,180 external member T center on.A pair of thrust bearing B6, B9 with the contact both sides of thrust bearing 46 comprises respectively all in pairs bearing housing B6a, B9a and a plurality of roller B6bs, the B9b of radial arrangement in bearing housing B6a and bearing housing B9a of the ring-type of configuration in the axial direction.

As shown in Figures 2 and 3, the elementary gear ratio control unit C1 that controls elementary gear ratio r1 by elementary variable-speed unit M1 is equipped with clutch 70 and overrunning clutch 80.Wherein, clutch 70 is as the elementary transmission controlling mechanism that is used for elementary speed change, and according to the rotational speed N i of input shaft 20, the rotation of control gear ring 50 directly is passed to the break-make of the transmission of gear carrier 40 without planetary pinion 41 ground.Overrunning clutch 80 is as the elementary rotation adjusting member that is used for regulating elementary rotation, stops sun gear 30 as the particular element gear along A1 direction rotation (seeing Fig. 4), allows simultaneously it towards opposite A2 direction rotation.

Primary clutch 70 is the centrifugal friction clutches as the low speed side clutch that enter complete jointing state in low rotation speed area, the rotating speed of high speed area that the clutch 170 that input speed Ni is used for secondary speed change than aftermentioned in low rotation speed area enters complete jointing state is low, this primary clutch 70 comprises elementary clutch inner piece 71, tubulose primary clutch exterior part 72, control gear is transmitted in elementary rotation, elementary pressing member 75 and one or more and be a plurality of elementary centrifugal weights 76 in the present embodiment, wherein, elementary clutch inner piece 71 is by the input of the rotation that receives input shaft 20 and is the input link that the flange 52 of the part of gear ring 50 consists of, but be connected to rotatably gear carrier 40 as the tubulose primary clutch exterior part 72 of output link being positioned in the radial direction clutch inner piece 71 outsides and one, elementary rotation is transmitted control gear and is comprised one or more clutch plate 73 of the elementary input side that radially is laminated between clutch inner piece 71 and the clutch Outside spare 72 and can contacts or alternately arrange discretely and one or more clutch plate 74 of elementary outlet side, elementary pressing member 75 is axially oppressed each clutch plate 73,74 and with clutch plate 73,74 contacts, elementary centrifugal weight 76 are to drive pressing member 75 and make its axially movable elementary driving component.

Clutch 70 is in the outside that is arranged in the radial direction planetary gears P1.

The clutch plate 73 of input side can be rotated integratedly and can move axially by the key on clutch inner piece 71 peripheries and clutch inner piece 71, and outlet side clutch plate 74 can be rotated integratedly and can move axially by key and the clutch Outside spare 72 of clutch Outside spare on 72 interior weeks.

According to input speed Ni so that a plurality of clutch plate 73 that can contact or separate, 74 contacts are the dish shape members that radially extend with the pressing member 75 that separates, be arranged in the opposition side right side of gear sidewall 54 (or be arranged in) of anastomosis part H1, gear sidewall 54 is located axially between pressing member and the anastomosis part, and the snap ring 77 as the member that prevents from misplacing is stopper, is used for regulating moving right of pressing member.Snap ring 77 is set to the right maximum mobile position as the pressure release position of pressing member 75.

Pressing member 75 be from gear ring 50, begin near as the interior axle 51 of the parts that connect with input shaft 20 through flange 52 in the radial extension of clutch Outside spare 72 from axial right side covering gear ring 50 and clutch plate 73,74 elementary sidewall.In addition, pressing member 75 is rotatably supported by thrust bearing B11 by near the wall the interior axle 51 of gear ring 50, and can be mobile integratedly with gear ring 50 in the axial direction.

The secondary gear ratio control unit C2 that controls secondary gear ratio r2 by secondary variable-speed unit M2 is equipped with clutch 170 and overrunning clutch 180.Wherein, clutch 170 is as the secondary transmission controlling mechanism that is used for secondary speed change, according to elementary output speed Na and input speed Ni, or more specifically according to input speed Ni elementary output speed Na as interior axle 44b rotating speed after elementary variable-speed unit M1 speed change, the rotation of control sun gear 130 directly is passed to the break-make of the transmission of gear carrier 140 without planetary pinion 140.Overrunning clutch 180 stops the gear carrier 140 as the particular element gear to rotate along A1 direction (seeing Fig. 4) as the secondary rotation adjusting member that is used for regulating secondary rotation, allows simultaneously it towards opposite A2 direction rotation.

The secondary clutch 170 as the high-speed side clutch that enters complete jointing state in the high speed area of input speed Ni is centrifugal friction clutches, this secondary clutch 170 comprises secondary clutch inner piece 171, tubulose secondary clutch exterior part 172, control mechanism is transmitted in secondary rotation, secondary pressing member 175 and and one or more and be a plurality of secondary centrifugal weights 176 in the present embodiment, wherein, secondary clutch inner piece 171 is the input of the rotation of axle 44b in receiving and the input link that is made of the outer shaft 132 as the part of sun gear 130, but tubulose secondary clutch exterior part 172 as output link in the outside that is arranged in the radial direction clutch inner piece 171 and one be connected with gear carrier 140 rotatably, secondary rotation is transmitted control mechanism and is comprised radially between clutch inner piece 171 and clutch Outside spare 172 and can contact or be stacked alternately discretely one or more clutch plate 173 of secondary input side of layout and one or more clutch plate 174 of secondary outlet side, secondary pressing member 175 is axially oppressed each clutch plate 173,174 and with clutch plate 173,174 contacts, secondary centrifugal weight 176 are to drive pressing member 175 and make its axially movable secondary drive member.

Clutch 170 is in the outside that is arranged in the radial direction planetary gears P2.

The clutch plate 173 of input side can be rotated integratedly and can move axially by the key on clutch inner piece 171 peripheries and clutch inner piece 171, and outlet side clutch plate 174 can be rotated integratedly and can move axially by key and the clutch Outside spare 172 of clutch Outside spare on 172 interior weeks.

Two clutches 70,170 clutch plate 73,74,173, each bottoms of 174 are immersed in the lubricant oil that is stored in the case of transmission 16.

According to by the elementary output speed Na of input speed Ni after through variable-speed unit M1 speed change so that a plurality of clutch plate 173 that can contact or separate, 174 contacts or the pressing member 175 that separates are the dish shape members that radially extend, be arranged in the opposition side (in the left side of gear sidewall 133) of secondary engagement part H2, gear sidewall 133 is located axially between pressing member and the secondary engagement part H2, and the snap ring 177 as the member that prevents from misplacing is stoppers, is used for regulating the movement left of pressing member.Snap ring 177 is set left maximum mobile position as the pressure release position of pressing member 175.

Pressing member 175 is used as and directly connects with output shaft 23 and will input to through the rotation of variable-speed unit M1, M2 speed change the secondary output rotor of output shaft 23, is from begin to cover sun gear 130 and clutch plate 173,174 secondary sidewall in the radial extension of clutch Outside spare 172 from axial left side through outer shaft 132 as the key 175 with the junction point of output shaft 23.Pressing member 175 is rotatably supported and can move axially integratedly with sun gear 130 by thrust bearing B 12 by near the wall the interior axle 131 of sun gear 130.

Two clutches 70, each clutch Outside spare 72 of 170,172 are provided with supporting walls 72a, 172a, stopper 72b, 172b and stopper 72c, 172c, wherein, supporting walls 72a, 172a is by outer shaft 45b, the annular end wall that 146 periphery can support axially slidably, stopper 72b, 172b is not expanding constantly adjusting when centrifugal weight 76,176 centrifugal weights 76 when not being operated (namely not expanding), 176 stop position, and stopper 72c, the maximum of adjusting when centrifugal weight expands to maximum expands position (dot and dash line that unexpected misfortune replaces in by Fig. 2 and Fig. 3 illustrates) to 172c expanding constantly.

When by input speed Ni or (be the rotating speed of interior axle 44b, clutch Outside spare 72 or the pressing member 75 of gear carrier 40 by the elementary output speed Na as the rotating speed of input speed Ni after with gear ratio r1 speed change more specifically, the example of elementary output speed Na has been shown among Fig. 6) when the centrifugal force that produces increased, centrifugal weight 76 contacted with each other by pressing member 75 and a plurality of clutch plate 73,74.When by elementary output speed Na or more specifically by as should be elementary the centrifugal force that produces through the output speed No (being the rotating speed of gear carrier 140, clutch Outside spare 172 or pressing member 175) of the rotating speed of variable-speed unit M2 after with gear ratio r2 speed change of output speed Na when increasing, centrifugal weight 176 contacts with each other by pressing member 175 and a plurality of secondary clutch sheets 173,174.

The a plurality of centrifugal weights 76,176 that consist of primary and secondary centrifugal weight group circumferentially arrange equally spacedly and supported wall 72a, 172a support so that centrifugal weight 76,176 can by act on centrifugal weight 76,176 centrifugal force radially outward expands.Each centrifugal weight 76,176 are provided with fulcrum part 76a, 176a, push mechanism 76d, 176d, contact component 76b, 176b and contact component 76c, 176c, wherein, fulcrum part 76a, 176a can with each gear carrier 40,140 flange 52 is by each taper dish shape spring 48 as intermediate member, 148 each supports 47 that arrange, 147 contacts, push mechanism 76d, the pressure F 1c of 176d by producing based on the centrifugal force when centrifugal weight expands, F2c promotes each the supporting walls 72a as functional component, 172a, contact component 76b, 176b in operation not constantly when centrifugal weight is not operated and each stopper 72b, 172b contact, and contact component 76c, 176c is expanding constantly when centrifugal weight expands to maximum and each stopper 72c, the 172c contact.Being arranged in each taper dish shape spring 48,148 between fixed wall 45c, the 146c regulates by key and is arranged on each support 47 on each clutch Outside spare 72,172,147 move axially.

Clutch housing 16 (seeing Fig. 1) has the high rigid element as thick section with primary and secondary centrifugal weight 76,176 relative positions in the radial direction.

In clutch 70, pressure F1c makes clutch 70 enter the engaging force of complete jointing state, and the second elementary axial force F 1a is that the joint that makes clutch 70 enter the state of being disengaged is removed power.Similarly, in secondary clutch 170, second subprime pressure F2c makes clutch 170 enter the engaging force of complete jointing state, and axial force F 2a to be the joint that makes clutch 170 enter the state of being disengaged remove power.

Along with increase pressure F1c, the F2c of centrifugal force greatly when overcoming axial force F 1a, F2a in each fulcrum part 76a, 176a and the state that respective holder 47,147 contacts, each centrifugal weight 76,176 to be waving and to expand centered by fulcrum part 76a, the 176a separately, and push mechanism 76d, 176d promote respective support wall 72a, 172a with mobile each clutch Outside spare 72,172 axially by pressure F1c, F2c.At this moment, pressing member 75,175 and clutch Outside spare 72,172 jointly move axially, axially oppress each clutch plate 73,74,173,174 and each clutch plate is contacted with each other towards the fixed wall 45c, the 146c that become one with outer shaft 45b, 146, by the frictional force between each clutch plate 73,74,173,174 that contacts with each other, the rotation of gear ring 50 or sun gear 130 is passed to clutch Outside spare 72,172 and gear carrier 40,140 by each clutch plate 73,74,173,174.

The centrifugal weight 176 of secondary clutch 170 has the structure that produces the larger second pressure F2c of primary pressure F1c that the centrifugal weight 76 than primary clutch 70 produced when clutch Outside spare 72,172 during with the rotation of same rotating speed.In the present embodiment, with regard to this pouring weight structure, so that the quality of centrifugal weight 176 is set to is larger than the quality of centrifugal weight 76.More specifically, set centrifugal weight 76,176 quality, so that when input speed Ni reaches the second predetermined speed N2 (seeing Fig. 6) of conduct the first specific rotation speeds that hereinafter will describe, second pressure F2c is larger than primary pressure F1c, the pressing member 175 that moves right and is removed the complete jointing state of clutch 70 so that the pressing member 75 that makes clutch 70 enter complete jointing state moves right.

As another example, the pouring weight structure also can be make fulcrum part 176a in the centrifugal weight 176 and the distance between the push mechanism 176d be set to than in the centrifugal weight 76 fulcrum part 76a and the short structure of the distance between the push mechanism 76d, in addition, also can use together these structures.

When each centrifugal weight 76,176 was in stop position, each clutch 70,170 was in the state of being disengaged, and was disengaged in the state at this, and rotation is not by paired clutch plate 73,74 and in pairs clutch plate 173,174 transmission.When each centrifugal weight 76,176 is positioned at maximum and expands the position, each clutch is in complete jointing state, in this complete jointing state, each clutch inner piece 71,171 and each clutch Outside spare 72,172 (thus gear ring 50 and gear carrier 40 and/or sun gear 130 and gear carrier 140) with constant speed rotation and each clutch plate 73,74; 173, do not slide between 174.When the centrifugal weight 76,176 that respectively expands is in stop position and the maximum clutch plate 73,74 that expands the neutral position between the position and contact with each other at this place, neutral position; 173, exist when sliding between 174, each clutch is in half jointing state (or clutch part jointing state), in this half jointing state, in each clutch plate 73,74; 173, under 174 conditions of sliding, the rotation of each clutch inner piece 71,171 (thus gear ring 50 or sun gear 130) is passed to each clutch Outside spare 72,172 (thus each gear carrier 40,140).

Speed changer M is equipped with the clutch linkage D as gear ratio change mechanism of the gear ratio r1 of the variable-speed unit M1 of input shaft 20 sides in the bang path that changes a plurality of variable-speed unit M1, the M2 that are arranged in speed changer M.Clutch linkage D is that the complete jointing state of removing clutch 70 makes its mechanism that enters the state of being disengaged, and is provided with as the push mechanism 134 of driver part and the pressing member 75 that the driving force of push mechanism 134 is passed to clutch 70 with the intermediate transfer member 36 as the Separating force of cut-off clutch 70.

Intermediate transfer member 36 be provided with the tubulose first intermediate transfer members 37 that can axially contact with push mechanism 134 with can with the first intermediate transfer member 37 axial tubulose the second intermediate transfer members 38 that contact.The first and second intermediate transfer members 37,38 rotatable and can support by output shaft 23 with moving axially.

The second intermediate transfer member 38 is provided with the flexible part 39 with spring 39a, and spring 39a is as the resilient member for the promotion member of controlling between axial two ends.Comprise as the spring 39a of resilient member one or more, four taper dish shape spring 39b for example in the present embodiment.An end in contact that is consisted of by flexible part 39 in the first intermediate transfer member 37 and the second intermediate transfer member 38, and the other end that is made of thrust bearing B 13 in the interior axle 51 of gear ring 50 and the second intermediate transfer member 38 contacts.

When two clutches 70,170 all are in when being disengaged state, form between two intermediate transfer members 37,38 and make these two intermediate transfer members 37,38 enter the axially spaced-apart that is in the state that contacts with each other of complete jointing state when clutch 70.

The the first intermediate transfer member 37 that promotes when push mechanism 134 contacts with the second intermediate transfer member 38 and being moved to the left when being prevented from of the second intermediate transfer member 38, spring 39a promotes pressing member 75 by gear ring 50, so that overcoming the pressure F1c that spring force causes, centrifugal weight 76 is in halted state, so that pressing member 75 is in pressure release position.

When elementary clutch 70 is in complete jointing state, expand and secondary clutch 170 enters the process of complete jointing state from being disengaged state in the growth of centrifugal weight 176 by the rotating speed of the gear carrier 140 of planetary gears P2, sun gear 130 moves right along with moving right of pressing member 175, and push mechanism 134 promotes the first and second intermediate transfer members 37, the 38 and second intermediate transfer member 38 contacts with interior axle 51.At this moment, because the pressure F2c that centrifugal weight 176 puts on pressing member 175 puts on the pressure F1c of pressing member 75 greater than centrifugal weight 76, the driving force of push mechanism 134 promotes gear carrier 40 and pressing members 75 and they is moved right by the first and second intermediate transfer members 37,38.By moving axially of pressing member 75, clutch 70 enters the state of being disengaged through the part jointing state.

In order to remove the complete jointing state of primary clutch 70, pressure F2c only needs specific pressure F1c larger.Simultaneously, being pushed parts 134 at clutch 70 promotes also in case after entering the state of being disengaged, when input speed Ni increase to surpass when again entering complete jointing state as the 3rd predetermined speed N3 (seeing Fig. 6) of the second specific rotation speeds and clutch 70, because the mechanical axis that flexible part 39 overcomes spring 39a is to shortening, pressure F1c left moves pressing member 75 and clutch 70 enters complete jointing state.Therefore, the power of spring 39a is the control force of the input speed Ni of regulation centrifugal weight 76 when again expanding.

Such as Fig. 3 and Fig. 4, the below will illustrate overrunning clutch 80,180.Owing to two overrunning clutchs 80,180 have essentially identical structure, Fig. 4 also illustrates the mark of the member that is associated with overrunning clutch 80.

The sun gear 30 of prevention planetary gears P1 is equipped with by annular element 33 along the secondary overrunning clutch 180 that a direction A1 rotates along overrunning clutch 80 and the prevention gear carrier 140 of the rotation of a direction A1; 152 back shafts of equipping 89; 189 can unsteadily support and be positioned at one or more counterparts of rotation side, in this embodiment, comprise two pairs of ratchets 81, the 82 or two pairs of ratchets 181,182, external member T and spring 84,184, wherein, external member T is provided with as passing through as the rotation adjusting member and cooperates each ratchet 81,82 at a direction A1; 181, the 182 a plurality of claws 83 that stop the rotational speed regulation side counterpart that sun gear 30 or gear ring 150 rotate at a direction A1; 183, and spring 84,184 is as promoting member at each ratchet 81,82; 181,182 and each claw 83; Promote each ratchet 81,82 on 183 directions that cooperate; 181,182.When spring inserts respectively annulus 33; 152 and ratchet 81,82; 181, after in 182 matching hole K1, the K2 that equip, spring 84; 184 by annulus 33; 152 and ratchet 81,82; 181,182 keep.

In the radial direction from each ratchet 81,82 of outer side covers; 181,182 external member T is and two overrunning clutchs 80, the 180 single tubular members that share and be formed on the in the radial direction annulus S 1 between external member and interior axle 44b.External member T by case of transmission 16 by becoming one with external member T and supporting from the outward extending supporting member of the periphery of external member T 65 in the radial direction.Supporting member 65 is bolted the assembly parts 16a (seeing Fig. 1) to case of transmission 16.

Each ratchet 81,82; 181,182 be provided with and each claw 83; 183 component 81a, the 82a that match; 181a, 182a and weight element 81b, 82b; 181b, 182b.Ratchet 81,82; 181,182 can be owing to acting on weight element 81b, 82b; Centrifugal force on 181b, the 182b and waving is until component 81a, 82a; 181a, 182a are arranged in not contact position (replacing shown in the dot and dash line such as Fig. 4 unexpected misfortune), this not contact position place component do not overcome spring 84; 184 thrust and claw 83; 183 component 85a; 185a matches.Contact position is not by each annular element 33; 152 stoppers that assemble 87; 187 limit.When ratchet 81,82; 181,182 when being in not contact position, each ratchet 81,82; 181,182 radial outsides and claw 83; 183 or relative whole outside 81c, the 82c of external member T; 181c, 182c in axial view, be positioned at a concentric imaginary circle 88 of rotation centerline L1, L2 on and radially be positioned at imaginary circle 88.

Radially stretch to ratchet 81,82; 181, near the claw 83 182; 183 are provided with and have separately component 85a; The main body 85 of 185a; 185 and the tilt component 86 that on the opposite sense of rotation A2 that allows sun gear 30 or gear ring 150 rotations, radially stretches out gradually; 186.When ratchet 81,82; 181,182 not with component 85a; During the 185a contact, ratchet 81,82; 181,182 by spring 84; 184 promote and with tilt component 86; 186 contacts.Because tilt component 86; 186 by conduct and component 85a; The rubber material of the elastic material of 185a sintering is made, and the work that tilt component plays buffer unit is in order to by tilt component and ratchet 81,82; 181,182 contacts come damping vibration and reduce noise.

A pair of ratchet 81 and a pair of ratchet 181 arrange symmetrically with respect to rotation centerline L1, the L2 of central authorities that respectively another is arranged symmetrically with respect to rotation centerline L1, the L2 of central authorities respectively ratchet 182 ratchet 82 and another, and works as each to ratchet 81,82; 181,182 are positioned at each to ratchet and mating part 85a separately; During cooperation position that 185a matches, another to ratchet be disposed in another to ratchet not with component 85a separately; The not cooperation position that 185a matches.Can increase thus when all ratchets 81,82; 181,182 when never cooperation position rotates along direction A1 with respect to external member T and component 85a; The probability that 185a matches, and ratchet can promptly enter the rotation stopping state.

As shown in Figures 2 and 3, whole elementary anastomosis part H1 and whole secondary engagement part H2 are arranged in a gear chamber 19, this gear chamber 19 by mutually axially spaced as the first side wall pressing member 75 and as the pressing member 175 of the second sidewall, respectively between two pressing members 75,175 axially extended clutch Outside spare 72,172, as two outer shaft 45b of the circumferential wall of gear, 146 and the circumferential wall of tubulose that formed by the external member T as the exterior circumferential wall formed.Gear chamber 19 is the spaces that are formed in the case of transmission 16.

Pressing member 75 and axially the gear sidewall 54 between pressing member 75 and anastomosis part H1 jointly be formed in the double-walled that comprises from axial direction in the whole of two anastomosis part H1, H2 or the substantially whole radial extension, and pressing member 175 and axially the gear sidewall 133 between pressing member 175 and anastomosis part H2 jointly be formed in the double-walled that comprises from axial direction in the whole of two anastomosis part H1, H2 or the substantially whole radial extension.

The first and second adjusting member 61,62 are disposed between two outer shaft 45b, 146, wherein outer shaft 45b, 146 as two outer shaft 45b, 146 axis towards each other near supporting part 45d, the 146d of relative end radially from outer side covers external member T.Because the first and second adjusting member 61,62 and supporting member 65 radially from two outer shaft 45b of outer side covers, 146 and external member T, vertically two outer shaft 45b, 146 and external member T on two outer shaft 45b, 146 and external member T between comprise interface.Can further reduce thus the noise that the joint sound owing to two anastomosis part H1, H2 produces.

Because clutch Outside spare 72 and outer shaft 45b, clutch Outside spare 172 and outer shaft 146 and each outer shaft 45b, 146 and external member T include axially upper mutually stacked overlapping part, can reduce the axial width of circumferential wall, by in as the circumferential wall of gear chamber 19 wall in the radial direction, partly forming double-walled, can strengthen two anastomosis part H1, H2 joints and the effect that the noise of generation reduces, and two variable-speed unit M1, M1 in the axial direction can be compacter.

As depicted in figs. 1 and 2, the output shaft 23 that is provided with the outrigger shaft 27 that axially extends from variable-speed unit M2 left makes the output that is arranged on driving mechanism 90 outlet sides derive axle 91 rotations.Driving mechanism 90 also is provided with output gear 92 except axle 91 is derived in output, driven gear 93 and neutral gear clutch 95, wherein, the conduct of being located at outrigger shaft 27 drives the output gear 92 of rotor in such position, this position, axially between driving mechanism and variable-speed unit M2 and in the prespecified range W of outrigger shaft 27, around the space S 2 of outrigger shaft 27 formation around the outer circumferential face 27a of outrigger shaft, driven gear 93 rotatably is located at output as driven rotor and is derived axle 91 and driven by engaging with output gear 92, and neutral gear clutch 95 is passed to the rotation of output gear 92 output derivation axle 91 and disconnects this transmission.

Whole output is derived axle 91 and is arranged in axially overlapping with variable-speed unit M2 position.Having derives axle 91 with the output of the parallel rotation centerline of rotation centerline L1, L2 and is provided with among prespecified range Ws the axially extended inner outrigger shaft 93a relative with driven gear 93 and runs through the outside outrigger shaft 93b that half casing 3b stretches out the 15a of crankshaft room.Outside outrigger shaft 93b is equipped with the driving sprocket wheel 97a of the final output block of conduct that is twining chain 97b.

The end of inner outrigger shaft 93a by as with crankcase 3 independently the bearing 16b that equips of the case of transmission 16 of member support by bearing B14.Output is derived axle 91 and is rotatably supported by the bearing B15 between driving sprocket wheel 97a and driven gear 93 by half casing 3b.

Output gear 92 and driven gear 93 consist of the rotational speed N o that limits reduction output shaft 23 and the reducing gear that further output speed No is carried out the outlet side gear ratio of speed change.The rotation of output shaft 23 is passed to driving sprocket wheel 97a outlet side driving mechanism 90 and axially be arranged in the both sides of two variable-speed unit M1, M2 as the reducing gear 18 of input side driving mechanism.

Neutral gear clutch 95 is arranged in outrigger shaft 93a upward and is arranged in the prespecified range W.Neutral gear clutch 95 is provided with by key and output derivation axle 91 and rotates integratedly and the shift unit 95a that can cooperate with driven gear 93 and the selector fork 95b that is operated and axially movably driven shift unit 95a by clutch operating member (not shown).

Input to output in the rotation of can axially movable shift unit 95a on the outrigger shaft 93a output gear 92 being transmitted by driven gear 93 during when the activation point that is positioned at shown in Fig. 2 solid line and derive axle 91, and derive speed ratio that axle 91 sets according to driving mechanism 90 with output and the rotational speed N o of output shaft 23 is adjusted the rotating speed that obtains be rotated.When shift unit 95a is in when replacing neutral position shown in the dot and dash line such as unexpected misfortune among Fig. 2, shift unit 95a disconnects the transmission that axle 91 is derived in output that rotates to of output shaft 23.

To Fig. 5 (d) and shown in Figure 6, the below will illustrate the operation of speed changer M such as Fig. 1, Fig. 5 (a).

Main shown in Fig. 5 (a), when internal-combustion engine E was started, engine speed was that the rotating speed of bent axle 6 is combined above idling speed and centrifugal clutch 17, the input speed Ni rotation that input shaft 20 and gear ring 50 are transmitted with reducing gear 18.At this moment, when input speed Ni was equal to or less than the first predetermined speed N1, the sun gear 30 of the overrunning clutch 80 prevention planetary gears P1 among the variable-speed unit M1 was stopped along rotation and the sun gear of a direction A1 (seeing Fig. 4).Therefore, in planetary gears P1, the rotating speed rotation of gear carrier 40 so that input speed Ni is slowed down and obtained with gear ratio r1 through planetary gears P1, gear ring 50 promotes to the right with the oppressed member 75 of axial force F 1a that produces that engages of gear ring 50 by planetary pinion 41 in the clutch 70, pressing member 75 is in pressure release position, clutch plate 73,74 disconnected from each other, centrifugal weight 76 is positioned at stop position and clutch 70 is in the state of being disengaged.

In addition, in variable-speed unit M2, the gear ring 150 of overrunning clutch 180 prevention planetary gears P2 is stopped along rotation and the gear ring of a direction A1 (seeing Fig. 4).Therefore, in planetary gears P2, the rotating speed rotation of gear carrier 140 slowing down and be obtained with gear ratio r2 through planetary gears P2 with the rotating speed of the sun gear 130 of gear carrier 40 same rotational speed of planetary gears P 1, sun gear 130 promotes pressing member 175 by planetary pinion 141 in the clutch 170 left with the axial force F 2a that produces that engages of sun gear 130, pressing member 175 is in pressure release position, clutch plate 173,174 disconnected from each other, centrifugal weight 176 is positioned at stop position and clutch 170 is in the state of being disengaged.

Under this state, speed changer M obtains one grade of gear ratio R1 by two gear ratio r1, r2 are multiplied each other, and output shaft 23 is with by being rotated input speed Ni through the rotating speed that one grade of gear ratio R1 speed change as the maximum gear ratio of speed changer M obtains.When neutral gear clutch 95 (seeing Fig. 2) is positioned at activation point, the rotation of output shaft 23 is input to output by output gear 92 and driven gear 93 and derives axle 91.

Main shown in Fig. 5 (b), when input speed Ni surpasses the first predetermined speed N1 and be less than or equal to than higher the second predetermined speed N2 of the first predetermined speed N1, along with the rotating speed of the gear carrier 40 of clutch 70 increases, the centrifugal weight 76 that surpasses among axial force F 1a and the variable-speed unit M1 based on the pressure F1c of the centrifugal force that acts on centrifugal weight 76 expands.Centrifugal weight 76 is positioned at maximum and expands the position, and pressing member 75 is moved to the left gear ring 50, and pressing member promotes clutch plate 73,74 contacts with each other it, and clutch 70 enters complete jointing state.Therefore, gear ring 50, gear carrier 40 and sun gear 30 become " 1 " with input speed Ni with direction A2 (seeing Fig. 4) rotation and the gear ratio r1 opposite with direction A1, and namely gear is in the state of being driven directly.

Simultaneously, in variable-speed unit M2, along with the rotating speed of gear carrier 140 increases, be equal to or less than axial force F 2a based on the pressure F2c of the centrifugal force that acts on centrifugal weight 176, centrifugal weight 176 is in halted state.Therefore, planetary gears P2 and clutch 170 are in state same when being set as one grade of gear ratio R1.

Under this state, speed changer M obtains two gear gear ratio R2.

Main shown in Fig. 5 (c), when input speed Ni surpasses the second predetermined speed N2 and be less than or equal to than higher the 3rd predetermined speed N3 of the second predetermined speed N2, along with the rotating speed of secondary clutch 170 middle gear framves 140 increases, the centrifugal weight 176 that surpasses among axial force F 2a and the secondary variable-speed unit M2 based on the pressure F2c of the centrifugal force that acts on centrifugal weight 176 expands.Centrifugal weight 176 is in maximum and expands the position, and pressing member 175 sun gear 130 that moves right, pressing member promote clutch plate 173,174 contacts with each other it, and secondary clutch 170 enters complete jointing state.Therefore, gear ring 150, gear carrier 140 and sun gear 130 are that elementary output speed Na becomes " 1 " with direction A2 (seeing Fig. 4) rotation and gear ratio r2 with a direction A1 opposite direction with the rotating speed of gear carrier 40, and namely gear is in the state of being driven directly.

The three class gear shift that becomes the high-speed side gear ratio higher than second gear gear ratio R2 at the second gear gear ratio R2 from the low speed side gear ratio is during than R3, begin through more than half jointing states until the process of complete jointing state from being disengaged state at clutch 170, sun gear 130 moves right integratedly with the pressing member 175 that moves right, push mechanism 134 moves right the first and second intermediate members 37,38, further by gear ring 50 so that the pressing member 75 of clutch 70 moves right, the direction that namely is disengaged towards the complete jointing state of clutch 70 moves.

Therefore, in clutch 70, centrifugal weight 76 expands position movement to stop position from maximum, clutch 70 enters the state of being disengaged from complete jointing state through more than half jointing states, and is rotated with the rotating speed that obtains after will input speed Ni slowing down through gear ratio r1 with the clutch Outside spare 72 of input speed Ni rotation and gear carrier 40 respectively.By making the stopper 135 of regulating pressing member 175 and the amount of movement of sun gear 130 contact to stop pressing member 175 and sun gear 130 movement to the right with the left end of the interior axle 44b of gear carrier 40.

Under this state, speed changer M reaches the three class gear shift that equates with the gear ratio r1 of variable-speed unit M1 and compares R3.

Becoming the process of three class gear shift than R3 from two gear gear ratio R2, when time detection unit 13c detects two clutches 70 by clutch jointing state detection unit 13b, when the time remaining that at least one in 170 enters half jointing state and enter half jointing state surpasses the scheduled time, controller 13 is by the air throttle 8a as corresponding revolution speed control device, at least one controls air inflow in Fuelinjection nozzle 9 and the ignition mechanism 10, the output-controlled variable of in fuel duty and the ignition timing at least one, thereby the clutch 170 that changes input speed Ni half jointing state so that input speed Ni increases to enters complete jointing state or so that the clutch 70 of half jointing state enters the input speed Ni of the state of being disengaged, promptly half jointing state of conversion clutch 70 or clutch 170 and advance two gear gear ratio R2 to the transformation of three class gear shift than R3.

On the contrary, the process that becomes two gear gear ratio R2 from three class gear shift than R3, the revolution speed control device of controller 13 control changes input speed Ni, and the clutch 70 of half jointing state enters complete jointing state or so that the clutch 170 of half jointing state enters the input speed Ni of the state of being disengaged so that input speed Ni is reduced to.

Similarly, the process that becomes second gear gear ratio R2 from a gear gear ratio R1 and becoming the process of four-speed gear shift than R4 from three gear gear ratio R3, when time detection unit 13c detected half jointing state that detects clutch 70 by clutch jointing state detection unit 13b and continue to surpass the scheduled time, controller 13 changes input speed Ni by revolution speed control device, and clutch 70 entered the input speed Ni of complete jointing state so that input speed Ni increases to.The process that becomes one grade of gear ratio R1 from two gear gear ratio R2 and becoming than R4 the process of three class gear shift than R3 from four-speed gear shift, when time detection unit 13c detects half jointing state that detects clutch 70 by clutch jointing state detection unit 13b and continue to surpass the scheduled time, controller 13 makes it change input speed Ni by the control revolution speed control device, and clutch 70 enters the input speed Ni of the state of being disengaged so that input speed Ni is reduced to.

Main shown in Fig. 5 (d), when input speed Ni surpassed the 3rd desired speed N3, planetary gears P2 was in and state identical when variable-speed unit M2 is in three class gear shift than R3 with clutch 170.

Simultaneously, in speed changer M1, the first and second intermediate transfer members 37,38 are pushed away to the right and pressing member 75 is pushed away to the right by the power of spring 39a under the state of (namely towards the direction of connect removing) at pressure F2c, along with the rise of rotational speed according to the gear carrier 40 in the clutch 70 of input speed Ni, pressure F1c surpasses the power of spring 39a, and centrifugal weight 76 expands.Centrifugal weight 76 is positioned at maximum and expands the position, and pressing member 75 is so that gear ring 50 is moved to the left and promotes clutch plate 73,74 contacts with each other, and clutch 70 enters complete jointing state.Therefore, gear ratio r1 becomes " 1 ", and namely variable-speed unit M1 is driven directly.

Because two gear ratio r1, the r2 of two variable-speed unit M1, M2 all become " 1 ", speed changer M is driven directly, thus the four-speed gear shift that reaches lowest transmission ratio than R4, and output shaft 23 is rotated with input speed Ni.

The effect of above-mentioned mode of execution then will be described.

In speed changer M, because each gear ratio control unit C1, C2 are equipped with overrunning clutch 80,180 and only be equipped with the overrunning clutch 25 that the rotation of output shaft 23 is passed to during above input speed Ni input shaft 20 as output speed No at the rotation bang path between input shaft 20 and the output shaft 23, the rotation of output shaft 23 is walked around planetary gears P1, P2 by overrunning clutch 25 and is passed to input shaft 20 in the speed reduction of motorcycle process, and wherein the rotation of trailing wheel 98 is passed through output shaft 23 so that input shaft 20 rotations.Therefore, also can carry out work in four-speed gear shift that speed changer M is driven directly than the engine brake in the situation of R3 of the gear ratio R1 outside the R4, engine brake can (or at gear ratio R1 to R4) work under all rotating speeds thus.

Because input shaft 20 and planetary gears P1, P2 are rotatably supported by output shaft 23 on output shaft 23 radial outside ground, the end 21a of input shaft 20 is provided with the enlarged-diameter part with axially open, overrunning clutch 25 is set on the end 21a of input shaft 20 by the radially inner side that overrunning clutch 25 is arranged in the enlarged-diameter part, in addition, overrunning clutch separates with the axially open of enlarged-diameter part.Therefore be conducive to dismantle overrunning clutch 25.

In speed changer M, the anastomosis part H1 of planetary gears P1 and the anastomosis part H2 of planetary gears P2 are contained in the gear chamber 19, wherein, gear chamber 19 by the pressing member 175 of the pressing member 75 of spaced-apart in the axial direction clutch 70 and clutch 170, consist of between two pressing members 75,175 (namely axially in two pressing members 76,175 inboard) two gear carriers 40 of axially extended circumferential wall, 140 outer shaft 45b, 146 and overrunning clutch 80,180 external member T form.The gear ring 50 of planetary gears P1 is equipped with the gear sidewall 54 between pressing member 75 and anastomosis part H1, the sun gear 130 of planetary gears P2 is equipped with the axially gear sidewall 133 between pressing member 175 and anastomosis part H2, and in pairs pressing member 75 and gear sidewall 54 and pressing member 175 and gear sidewall 133 are formed in respectively double-walled in the radial extension that comprises two anastomosis part H1, H2 in the axial view in pairs.

Because this structure, be equipped with primary and secondary planetary gears P1, P2 and primary and secondary clutch 70,170 primary and secondary variable-speed unit M1, M2 are positioned at a shared gear chamber 19, the member that consists of two variable-speed unit M1, M2 can be shared and can reduce cost by the quantity that reduces parts.In addition, can arrange compactly member of formation by sharing member of formation, and can make speed changer M miniaturization.

Because be contained in two anastomosis part H1 in the gear chamber 19 that is formed in crankcase 3 and the case of transmission 16, H2 is in the radial direction by two outer shaft 45b, 146 and external member T from outer side covers, utilize in the axial direction and consist of two variable-speed unit M1, the double-walled that the member of M2 forms by oppressed member 75 and gear sidewall 54 and the double-walled that is formed by pressing member 175 and gear sidewall 133 cover from both sides, so except passing through two outer shaft 45b, 146 and the noise reduction of external member T outside, the double-walled construction of axial direction upper side wall also can strengthen because each anastomosis part H1, the joint of H2 and the noise reduction of the noise that produces.

Because pass through by two planetary gears P1, the gear carrier 40 of P2,140 outer shaft 45b, 146 and as two overrunning clutchs 80, the external member T of 180 share components is formed in the radial direction from two anastomosis part H1 of outer side covers, the circumferential wall of H2, use and consist of two variable-speed unit M1, the circumferential wall of the member of M2 and the gear chamber 19 that forms is except as using two planetary gears P1, each gear carrier 40 of P2, the outer shaft 45b of 140 the circumferential wall of primary and secondary gear, outside 146, also comprise two overrunning clutchs 80 of conduct as circumferential wall, the external member T of 180 share components, consist of two variable-speed unit M1 so consist of the structure of the circumferential wall of gear chamber 19 by sharing, two overrunning clutchs 80 that M2 is provided with, 180 member and being simplified, and member of formation can be arranged compactly.In addition, two overrunning clutchs 80,180 can be arranged compactly.

Because gear ratio control unit C1 is equipped with the rotational speed N i that has according to input shaft 20 so that a plurality of separable clutch plate 73, the clutch 70 of the pressing member 75 of 74 contacts or separation, gear ratio control unit C2 is equipped with the elementary output speed Na that has according to gear carrier 40 so that a plurality of separable clutch plate 173, the clutch 170 of the pressing member 175 of 174 contacts or separation, and the outer side wall of the double-walled of gear chamber 19 can pass through by two clutches 70,170 separately pressing member 75,175 consist of the axial double side wall of formative gear chambers 19 and use two clutches 70, each pressing member 75 of 170,175 consist of, do not make such as planetary gears P1, the primary and secondary element gear of the gear ring 40 of P2 and sun gear 130 increases to fall in the low noise situation in the radial direction size, can reduce because each anastomosis part H1, the joint of H2 and the noise that causes.

Because 175 rotations that will be obtained by the gear ratio R of variable-speed unit M1, M2 of the pressing member of clutch 70 input to the function of the secondary output rotor of output shaft 23, the function of the noise that 175 reductions of the pressing member of the joint of solenoidoperated cluthes 170 produce owing to the joint of each anastomosis part H1, H2 and rotation is passed to the function of output shaft 23 is so can reduce number of components.

Among the speed changer M, by being overrunning clutch 80,180 provide be arranged as axially the external member T that shares between the anastomosis part H2 of the anastomosis part of planetary gears P1 H1 and planetary gears P2, so that overrunning clutch 80,180 are equipped with as sharing the rotation adjusting member and being provided with planetary gears P1, P2 and gear ratio control unit C1, the variable-speed unit M1 of C2, utilize among the M2 and axially be formed at two anastomosis part H1, the external member T that space between the H2 is arranged consists of overrunning clutch 80 so can share, 180 member and can reduce cost by the quantity that reduces parts.

Because be equipped with the axially movable adjusting member 60 with the gear ring 150 of planetary gears P2 of moving axially of the sun gear 30 of regulating planetary gears P1, and by external member T being fixed to the adjusting member 60 that is fixed on the case of transmission 16, use to regulate planetary gears P1, the sun gear 30 of P2 and the separately axially movable adjusting member 60 of gear ring 150 and fix external member T, so do not need the Special support member to come supports outer member T and can reduce the quantity of parts.

Because speed changer M is equipped with a thrust bearing 46, the sun gear 30 that engages the axial force F 1b effect that produces of the sun gear 30 that wherein is subject to planetary gears P1 and the planetary pinion 41 of gear carrier 40 and the gear ring 150 that is subject to planetary gears P2 are oppressed this thrust bearing 46 with the gear carrier 140 of the axial force F 2b effect that engages generation of the planetary pinion 141 of gear carrier 140 at each axial opposite direction, and come so that be provided with planetary gears P1 between the compressing parts 34 by thrust bearing 46 axially being arranged in sun gear 30 and the compressing parts 153 of gear carrier 140, the variable-speed unit M1 of P2, thrust bearing that shares 46 preventions among the M2 are subject to planetary gears P1, joint among the P2 and each axial force F 1b of producing, the sun gear 30 of F2b effect and moving axially of gear carrier 140, planetary gears P1, P2 shares this thrust bearing 46 and can reduce cost by the quantity that reduces parts.

Because be subject to the sun gear 30 of each axial force F 1b, F2b effect and the thrust bearing 46 that gear carrier 140 shares with each opposite direction compressing in the axial direction, thereby two structures that axial force F 1b, F2b cancel each other at thrust bearing 46 places and reduce with joint efforts and simplify thrust bearing 46.

Because by only being provided as the thrust bearing 46 of annular construction member for the interior axle 44b of gear carrier 40 and sun gear 30 and gear carrier 140 axially being arranged in the both sides of thrust bearing 46, can only use the interior axle 44b as the elementary output rotor that the rotation after the variable-speed unit M1 speed change is inputed to variable-speed unit M2 that thrust bearing 46 is set, so except interior axle 44b, do not need for the member that supports thrust bearing 46.Can reduce thus the quantity of parts and the structure of simplification speed changer M.

Because sun gear 30 and gear carrier 140 axially are arranged in the both sides of thrust bearing 46, sun gear 30 and gear carrier 140 can arrange compactly in the axial direction that therefore two variable-speed unit M1, M2 can arrange in the axial direction compactly.

Because thrust bearing 46 is arranged in the space S 1 that is centered on by the overrunning clutch 80 that stops sun gear 30 and gear carrier 140 along a direction A1 rotation, 180 external member T, sun gear 30 and gear carrier 140 can utilize by the overrunning clutch 80 of the sense of rotation of regulating sun gear 30 and gear carrier 140,180 the formed space S 1 of external member T and arrange thrust bearing 46, so can be arranged in the axial direction compactly.

Because the gear carrier 40 by regulating planetary gears P1 for speed changer M equipment move axially axially movable shared adjusting member 60 with the gear carrier 140 of planetary gears P2, and be adjusting member 60 equipment regulating tooth wheel carriers 40 at the axially movable supporting lip 61b on the both direction and regulating tooth wheel carrier 140 the axially movable supporting lip 62b on both direction, be equipped with planetary gears P1, P2 and gear ratio control unit C1, the variable-speed unit M1 of C2, planetary gears P1 among the M2, two gear carriers 40 of P2,140 move axially separately by common adjusting member 60 regulated, so adjusting member 60 is by planetary gears P1, P2 shares and can reduce cost by the quantity that reduces parts.

Because two gear carriers 40,140 moving axially separately on both direction can be regulated by independently supporting lip 61b, 62b, can improve the degrees of freedom of being regulated its axially movable each gear carriers 40,140 layout by adjusting member 60.

Because adjusting member 60 comprises the first adjusting member 61 that is provided with the first supporting lip 61b and the second adjusting member 62 that is provided with the second supporting lip 62b, and by with on the interconnected assembly parts 16a that is connected to simultaneously case of transmission 16 of the first adjusting member 61 and the second adjusting member 62, member became one when the first and second adjusting member 61,62 were connected to case of transmission 16, was simplified so be used for connecting the structure of adjusting member 60.

Because each first and second adjusting member 61,62 are provided with axially extended cylindrical parts 61a, 62a, from cylindrical parts 61a, each supporting lip 61b that the tip side of the axial direction of 62a is radially extended, 62b and from each cylindrical parts 61a, the base flange 61c that the base portion of the axial direction of 62a radially extends, 62c, by with the first and second adjusting member 61,62 base flange 61c, 62c is connected to each other base flange when being connected to assembly parts 16a, be equipped with cylindrical parts 61a, 62a and supporting lip 61b, the first and second adjusting member 61 of 62b, 62 by base flange 61c, 62c is connected to each other, so be that the rigidity that the situation of flat element is compared adjusting member 60 is strengthened with adjusting member.In addition, because rigidity is very high, adjusting member 60 can be made by the thin material that is easy to process.

Because adjusting member 60 is connected to case of transmission 16 jointly with the supporting member 65 that supports overrunning clutch 80,180 external member T, so the quantity of parts and the quantity of rigging position are reduced, and the structure that be used for to connect adjusting member 60 and supporting member 65 is simplified.

In speed changer M, the clutch 70 of variable-speed unit M1 is equipped with a plurality of mutual discerptible clutch plate 73,74 and along with the increase of the centrifugal force that is produced by input speed Ni so that a plurality of clutch plate 73,74 centrifugal weights that contact with each other 76, the clutch 170 of variable-speed unit M2 is equipped with a plurality of clutch plate 173 that can be separated from each other, 174 and the increase of the centrifugal force that produces along with the elementary output speed Na by variable-speed unit M1 so that a plurality of clutch plate 173,174 centrifugal weights that contact with each other 176, the controller 13 that internal-combustion engine E equips is provided with and detects in clutch 70 and the clutch 170 at least one and be in the clutch jointing state detection unit 13b of half jointing state and detect time detecting unit 13c by the endurance of detected half jointing state of clutch jointing state detection unit 13b, and by when the detected endurance of time detection unit 13c surpasses the scheduled time, the control gear that passes on of control inputs rotational speed N i being controlled to change input speed Ni, when two clutches 70, when half jointing state of at least one in 170 continues to surpass the scheduled time, controller 13 is so that the revolution speed control device of being controlled by controller 13 changes the rotational speed N i of input shaft 20 to enter complete jointing state, thereby and input speed changed into the rotating speed that becomes half jointing state, can promptly remove clutch plate 73 under half jointing state at this state, 74; 173,174 states that slide over each other.Therefore, stoped clutch plate 73,74; 173, the wearing and tearing between 174 can be strengthened centrifugal clutch 70,170 serviceability.Thereby, so that cornering ability is satisfactory and improve driving experience.

Because by the process that becomes complete jointing state at clutch 170 from being disengaged state clutch 70 being become the state of being disengaged from complete jointing state, centrifugal weight 176 can advance the transition of half jointing state when clutch 170 becomes complete jointing state from being disengaged state and become the transition of half jointing state when being disengaged state from complete jointing state when clutch 70, so can increase each clutch 70,170 serviceability is so that cornering ability is satisfactory and improve driving experience.

When clutch 170 enters complete jointing state and gear ratio r2 and is changed, the gear ratio that secondary gear ratio r2 when being in complete jointing state by making the clutch 70 that is in complete jointing state enter the state of being disengaged, can obtaining clutch 170 and clutch 70 are in the combination of the gear ratio r1 when being disengaged state.Therefore, the speed changer that does not enter the state of being disengaged with the clutch 70 that is in complete jointing state when input speed Ni increases is compared, and the gear ratio quantity that speed changer M can reach can be obtained by the planetary gears of smaller amounts.

Because clutch jointing state detection unit 13b is based on the gearshift state detection unit that the actual output speed No of actual input speed Ni and the output shaft 23 actual gear ratio of calculating and the speed change of presetting recently detect the gearshift state, each clutch 70,170 half jointing state recently detect by actual speed change, so strengthened the accuracy for the control of the transition that advances half jointing state.

Revolution speed control device is air throttle 8a, Fuelinjection nozzle 9 or igniting unit 10, and come the rotational speed N i of control engine rotating speed and control inputs axle 20 by at least one the output-controlled variable in air inflow, fuel duty and the ignition timing of controlling combustion engine E, can change half jointing state of each clutch 70,170.

For example, controller 13 does not compare by based on the testing result of clutch jointing state detection unit 13b clutch not being in the engine speed that engine speed under half jointing state and clutch be under half jointing state, when the height of the engine speed under half jointing state (perhaps low), determine to upgrade (or lowering category), and control air throttle 8a, in Fuelinjection nozzle 9 or the ignition mechanism 10 at least one controlled air inflow, in fuel duty and the ignition timing at least one, and increase (or minimizing) engine speed until change half jointing state of clutch 70 or clutch 170.

In speed changer M, output shaft 23 is equipped with the axially extended outrigger shaft 27 from secondary variable-speed unit M2, the driving mechanism 90 of outlet side is equipped with in the axial prespecified range W between driving mechanism and variable-speed unit M2 the output gear of being located at outrigger shaft 27 92 around the position of the circumferential space S 2 of outrigger shaft 27 that forms around outrigger shaft 27, being located at output derives axle 91 and is output driven gear 93 that gear 92 drives and the rotation of output gear 92 is passed to the neutral gear clutch 95 that output is derived axle 91 and interrupted this transmission, whole output is derived axle 91 and is disposed in position overlapping with variable-speed unit M2 on the axial view, by neutral gear clutch 95 axially being arranged in the prespecified range W and utilizing the space S 2 that axially is formed at outrigger shaft 27 outsides, being disposed on the axial view output of arranging with the overlapping position of variable-speed unit M2 derives axle 91 and can be disposed in radially position near output shaft 23, and neutral gear clutch 95 can be disposed in radially the position near output shaft 23, and the driving mechanism 90 that is equipped with output and derives on the outlet side of axle 91 and neutral gear clutch 95 can be in the radial direction compactly near output shaft 23.So can be in the radial direction so that speed changer M miniaturization.

Variable-speed unit U comprises the elementary variable-speed unit M1 that is equipped with elementary planetary gears P1 and elementary gear ratio control unit C1 and the secondary variable-speed unit M2 that is equipped with secondary planetary gears P2 and secondary gear ratio control unit C2, the rotation of the pressing member 175 of secondary variable-speed unit M2 is input to output shaft 23, elementary gear ratio control unit C1 is equipped with and stops sun gear 30 along the elementary overrunning clutch 80 of the rotation of a direction, secondary gear ratio control unit C2 is equipped with and stops gear ring 150 along the secondary overrunning clutch 180 of the rotation of a direction, and two overrunning clutchs 80,180 are equipped with the external member T of the rotation adjusting member that the conduct between the secondary engagement part H2 of the elementary anastomosis part H1 that axially is arranged in elementary planetary gears P1 and secondary planetary gears P2 shares.

Because this structure, be equipped with primary and secondary planetary gears P1, P2 and primary and secondary gear ratio control unit C1, the primary and secondary variable-speed unit M1 of C2, among the M2, because primary and secondary overrunning clutch 80,180 are equipped with utilization axially is formed at primary and secondary anastomosis part H1, the external member T that shares that space between the H2 is arranged, compare with the speed changer that all is equipped with the primary and secondary overrunning clutch of external member independently and axially is arranged in the outside of primary and secondary planetary gears, variable-speed unit M1 among the speed changer M, M2 can be compacter in the axial direction, and the neutral gear clutch 95 that therefore is arranged in the prespecified range W according to the length of the outrigger shaft 27 that extends from variable-speed unit M2 in the axial direction can be compacter.

The below will describe a kind of revised configuration of this mode of execution in the situation that the partial configuration in the above-mentioned mode of execution is modified.

Speed changer M is equipped with two variable-speed unit M1, M2 in the above-described embodiment, still, also can be equipped with a plurality of similar variable-speed unit M1, M2 except two, and in this case, the present invention is applicable to the situation of at least two variable-speed unit M1, M2.

The main shaft of speed changer also can be provided with the central axial line coaxial or parallel with the rotation centerline of input shaft or output shaft, also can be the back shaft that supports variable-speed unit, and this back shaft also can be non-rotatable axle.

In elementary planetary gears, the first primary element gear also can be sun gear, and the second primary element gear also can be gear ring.In secondary planetary gears, the first secondary element gear also can be gear ring, and second subprime element gear also can be sun gear.

Driving each pressing member 75,175 driving component also can comprise and replace centrifugal weight 76,176 the pressure-type actuator that utilizes oil pressure etc. or electromagnetic actuators.

Be used for to engage and cut-off clutch 70,170 power also can be that promotion centrifugal weight 76,176 makes centrifugal weight 76,176 be positioned at the spring force of its stop position.

Adjusting member 60 also can only be made of a member.

The clutch jointing state detection unit 13b that is located at controller 13 also can detect the temperature of lubricated clutch 70,170 lubricant oil.For example, when in two clutches 70,170 at least one slided along with lubricating oil temperature raises, when the temperature of lubricant oil is higher than predetermined temperature or the speed that raises when lubricating oil temperature during greater than predetermined value, clutch jointing state detection unit 13b detects each clutch 70,170 half jointing state based on the lubricating oil temperature that is detected by the temperature transducer of being located at controller 13.In this case, can for detection of each clutch 70,170 half jointing state, can reduce cost by the quantity that reduces parts because detect the temperature transducer of lubricating oil temperature.

Internal-combustion engine E also can be the multi-cylinder engine that is equipped with a plurality of cylinders.

Prime mover also can be motor.

Main shown in Fig. 5 (d), when input speed Ni surpassed the 3rd desired speed N3, planetary gears P2 was in and state identical when variable-speed unit M2 is in three class gear shift than R3 with clutch 170.

Simultaneously, in speed changer M1, the first and second intermediate transfer members 37,38 are pushed away to the right and pressing member 75 is pushed away to the right by the power of spring 39a under the state of (namely towards the direction of connect removing) at pressure F2c, along with the rise of rotational speed according to the gear carrier 40 in the clutch 70 of input speed Ni, pressure F1c surpasses the power of spring 39a, and centrifugal weight 76 expands.Centrifugal weight 76 is positioned at maximum and expands the position, and pressing member 75 is so that gear ring 50 is moved to the left and promotes clutch plate 73,74 contacts with each other, and clutch 70 enters complete jointing state.Therefore, gear ratio r1 becomes " 1 ", and namely variable-speed unit M1 is driven directly.

Because two gear ratio r1, the r2 of two variable-speed unit M1, M2 all become " 1 ", speed changer M is driven directly, thus the four-speed gear shift that reaches lowest transmission ratio than R4, and output shaft 23 is rotated with input speed Ni.

The effect of above-mentioned mode of execution then will be described.

In speed changer M, output shaft 23 is equipped with the axially extended outrigger shaft 27 from secondary variable-speed unit M2, the driving mechanism 90 of outlet side is equipped with in the axial prespecified range W between driving mechanism and variable-speed unit M2 the output gear of being located at outrigger shaft 27 92 around the position of the circumferential space S 2 of outrigger shaft 27 that forms around outrigger shaft 27, being located at output derives axle 91 and is output driven gear 93 that gear 92 drives and the rotation of output gear 92 is passed to the neutral gear clutch 95 that output is derived axle 91 and interrupted this transmission, whole output is derived axle 91 and is disposed in position overlapping with variable-speed unit M2 on the axial view, by neutral gear clutch 95 axially being arranged in the prespecified range W and utilizing the space S 2 that axially is formed at outrigger shaft 27 outsides, being disposed on the axial view output of arranging with the overlapping position of variable-speed unit M2 derives axle 91 and can be disposed in radially position near output shaft 23, and neutral gear clutch 95 can be disposed in radially the position near output shaft 23, and the driving mechanism 90 that is equipped with output and derives on the outlet side of axle 91 and neutral gear clutch 95 can be in the radial direction compactly near output shaft 23.So can be in the radial direction so that speed changer M miniaturization.

Variable-speed unit U comprises the elementary variable-speed unit M1 that is equipped with elementary planetary gears P1 and elementary gear ratio control unit C 1 and the secondary variable-speed unit M2 that is equipped with secondary planetary gears P2 and secondary gear ratio control unit C2, the rotation of the pressing member 175 of secondary variable-speed unit M2 is input to output shaft 23, elementary gear ratio control unit C 1 is equipped with and stops sun gear 30 along the elementary overrunning clutch 80 of the rotation of a direction, secondary gear ratio control unit C2 is equipped with and stops gear ring 150 along the secondary overrunning clutch 180 of the rotation of a direction, and two overrunning clutchs 80,180 are equipped with the external member T of the rotation adjusting member that the conduct between the secondary engagement part H2 of the elementary anastomosis part H1 that axially is arranged in elementary planetary gears P1 and secondary planetary gears P2 shares.

Because this structure, be equipped with primary and secondary planetary gears P1, P2 and primary and secondary gear ratio control unit C1, the primary and secondary variable-speed unit M1 of C2, among the M2, because primary and secondary overrunning clutch 80,180 are equipped with utilization axially is formed at primary and secondary anastomosis part H1, the external member T that shares that space between the H2 is arranged, compare with the speed changer that all is equipped with the primary and secondary overrunning clutch of external member independently and axially is arranged in the outside of primary and secondary planetary gears, variable-speed unit M1 among the speed changer M, M2 can be compacter in the axial direction, and the neutral gear clutch 95 that therefore is arranged in the prespecified range W according to the length of the outrigger shaft 27 that extends from variable-speed unit M2 in the axial direction can be compacter.

In speed changer M, by providing overrunning clutch 80,180 and the overrunning clutch 25 that the rotation of output shaft 23 is passed to during above input speed Ni input shaft 20 as output speed No only is provided for gear ratio control unit C1, C2 on the rotation bang path between input shaft 20 and the output shaft 23, the rotation of output shaft 23 is walked around planetary gears P1, P2 by overrunning clutch 25 and is passed to input shaft 20 in the speed reduction of motorcycle process, and wherein the rotation of trailing wheel 98 is passed through output shaft 23 so that input shaft 20 rotations.Therefore, also can carry out work in four-speed gear shift that speed changer M is driven directly than the engine brake in the situation of R3 of the gear ratio R1 outside the R4, engine brake can (or at gear ratio R1 to R4) work under all rotating speeds thus.

Because input shaft 20 and planetary gears P1, P2 are rotatably supported by output shaft 23 on output shaft 23 radial outside ground, the end 21a of input shaft 20 is provided with the enlarged-diameter part with axially open, overrunning clutch 25 is set on the end 21a of input shaft 20 by the radially inner side that overrunning clutch 25 is arranged in the enlarged-diameter part, in addition, overrunning clutch is connected or separates at the axially open with the enlarged-diameter part, therefore can easily dismantle overrunning clutch 25.

As above describe the present invention, be clear that very much and can carry out modification to the present invention in many ways.Will be understood that these modification do not break away from the spirit and scope of the present invention, and those skilled in the art will be very clear, the scope of claims is intended to comprise all these modification.

Claims (6)

1. automatic transmission for vehicles comprises:

Input shaft, it is rotated by prime mover;

Variable-speed unit, it is equipped with planetary gears and gear ratio control unit, described planetary gears has three element gears that are made of the gear carrier of sun gear, support planetary gears and gear ring, and described gear ratio control unit is used for by described planetary gears control gear ratio; And

Output shaft, its output speed rotation so that the input speed of described input shaft is obtained after by described variable-speed unit speed change, and the driving wheel of described output shaft rotation vehicle;

Wherein, described gear ratio control unit is equipped with the overrunning clutch for speed change, and described overrunning clutch is used for stoping the specific element gear of described three element gears to a direction rotation; And

Be equipped with the transmission control member between described input shaft and described output shaft, described transmission control member only is passed to described input shaft with the rotation of described output shaft when described output speed surpasses described input speed.

2. automatic transmission for vehicles as claimed in claim 1, wherein,

The described input shaft and the described planetary gears that are positioned at diametrically the described output shaft outside are rotatably supported by described output shaft;

The end of described input shaft is provided with the enlarged-diameter part of axially open; And

Described transmission control member is for being arranged on diametrically the transmission overrunning clutch in the described enlarged-diameter part.

3. automatic transmission for vehicles as claimed in claim 1, wherein, described variable-speed unit comprises two variable-speed units that begin series winding layout during will rotating the path that is passed to described output shaft from described input shaft from described input shaft side, and described two variable-speed units are rotatably supported by the described output shaft of described speed changer.

4. automatic transmission for vehicles as claimed in claim 1, wherein, described sun gear and described gear carrier are disposed in the both sides of thrust bearing in the axial direction, and are disposed in diametrically the outside of interior axle, and described sun gear and described gear carrier are rotatably installed by bearing by described interior axle.

5. automatic transmission for vehicles as claimed in claim 1, wherein, described overrunning clutch comprises that the back shaft of being equipped by annular element can unsteadily support and be positioned at one or more counterparts of rotation side, the two pairs of ratchets, regulate the rotary component of side and be used for stoping described sun gear to the external member of a direction rotation as rotation.

6. automatic transmission for vehicles as claimed in claim 5, wherein, each ratchet includes component and the weight element that matches with each claw, wherein each ratchet can swing owing to centrifugal force, until described component is in not contact position, do not match with the component of described claw thereby state the thrust that component do not overcome spring in described not contact position place.

Images