CN101839313A - The automatic transmission that possesses planetary gears - Google Patents

Abstract

The invention provides a kind of automatic transmission, in automatic transmission, can seek cost cutting based on the reduction of number of spare parts with a plurality of variable-speed units that contain planetary gears, and, can seek reduction effect to the noise that produces based on the engagement sound.In speed changer (M), the engaging piece (H1, H2) of planetary gears (P1, P2) is housed in the gear chamber (19), and this gear chamber (19) is by the push part (75,175) of the clutch that is separated from each other in the axial direction (70,170) and be formed in the outside axial region (45b, 146) of two planetary carriers (40,140) of the perisporium that extends in the axial direction between two push part (75,175) and the outside body component (T) of overrunning clutch (80,180) forms.The gear sidewall (133) of the gear sidewall (54) of push part (75) and ring gear (50) and push part (175) and central gear (130) constitutes dual-layer wall respectively from end on observation in the radial extension that comprises two engaging pieces (H1, H2).

Description

The automatic transmission that possesses planetary gears

Technical field

The present invention relates to possess the automatic transmission of planetary gears, this automatic transmission for example is loaded on the vehicle.

Background technique

Known a kind of like this automatic transmission, this automatic transmission has a plurality of variable-speed units, and each variable-speed unit has planetary gears and controls the gear ratio control unit of gear ratio according to the rotational speed of input shaft.(for example, with reference to patent documentation 1～3)

Patent documentation 1: No. 5514043 specification of U. S. Patent

Patent documentation 2: TOHKEMY 2001-165250 communique

Patent documentation 3: TOHKEMY 2000-283251 communique

In having the automatic transmission of a plurality of planetary gears,, can become big owing to result from the noise that the engagement sound of this engagement produces automatic transmission because a plurality of gears often mesh in the planetary gears of each variable-speed unit.Therefore, in order to reduce noise, the engaging piece of planetary gears is accommodated under the situation of locular wall of gear chamber being provided with formation, because each planetary gears all is formed with gear chamber, (this component parts comprises the parts beyond planetary gears and gear ratio control unit and these mechanisms to the component parts of variable-speed unit.) to be configured in all be identical in each variable-speed unit, thereby based on the reduction of the part number of the sharing of the parts in a plurality of variable-speed units difficulty relatively, aspect the cost cutting of the reduction of number of spare parts, have room for improvement.

Summary of the invention

Given this present invention plants situation and makes, its purpose is to provide a kind of automatic transmission, in automatic transmission with a plurality of variable-speed units that contain planetary gears, can seek cost cutting, and can improve reduction effect based on the noise that meshes sound based on the reduction of number of spare parts.

Technological scheme of the present invention 1 is described to be a kind of automatic transmission, has: the input shaft (20) that is driven by prime mover (E) rotation; A variable-speed unit (M1), this variable-speed unit has: a planetary gears (P1), it has three key element gears, i.e. the planetary carrier (40) of central gear (30), planetary gear bearing (41) and ring gear (50); A gear ratio control unit (C1), its gear ratio (r1) to a described planetary gears (P1) of rotation that described input shaft (20) is arranged based on input is controlled; Secondary variable-speed unit (M2), this secondary variable-speed unit has: secondary planetary gears (P2), it has three secondary key element gears, i.e. the planetary carrier (140) of central gear (30), planetary gear bearing (141) and ring gear (150); Secondary gear ratio control unit (C2), its secondary gear ratio (r2) to the described secondary planetary gears (P2) of the rotation of once output solid of rotation (44b) that a described variable-speed unit (M1) is arranged based on input is controlled; Output shaft (23) is imported the rotation of the secondary output solid of rotation (175) of described secondary variable-speed unit (M2) to this output shaft; Gearbox case (16), this gearbox case is accommodated a described variable-speed unit (M1) and described secondary variable-speed unit (M2), it is characterized in that, an engaging piece (H1) of a described planetary gears (P1) and the secondary engaging piece (H2) of described secondary planetary gears (P2) are housed in the gear chamber (19), this gear chamber (19) is by the first side wall that is separated from each other in the axial direction (75) and second sidewall (175) and the perisporium (45b that extends in the axial direction between described the first side wall (75) and described second sidewall (175), 146, T) be formed in the described gearbox case (16), the described secondary sidewall (175) that sidewall (75) that described the first side wall (75) and described second sidewall (175) are had by a described gear ratio control unit (C1) respectively and secondary gear ratio control unit (C2) are had constitutes, the first key element gears (50) in described three key element gears have a gear sidewall (54) that is presented axially between a described sidewall (75) and the described engaging piece (H1), the first secondary key element gear (130) in described three secondary key element gears has the secondary gear sidewall (133) that is presented axially between described secondary sidewall (175) and the described secondary engaging piece (H2), a described sidewall (75) and a described gear sidewall (54) and described secondary sidewall (175) and described secondary gear sidewall (133) constitute dual-layer wall at the radial extension that comprises a described engaging piece (H1) and described secondary engaging piece (H2) respectively from end on observation.

The invention of technological scheme 2 is in technological scheme 1 described automatic transmission, and described perisporium (45b, 146, T) is by constituting with the bottom: the gear perisporium (45b) that the three the key element gear (40) in described three key element gears had, the secondary gear perisporium (146) that the 3rd secondary key element gear (140) in described three secondary key element gears is had; The shared periphery wall (T) that a described gear ratio control unit (C1) and described secondary gear ratio control unit (C2) are had.

The invention of technological scheme 3 is in technological scheme 2 described automatic transmission, a described gear ratio control unit (C1) has once rotation restriction overrunning clutch (80), this once rotates restriction and stops the second key element gears (30) in described three key element gears to the rotation of a direction with overrunning clutch, described secondary gear ratio control unit (C2) has secondary rotation restriction overrunning clutch (180), this secondary rotation restriction stops the second secondary key element gear (150) in described three secondary key element gears to the rotation of a direction with overrunning clutch, described periphery wall (T) be for described once rotation restriction with overrunning clutch (80) and described secondary rotation restriction with the shared outside body component (T) of overrunning clutch (180).

The invention of technological scheme 4 is in each described automatic transmission of technological scheme 1～3, a described gear ratio control unit (C1) has speed change clutch (70) one time, this speed change with clutch (70) have allow to connect from a plurality of clutch plate (73,74) according to the rotational speed (Ni) of described input shaft (20) connect from a push part (75), described secondary gear ratio control unit (C2) has secondary speed change clutch (170), this secondary speed change with clutch (170) have allow to connect from a plurality of clutch plate (173,174) according to the described rotational speed (Na) of once exporting solid of rotation (44b) connect from secondary push part (175), a described sidewall (75) and described secondary sidewall (175) are made of a described push part (75) and described secondary push part (175) respectively.

The invention of technological scheme 5 is in technological scheme 4 described automatic transmission, and described secondary output solid of rotation (175) is a described secondary push part (175).

(effect of invention)

According to technological scheme 1 of the present invention, have once, the secondary planetary gears and once, the secondary gear ratio control unit once, the secondary variable-speed unit is housed in the shared gear chamber, therefore, can realize once, the sharing of the component parts of secondary variable-speed unit, the cost cutting of cutting down based on number of spare parts becomes possibility.And because the sharing of component parts, the compactness of the configuration of component parts becomes possibility, and the miniaturization of automatic transmission becomes possibility.

In addition, be housed in the gear chamber that is formed in the gearbox case once, the secondary planetary gears once, the secondary engaging piece, covered by perisporium from radial outside, both sides on axially are to once, the component parts of secondary variable-speed unit utilizes, thus, by dual-layer wall that forms by sidewall and gear sidewall and the dual-layer wall covering that forms by secondary sidewall and secondary gear sidewall, therefore, the noise that not only has based on perisporium reduces effect, and, because the double-wall structure of the sidewall axially, can improve resulting from the reduction effect of noise of engagement of secondary engaging piece.

According to technological scheme 2 of the present invention, the perisporium of the gear chamber that utilize once, the component parts of secondary variable-speed unit forms, except utilized first and second planetary gears once, secondary key element gear once, the secondary gear perisporium, also by once, the shared component parts of secondary gear ratio control unit is that periphery wall constitutes, therefore, because once, the sharing of the component parts of secondary variable-speed unit, can make the designs simplification of the perisporium of formative gear chamber, help the compactness of the configuration of component parts.

According to technological scheme 3 of the present invention, the part of perisporium be periphery wall by once, the secondary gear ratio control unit once, the secondary overrunning clutch shared outside body component constitute, therefore, because once, the secondary variable-speed unit once, the sharing of the component parts of secondary overrunning clutch, can make once, the configuration compactness of secondary overrunning clutch.

According to technological scheme 4 of the present invention, can utilize once, the secondary variable-speed unit once, the secondary clutch once, the secondary push part constitutes the wall in the double walled outside of gear chamber, therefore, needn't make in order to reduce noise once, the secondary planetary gears once, secondary key element gear maximizes diametrically, can reduce result from once, the noise of the engagement of secondary engaging piece.

According to technological scheme 5 of the present invention, the secondary push part performance that the secondary speed change is controlled with the coupled condition of clutch to result from once, the reduction effect of the noise of the engagement of secondary engaging piece and to the effect of output shaft transmission rotation, therefore, can cut down number of spare parts.

Description of drawings

Fig. 1 is the sectional view of the power plant with automatic transmission and internal-combustion engine that are suitable for of the present invention, has schematically represented the part of internal-combustion engine.

Fig. 2 is the enlarged view of the automatic transmission of Fig. 1, with overrunning clutch, is the II-II line sectional view of Fig. 4 for the rotation restriction.

Fig. 3 is the major component enlarged view of Fig. 2.

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

Fig. 5 is the schematic representation that the action to the automatic transmission of Fig. 1 describes, Fig. 5 (a) is the figure when establishing 1 fast gear ratio, Fig. 5 (b) is the figure when establishing 2 fast gear ratio, and Fig. 5 (c) is the figure when establishing 3 fast gear ratio, and Fig. 5 (d) is the figure when establishing 4 fast gear ratio.

Fig. 6 is the conceptual explanatory drawing of the gear ratio that obtains of the automatic transmission with Fig. 1.(explanation of reference character)

6 ... bent axle, 9 ... Fuelinjection nozzle, 10 ... ignition mechanism, 13 ... control gear, 13b ... clutch coupled condition feeler mechanism, 13c ... time detecting mechanism, 16 ... gearbox case, 20 ... input shaft, 23 ... output shaft, 25 ... overrunning clutch, 27 ... extend axial region, 30,130 ... central gear, 40,140 ... planetary carrier, 41,141 ... planetary pinion, 46 ... thrust is born portion, 50,150 ... ring gear, 60 ... limiting part, 65 ... support unit, 70,170 ... clutch, 75,175 ... push part, 76,176 ... governor weight, 80,180 ... overrunning clutch, 90 ... the outlet side driving mechanism, 91 ... axle, 95 are taken out in output ... the neutral gear clutch, M ... automatic transmission, E ... internal-combustion engine, P1, P2 ... planetary gears, M1, M2 ... variable-speed unit, C1, C2 ... gear ratio control unit, F1a, F1b, F2a, F2b ... axial force, H1, H2 ... engaging piece, F1c, F2c ... pushing force, T ... outside body component.

Embodiment

Below, with reference to Fig. 1～Fig. 6 embodiments of the present invention are described.

With reference to Fig. 1, the automatic transmission M that the present invention was suitable for is a vehicle automatic transmission, this automatic transmission M and constitute the power plant that are loaded in as on the two-wheeled motor vehicle of vehicle together as the internal-combustion engine E of prime mover.

In addition, in mode of execution, left and right directions and fore-and-aft direction are consistent with the left and right directions and the fore-and-aft direction of the two-wheeled motor vehicle that has loaded above-mentioned power plant respectively, and in addition, above-below direction is a vertical direction.

In addition, in the scope of specification or claims, axially be the direction with the rotating center line parallel of the input shaft of speed changer or output shaft, radially and circumferentially be respectively to be radially reaching circumferentially of center with this rotation centerline.And, with a side of right-hand and left during as axial direction, with the opposing party of right-hand and left as another axial direction.

In addition, the gear ratio of speed changer is a reduction speed ratio.

Air-cooling type list cylinder quartastroke engine is that internal-combustion engine E has body of the internal-combustion engine, and this body of the internal-combustion engine comprises: cylinder block 1, this cylinder block 1 have for piston 4 with can the chimeric cylinder 1a of reciprocating mode; Be combined in the cylinder head 2 of the upper end portion of cylinder block 1; Be combined in the crankcase 3 of the underpart of cylinder block 1.

Be provided with in the cylinder head 2: firing chamber 7; Suction port (not shown), this suction port will and be directed into firing chamber 7 from the formed mixed gas of the fuel of Fuelinjection nozzle 9 from the combustion air that is connected the air inlet system 8 on the cylinder head 2; Relief opening (not shown), the exhaust gas of this relief opening spontaneous combustion in the future chamber 7 is directed into the venting gas appliance that is connected on the cylinder head 2; Spark plug 10a in the face of firing chamber 7; The valve device 11 that suction valve and outlet valve (all not shown), this suction valve and outlet valve are had camshaft 11a drives, and above-mentioned suction port and above-mentioned relief opening are opened and closed respectively.

Piston 4 is driven by the pressure of the combustion gas that produce because of the combustion of mixed gas in the firing chamber 7, moves back and forth, and rotation drives bent axle 6 via connecting rod 5.Camshaft 11a is driven in rotation by the power of bent axle 6, and the power of described bent axle 6 transmits via the timing driving mechanism 12 with chain 12a.

(in this specification, this rotation can rename as power or moment of torsion in the rotation of the bent axle 6 that internal-combustion engine E is had.) input to speed changer M.And, take out axle 91 power that are removed from the output of speed changer M, via constituting the chain 97b that drives with driving mechanism 97, be that trailing wheel 98 drives to driving wheel as driven object.

The throttle valve 8a that air inlet system 8 is had is that air inflow is controlled to the flow of the combustion air that is inhaled into firing chamber 7; As the Fuelinjection nozzle 9 of mixed gas formation mechanism, the delivery volume that is ejected into the fuel in the combustion air is controlled for the air fuel ratio of controlling mixed gas; 10 control ignition opportunitys of ignition mechanism with spark plug 10a.

Throttle valve 8a, Fuelinjection nozzle 9 and ignition mechanism 10 are controlled by the control gear 13 that internal-combustion engine E is had respectively, it is the output control mechanism that to control the output of internal-combustion engine E according to the working state of the operating condition of internal-combustion engine E and speed changer M, and, still control the rotational speed of bent axle 6 and then rotational speed control mechanism that the rotational speed Ni (with reference to Fig. 6) of the input shaft 20 of speed changer M is controlled by the output of internal-combustion engine E.

The state detection mechanism that the working state to the operating condition of internal-combustion engine E and speed changer M that has control gear 13 detects and for control device 13a from the testing signal input of this state detection mechanism.Above-mentioned state detection mechanism is except the operating condition feeler mechanism that comprises the internal-combustion engine rotational speed that detects internal-combustion engine E and engine load, also comprise: the clutch coupled condition 13b of feeler mechanism, its speed change to speed changer M detects with the situation that clutch 70,170 is in semi-connection state; The 13c of time detecting mechanism, it is to detecting by the endurance of the detected semi-connection state of the clutch coupled condition 13b of feeler mechanism.

The clutch coupled condition 13b of feeler mechanism is by comparing and detect above-mentioned half connection state setting gear ratio and actual gear ratio, wherein, set gear ratio and be according to the input rotational speed Ni of the input shaft 20 of speed changer M and predefined, actual gear ratio is to calculate according to the rotational speed No of the reality of the output shaft 23 of speed changer M and actual input rotational speed Ni, and the rotational speed No of above-mentioned reality and actual input rotational speed Ni are detected by rotational speed feeler mechanism.For example, when at least one side in two clutches 70,170 is skidded, because above-mentioned actual gear ratio becomes littler than above-mentioned setting gear ratio, therefore, the 13b of clutch coupled condition feeler mechanism detects above-mentioned semi-connection state when making above-mentioned actual gear ratio less than the judgement of above-mentioned setting gear ratio.

When exceeding schedule time by the detected endurance of the 13c of time detecting mechanism, control device 13a is in order to control at least one the output controlled quentity controlled variable in air inflow, fuel feed and igniting opportunity, and at least one action of throttle valve 8a, Fuelinjection nozzle 9 and ignition mechanism 10 is controlled.By this control, input rotational speed Ni is changed in the mode that increases or reduce, and carrying out the transition to each clutch 70,170 becomes the rotational speed that connects finishing stage.

Crankcase 3 constitutes and comprises: a pair of case halfbody 3a, the 3b that mutually combine and can cut apart on overall width direction (left and right directions also can) by a plurality of bolts; Be combined in a pair of cover 3c of portion, 3d on each case halfbody 3a, 3b respectively by a plurality of bolts.Bent axle 6 is bearing on a pair of case halfbody 3a, the 3b in the mode that can rotate via a pair of main bearing 14a, 14b.

Crankcase 3 forms the containing room 15 of accommodating bent axle 6 and speed changer M.By being located at the gearbox case 16 as partition wall in this containing room 15, containing room 15 is separated into: as the 15a of crankshaft room of drive chamber, dispose the bent axle 6 as the rotary driving axle among the 15a of this crankshaft room; Gearbox chamber 15b disposes speed changer M among the 15b of this gearbox chamber.In this embodiment, gearbox case 16 is so that the mode that 15a of crankshaft room and gearbox chamber 15b are communicated with on the top of containing room 15, with containing room 15 partial divisions, the diapire of gearbox chamber 15b is made of a pair of case halfbody 3a, 3b and the 3d of cover portion in the bottom of containing room 15.In addition, as other example, gearbox case 16 also can be so that 15a of crankshaft room and gearbox chamber 15b become the mode in separate space that containing room 15 is separated.

At the perforation main bearing 14a of bent axle 6 and be provided with centrifugal clutch 17 on the shaft end 6a of right-hand extension, this centrifugal clutch 17 is that the rotational speed according to bent axle 6 is that the internal-combustion engine rotational speed is carried out the start clutch of transmission from the rotation of bent axle 6 to speed changer M and blocking-up.Centrifugal clutch 17 has governor weight 17a, the coupled condition of the variation servo-actuated ground control centrifugal clutch 17 of this governor weight 17a and internal-combustion engine rotational speed.

Described power plant have the reducing gear 18 as the input side driving mechanism, and this reducing gear 18 is the input shaft 20 that is passed to the rotation of bent axle 6 speed changer M via being in the centrifugal clutch 17 that connects finishing stage.Reducing gear 18 constitutes by the actuation gear 18a of the rotation of transmitting centrifugal clutch 17 with the driven gear 18b of input shaft 20 one rotation, via the input side clutch is centrifugal clutch 17 with the rotation input speed changer M of the bent axle 6 that passes over, and the transmission and the blocking-up of the rotation of described centrifugal clutch 17 subtend input shafts 20 are controlled.

With reference to Fig. 1, Fig. 2, speed changer M has: the input shaft 20 that is driven in rotation via the bent axle 6 of driven gear 18b by internal-combustion engine E; Variable-speed unit U with planetary gears P1, P2; Output shaft 23, this output shaft 23 is rotated with output rotational speed No, and output rotational speed No has carried out speed change by variable-speed unit U to input rotational speed Ni and has obtained; Outlet side driving mechanism 90, it has the output that is driven in rotation by output shaft 23 and takes out axle 91; Gearbox case 16, it is accommodated input shaft 20, variable-speed unit U and accommodates output shaft 23.

Here, with variable-speed unit U in rotary components such as planetary gears P1, P2, input shaft 20, output shaft 23 and the contrast of the output rotary component that takes out axle 91 iso-variable velocity device M in, gearbox case 16 and crankcase 3 are the parts that are not included in these rotary components, for example are that non-rotary parts are the fixed side parts.

Input shaft 20 is bearing on the gearbox case 16 in the mode that can rotate, and is bearing on the case halfbody 3b in the mode that can rotate via output shaft 23.Input shaft 20 has: first input shaft 21, and its outside that is configured in gearbox chamber 15b (or gearbox case 16) in the axial direction is on the 15a of crankshaft room, and by the integrally formed driven gear 18b that is provided with; Second input shaft 22, it has limited axial moving with respect to output shaft 23 by thrust-bearing B 1.Second input shaft 22 is bearing on the periphery of output shaft 23 in the mode that can rotate within it in week, is bearing on the shell 16 in the mode that can rotate via bearing B2 in its periphery.

First input shaft 21 is by on the chimeric periphery that is attached at second input shaft 22 of spline, and coaxial with this second input shaft 22, and this first input shaft 21 has the shaft end 21a that forms opening port 21b, and this opening port 21b is in the axial direction to the 15a of crankshaft room opening.This shaft end 21a is than the big wide diameter portion of second input shaft, 22 diameters in input shaft 20.

A shaft end 23b of output shaft 23 is bearing on the case halfbody 3b in the mode that can rotate via bearing B3, and near the part another shaft end 23a is bearing on the gearbox case 16 in the mode that can rotate via the bearing B4 and second input shaft 22.With input shaft 20 arranged coaxial and have the output shaft 23 of the rotation centerline L2 consistent, connect variable-speed unit U, input shaft 20 and shell 16 in the axial direction and extend in the 15a of crankshaft room with the rotation centerline L1 of this input shaft 20.The rotating center line parallel of each rotation centerline L1, L2 and bent axle 6.

Speed changer M has the transmission overrunning clutch 25 as the transmission control part part that is configured between input shaft 20 and the output shaft 23.Output shaft 23 is attached on the shaft end 21a of input shaft 20 via overrunning clutch 25 at its shaft end 23a.Overrunning clutch 25 has: as lateral body 25a in the clutch of input block, it is located on the shaft end 23a, rotates integratedly with output shaft 23; As the outer lateral body 25b of the clutch of output block, it is located on the shaft end 21a, itself is made of shaft end 21a in the present embodiment; A plurality of clutch element 25c (for example, pillar or roller), it disposes on the devices spaced apart ground that makes progress in week between lateral body 25b outside lateral body 25a and the clutch in clutch diametrically.In addition, in other example, the outer lateral body 25b of clutch can also be made of the miscellaneous part different with shaft end 21a and be located on this shaft end 21a, and lateral body 25a also can itself be made of shaft end 23a in the clutch.

When the rotational speed No of output shaft 23 surpasses input rotational speed Ni, in clutch element 25c and the clutch lateral body 25a and clutch outward lateral body 25b become fastening state, the rotation of output shaft 23 is passed to input shaft 20; Be input rotational speed Ni when following at output rotational speed No, the outer lateral body 25b of lateral body 25a and clutch becomes non-fastening state in clutch element 25c and the clutch, the rotation of input shaft 20 via overrunning clutch 25 to output shaft 23 transmission.

Therefore, as overrunning clutch 25, when two-wheeled motor vehicle slows down, under the situation of having established the gear ratio R1～R3 (with reference to Fig. 6) of speed changer M beyond the minimum gear ratio under the direct connecting state described later is 4 fast gear ratio R4, power by the trailing wheel that only do not transmit via output shaft 23 via variable-speed unit U drives internal-combustion engine E, this overrunning clutch 25 becomes described fastening state in the mode of performance engine braking effect, when by internal-combustion engine E trailing wheel being driven, this overrunning clutch 25 becomes described non-fastening state.

Variable-speed unit U is made of the variable-speed unit M1 and the secondary variable-speed unit M2 that are two the bang path of 23 the rotation from input shaft 20 to output shaft from a plurality of, the present embodiment of input shaft 20 side arranged in series.Two variable-speed unit M1, M2 are bearing on the main shaft and the output shaft 23 as supporting axle as speed changer M in the mode that can rotate, and this two variable-speed unit M1, M2 are in the axial direction from (or shaft end 23a of output shaft 23 near) near the reducing gear 18 with the order arrangement of variable-speed unit M1 and variable-speed unit M2 in the axial direction.

With reference to Fig. 2, Fig. 3, each variable-speed unit M1, M2 have: planetary gears P1, P2, it has three key element gears, promptly central gear 30,130, support the planetary carrier 40,140 and the ring gear 50,150 of a plurality of planetary pinions 41,141 in the mode that can rotate; Gear ratio control unit C1, C2, it is controlled the gear ratio R (with reference to Fig. 6) based on planetary gears P1, P2.

Central gear 30,130, planetary pinion 41,141 and ring gear 50,150 constitute by helical gear.As its rotation centerline, central gear 30,130, planetary carrier 40,140 and ring gear 50,150 total rotation centerline L1, L2.

The ring gear 50 of the planetary gears P1 of variable-speed unit M1 has: the inboard axial region 51 of tubulose, and it is attached on second input shaft 22 by spline is chimeric; Edge part 52, its conduct is positioned at the outside axial region of the tubulose of radial outside with respect to this inboard axial region 51, and is provided with the tooth portion 53 of meshing with the tooth portion 42 of each planetary pinion 41 on interior week; As a gear sidewall 54 of discoid annular wall, it extends diametrically, links to each other with inboard axial region 51 and links to each other with edge part 52 in outer periphery at inner circumference edge.In planetary gears P1, ring gear 50 is once input gears that the rotation of input shaft 20 is imported, and this ring gear 50 is the first key element gears in three key element gears among the planetary gears P1.

The planetary carrier 40 of planetary gears P1 is made of first, second planetary carrier 44,45 that mutually combines by supporting axle 43, and described supporting axle 43 supports each planetary pinion 41 in the mode that can rotate.First planetary carrier 44 has: as the annulus 44a of annular wall, it supports supporting axle 43; The inboard axial region 44b of tubulose, its inner circumference edge with annulus 44a link to each other and are bearing on the output shaft 23 in the mode that can rotate via the central gear 130 of inboard axial region 51 and secondary planetary gears P2.Second planetary carrier 45 has: as the annulus 45a of annular wall, it supports supporting axle 43; The outside axial region 45b of tubulose, its outer periphery with annulus 45a link to each other.Planetary carrier 40 be will carry out speed change by planetary gears P1 the rotation of input shaft 20 to the output gear that planetary gears P2 exports, be the three key element gear in three key element gears among the planetary gears P1.

The inboard axial region 44b of planetary carrier 40 is the once output solid of rotation that the rotation of input shaft 20 inputed to planetary gears P2 via variable-speed unit M1.Outside axial region 45b has fixed wall 45c in the axial direction on a near end the planetary gears P1, this fixed wall 45c is chimeric and be attached on the outer lateral body 72 of clutch in the mode of one rotation by spline as linking department; Outside axial region 45b has the 45d of the portion of being supported on another end, this is supported that the 45d of portion is provided with in the axial direction across first limiting part 61 and a pair of thrust-bearing B5 of configuration.Therefore, by first limiting part 61, planetary carrier 40 with respect to output shaft 23 and gearbox case 16 axially on mobile being prevented from.

Central gear 30 has as the second key element gears in three key element gears among the planetary gears P1: the axial region 31 of tubulose, and it is provided with tooth portion 32 with tooth portion 42 engagements of each planetary pinion 41 in periphery; Annular wall is an annulus 33, and it extends to radial outside from axial region 31, as supplying ratchet pawl 81,82 described later; 181,182 supports that are provided with.Be bearing in axial region 31 on the periphery of inboard axial region 44b of planetary carrier 40 in the mode that can rotate and have once pushing portion 34 as the end, this once pushing portion 34 be presented axially near the planetary gears P2 with respect to being fixed on annulus 33 on the axial region 31.Portion 46 is born to axial push via thrust-bearing B6 with thrust by pushing portion 34, and this thrust is born portion 46 and is arranged on the periphery of inboard axial region 44b in the mode with inboard axial region 44b one rotation.Therefore, bear by thrust that portion 46 stops central gears 30 because the first axial force F 1b left that produce based on engagement and moving with respect near planetary carrier 40 planetary gears P2 (or left side) with planetary pinion 41.

These tooth portions 32,42,53 of planetary gears P1, in planetary gears P1, be that three key element gears are meshing with each other, that is to say that time key element gear is each planetary pinion 41 is meshing with each other with ring gear 50 and inferior one to one in addition key element gear is a planetary carrier 40 each planetary pinion 41 and central gear 30 intermeshing engaging piece H1 of planetary carrier 40 one to one.

On the other hand, the central gear 130 of the planetary gears P2 of secondary variable-speed unit M2 has: the inboard axial region 131 of tubulose, on its inboard axial region 44b by the chimeric planetary carrier 40 that is attached at planetary gears P1 of spline; The outside axial region 132 of tubulose, it is positioned at radial outside with respect to inboard axial region 131; Discoid annular wall is a secondary gear sidewall 133, and it extends diametrically, links to each other with inboard axial region 131 and links to each other with outside axial region 132 in outer periphery at inner circumference edge.Be bearing in the mode that can rotate on the periphery of the inboard axial region 131 on the output shaft 23 via bearing B7, be provided with the 131a of tooth portion with the 142a of tooth portion of each planetary pinion 141 engagement.

Inboard axial region 131 has: elastic pressing part 134, and its radially inner side at the inboard axial region 44b of planetary carrier 40 extends in the axial direction to the inboard axial region 51 of the ring gear 50 of planetary gears P1; Block 135, it is in the axial direction to mobile prevention to the right of central gear 130, inboard axial region 131 on this elastic pressing part 134 by spline chimeric being attached on the inboard axial region 44b.Move to the right at central gear 130, when elastic pressing part 134 suppresses push part 75,175 described later to the right, block 135 in the axial direction with inboard axial region 44b butt, thus, stop central gear 130 moving to the right, the amount of movement of the central gear 130 on is axially stipulated.

Central gear 130 is by inboard axial region 44b its input to be had from the secondary input gear of the rotation of variable-speed unit M1 output in planetary gears P2, is the first secondary key element gear in three secondary key element gears among the planetary gears P2.

On the planetary carrier 140 of planetary gears P2, be provided with the supporting axle 144 that supports each planetary pinion 141 in the mode that can rotate.Planetary carrier 140 has the outside axial region 146 of the tubulose that links to each other with outer periphery with annulus 145 as the annulus 145 of annular wall that supporting axle 144 is supported.Planetary carrier 140 is secondary output gears that the rotation that will carry out the inboard axial region 44b of speed change by planetary gears P2 exports output shaft 23 to, is the 3rd secondary key element gear in three secondary key element gears among the planetary gears P2.

Outside axial region 146 exports output shaft 23 to the rotation speed change of inboard axial region 44b and with it, and this outside axial region 146 is the whole output shafts among speed changer the M whole planetary gears P 1, the P2 that are had.In addition, outside axial region 146 has fixed wall 146c on the end of that side near the planetary gears P2 in the axial direction, this fixed wall 146c is chimeric and be attached on the outer lateral body 172 of clutch in the mode of one rotation by spline as linking department, outside axial region 146 has the 146d of the portion of being supported on the end of opposite side, this is supported that the 146d of portion is provided with in the axial direction across second limiting part 62 and a pair of thrust-bearing B8 of configuration.Therefore, by second limiting part 62, axial mobile being prevented from respect to output shaft 23 and gearbox case 16 of planetary carrier 140.

Ring gear 150 is second secondary key elements in three secondary key element gears among the planetary gears P2, and this ring gear 150 has: the outside axial region 151 of tubulose, and it is at the 151a of tooth portion that is provided with in interior week with the 143a of the tooth portion engagement of each planetary pinion 141; Annular wall as support is an annulus 152, and it extends to radially inner side from outside axial region 151, and this annulus 152 is provided with ratchet pawl 81,82,181,182; As the secondary pushing portion 153 of inboard axial region, it is bearing on the periphery of inboard axial region 44b in the mode that can rotate.Be presented axially near the planetary gears P1 pushing portion 153 with respect to annulus 152, in the axial direction thrust born portion 46 to the direction pushing opposite with pushing portion 34 via thrust-bearing B9.Therefore, bear by thrust that portion 46 stops ring gears 150 because the first secondary axial force F 2b to the right that produces based on engagement and with respect near two planetary carriers 140 the moving of (or right side) planetary gears P1 with planetary pinion 141.

Each planetary pinion 141 is made of first gear 142 and second gear 143, wherein, first gear 142 has first 142a of tooth portion with the 131a of tooth portion of central gear 130 engagement, second gear, 143 to the first gears, 142 diameters are big, and have second 143a of tooth portion with the 151a of tooth portion of ring gear 150 engagement.And, by planetary pinion 141, can obtain than the gear ratio based on planetary gears P1 by planetary gears P2 be the big secondary gear ratio r2 of gear ratio r1, this planetary gears P2 has the roughly the same ring gear 150 of external diameter of the ring gear 50 of external diameter and planetary gears P1, therefore, this structure of this planetary pinion 141 helps the miniaturization of the speed changer M that makes progress of footpath.

In addition, (with respect to axially) angle of inclination of the 142a of first, second tooth portion, 143a is set greatlyyer than (with respect to axially) angle of inclination of the tooth portion 42 of each planetary pinion 41 of planetary gears P1, therefore, the angle of inclination of each 131a of tooth portion, 151a is set greatlyyer than the angle of inclination of each tooth portion 32,53.

Therefore, at the torsional interaction of identical size under the situation on planetary pinion 41 and the planetary pinion 141, and the central gear 130 of secondary planetary pinion 141 engagements and ring gear 150 between the secondary axial force F 2a, the F2b that produce than and the ring gear 50 of planetary pinion 41 engagements and central gear 30 between axial force F 1a, a F1b producing big.

In addition, as other examples, the angle of inclination of the whole tooth portion 32,42,53 among two planetary gears P1, the P2,131a, 142a, 143a, 151a also can be set at respectively and equate.

The 131a of these tooth portions of planetary gears P2,142a, 143a, 151a, in planetary gears P2, be that three secondary key element gears intermesh, that is to say each planetary pinion 141 is meshing with each other with ring gear 150 and other a pair of secondary key element gear is a planetary carrier 140 each planetary pinion 141 and central gear 130 intermeshing secondary engaging piece H2 that a pair of secondary key element gear is a planetary carrier 140.

And from axially observing, two gear sidewalls 54,133 are comprising once, are forming in the whole or roughly whole radial extension of secondary engaging piece H1, H2.

With reference to Fig. 1～Fig. 3, the moving axially of planetary carrier 40,140 of limiting part 60 couples of each planetary gears P1, P2 that speed changer M is had limited.Be configured in the limiting part 60 between engaging piece H1 and the engaging piece H2 in the axial direction, have first limiting part 61 that the position of planetary carrier 40 is limited and second limiting part 62 that the position of planetary carrier 140 is limited. Two limiting parts 61,62 all mutually combine with the support unit 65 that supports overrunning clutch 80,180, and wherein, the central gear 30 of overrunning clutch 80,180 couples two planetary gears P1, P2 and the sense of rotation of ring gear 150 limit.

And each limit material parts 61,62 has: the 61a of tube portion, the 62a of Yan Shening in the axial direction; The forward end of the 61a of tube portion, 62a on axially is to radially first, second support lug 61b, the 62b of first, second support of conduct of extension; The terminal side of in the axial direction the 61a of tube portion, 62a is to cardinal extremity flange 61c, the 62c as the fixing part that radially extend.And, cardinal extremity flange 61c, 62c each other across under the state of support unit 65 and all with state that this support unit 65 combines under, be installed on a plurality of assembly department 16a (with reference to Fig. 1) by bolt, these a plurality of assembly department 16a are provided with on the devices spaced apart ground that makes progress in week on gearbox case 16.

The thrust that speed changer M is had is born portion 46, is configured in the axial direction between the pushing portion 153 of the pushing portion 34 of central gear 30 and planetary carrier 140, and is located on the inboard axial region 44b.This thrust is born portion 46 and is made of circlip, and this circlip is entrenched among the annular slot 44c on the outer circumferential face that is located at inboard axial region 44b.

Therefore, central gear 30 and planetary carrier 140 dispose the both sides that in the axial direction thrust is born portion 46 respectively, and this central gear 30 and planetary carrier 140 are configured in the radial outside of inboard axial region 44b, are bearing on the inboard axial region 44b in the mode that can rotate via bearing B10.And thrust is born portion 46 and is configured in the space that is surrounded by the outside body component T of unidirectional clutch 80,180.In addition, a pair of thrust-bearing B6, B9, be connected to thrust in the axial direction and bear on the both sides of portion 46, this a pair of thrust-bearing B6, B9 respectively by bearing housing B6a, the B9a of a pair of ring-type and be configured in two bearings case B6a radially and two bearings case B9a between a plurality of roller B6b, B9b constitute.

One time gear ratio control unit C1 controls a gear ratio r1 based on a variable-speed unit M1, with reference to Fig. 2, Fig. 3, this gear ratio control unit C1 has: as the speed change clutch 70 of a transmitting control mechanism, it is according to the rotational speed Ni of input shaft 20, to ring gear 50 not via planetary pinion 41 direct transmission and the blocking-up to the rotation of planetary carrier 40 control; As the once rotation restriction overrunning clutch 80 of a rotation restricting unit, it stops the rotation to a direction A1 (with reference to Fig. 4) as the central gear 30 of specific factor gear, but allows the rotation of A2 round about of this central gear 30.

Low speed side clutch i.e. clutch 70 is compared and is imported the less low speed rotation territory of rotational speed Ni and become the connection finishing stage becoming the high speed rotating territory that is connected finishing stage with secondary speed change described later with clutch 170, this clutch 70 is centrifugal friction clutches, have: as lateral body 71 in the clutch of input block, its input is had rotation from input shaft 20, and lateral body 71 is that edge part 52 constitutes by the part of ring gear 50 in this clutch; As the outer lateral body 72 of a clutch of the tubulose of output block, it is configured in the radial outside of lateral body 71 in the clutch, combines in the mode with the rotation of planetary carrier 40 one; Once rotate transmitting control portion, it comprise diametrically with can the phase mutual connection from the mode interaction cascading be configured in the clutch a more than one input side clutch plate 73 and the more than one outlet side clutch plate 74 between the lateral body 72 outside the lateral body 71 and clutch; A push part 75, its with each clutch plate 73,74 to axial push and clutch plate 73,74 is contacted with each other; As a driver part more than one, be a plurality of governor weights 76 at this, this governor weight 76 drives push part 75 moves it in the axial direction.

Clutch 70 is configured in radial outside with respect to planetary gears P1.

Input side clutch plate 73 is provided with as follows: by the spline on the periphery of lateral body in clutch 71 chimeric and with clutch in lateral body 71 one rotation and can moving in the axial direction, outlet side clutch plate 74 is provided with as follows: by the spline on the interior week of lateral body outside clutch 72 chimeric and with clutch outside lateral body 72 one rotate and can move in the axial direction.

Allow to connect from a plurality of clutch plate 73,74 according to input rotational speed Ni connect from push part 75, it is the disc-shaped part that extends diametrically, be configured in the opposition side right side of gear sidewall 54 (or with respect to) with respect to gear sidewall 54 and engaging piece H1 in the axial direction, by as block being the back-up ring 77 of anticreep parts, this push part 75 mobile being restricted to the right.The conduct pushing of 77 pairs of push part 75 of back-up ring is removed the maximum mobile position to the right of position and is set.

Push part 75 be near the linking department with input shaft 20 from ring gear 50 is inboard axial region 51, surpass in the radial extension of edge part 52 lateral body 72 outside clutch, in the axial direction from a sidewall of right side cover ring generating gear 50 and clutch plate 73,74.In addition, push part 75 is bearing in the mode that can rotate via thrust-bearing B11 near the inboard axial region 51 of ring gear 50 the wall portion, and this push part 75 can move with ring gear 50 one in the axial direction.

Secondary gear ratio control unit C2 controls the secondary gear ratio r2 based on secondary variable-speed unit M2, this secondary gear ratio control unit C2 has: as the secondary speed change clutch 170 of secondary transmitting control mechanism, it is according to input rotational speed Ni, more particularly according to the rotational speed that input rotational speed Ni has carried out the inboard axial region 44b that speed change obtains promptly once being exported rotational speed Na by variable-speed unit M1, to central gear 130 not via planetary pinion 140 direct transmission and the blocking-up to the rotation of planetary carrier 140 control; As the secondary rotation restriction overrunning clutch 180 of secondary rotation restricting unit, it stops the rotation to a direction A1 (with reference to Fig. 4) as the planetary carrier 140 of specific factor gear, but allows the rotation of A2 round about of this planetary carrier 140.

The high-speed side clutch is that secondary clutch 170 becomes the connection finishing stage in the high speed rotating territory of input rotational speed Ni, this secondary clutch 170 is centrifugal friction clutches, have: as lateral body 171 in the secondary clutch of input block, its input is had rotation from inboard axial region 44b, and in this secondary clutch lateral body 171 by the part of central gear 130 promptly outside axial region 132 constitute; As the outer lateral body 172 of the secondary clutch of the tubulose of output block, it is configured in the radial outside of lateral body 171 in the clutch, combines in the mode with the rotation of planetary carrier 140 one; Secondary rotation transmitting control portion, it comprise diametrically with can the phase mutual connection from the mode interaction cascading be configured in the clutch more than one secondary input side clutch plate 173 and the more than one secondary outlet side clutch plate 174 between the lateral body 172 outside the lateral body 171 and clutch; Secondary push part 175, its with each clutch plate 173,174 to axial push and clutch plate 173,174 is contacted with each other; As the secondary driver part more than one, be a plurality of secondary centrifuging counterweights 176 at this, this secondary centrifuging counterweight 176 drives push part 175 moves it in the axial direction.

Clutch 170 is configured in radial outside with respect to planetary gears P2.

Input side clutch plate 173 is provided with as follows: by the spline on the periphery of lateral body in clutch 171 chimeric and with clutch in lateral body 171 one rotation and can moving in the axial direction, outlet side clutch plate 174 is provided with as follows: by the spline on the interior week of lateral body outside clutch 172 chimeric and with clutch outside lateral body 172 one rotate and can move in the axial direction.

The clutch plate 73,74,173,174 of two clutches 70,170 is immersed in the lubricant oil that stores in gearbox case 16 in its underpart.

Allow to connect from a plurality of clutch plate 173,174 according to by variable-speed unit M1 to input rotational speed Ni carried out that speed change obtains once export rotational speed Na connect from push part 175, it is the disc-shaped part that extends diametrically, be configured in the opposition side left side of gear sidewall 133 (or with respect to) with respect to gear sidewall 133 and secondary engaging piece H2 in the axial direction, by as block being the back-up ring 177 of anticreep parts, this push part 175 mobile being restricted to the left.The conduct pushing of 177 pairs of push part 175 of back-up ring is removed the maximum mobile position to the left of position and is set.

Secondary output solid of rotation is that push part 175 directly is attached on the output shaft 23, will by once, secondary variable-speed unit M1, the M2 rotation of having carried out speed change inputs to output shaft 23, this push part 175 be from linking department be with output shaft 23 spline 175a begin to surpass in the radial extension of outside axial region 132 lateral body 172 until clutch outside, in the axial direction from the secondary sidewall of left side covering central gear 130 and clutch plate 173,174.In addition, push part 175 is bearing in the mode that can rotate via thrust-bearing B12 near the inboard axial region 131 of central gear 130 the wall portion, and this push part 175 can move with central gear 130 one in the axial direction.

In two clutches 70,170, the outer lateral body 72,172 of clutch has: the end wall of ring-type is abutment wall 72a, 172a, and it is bearing on outside axial region 45b, 146 the periphery in the mode that can move by sliding in the axial direction; Block 72b, 172b when non-expansion is opened, the idle position of its governor weight 76,176 of (when non-expansion is opened) during to inoperative limits; Expand block 72c, 172c when opening, the maximum when it is opened at utmost expanding expands open position and (is represented by double dot dash line among Fig. 2, Fig. 3.) limit.

When according to input rotational speed Ni, more particularly when promptly once exporting rotational speed Na (promptly according to input rotational speed Ni having been carried out the rotational speed that speed change obtains with gear ratio r1, be the outer lateral body 72 of inboard axial region 44b, clutch of planetary carrier 40 or the rotational speed of push part 75, among Fig. 6 illustration one once export rotational speed Na.) and the centrifugal force that produces when increasing, governor weight 76 is in contact with one another a plurality of clutch plate 73,74 via push part 75.In addition, when basis is once exported rotational speed Na, more particularly when according to having carried out rotational speed that speed change obtains and promptly export rotational speed No and (that is, be the rotational speed of outer lateral body 172 of planetary carrier 140, clutch or push part 175 this is once exported rotational speed Na based on the gear ratio r2 of variable-speed unit M2.) and the centrifugal force that produces when increasing, governor weight 176 is in contact with one another a plurality of secondary clutch plate 173,174 via push part 175.

Constitute respectively once, described a plurality of governor weights 76,176 of secondary centrifuging weight set upwards separate uniformly-spaced in week and dispose, and, be bearing on abutment wall 72a, the 172a expanding the mode of opening to radial outside by acting on the centrifugal force on the governor weight 76,176.Each governor weight 76,176 has: can be connected to fulcrum 76a, 176a on the carrier 47,147, described carrier 47,147 is via as the belleville spring 48,148 of intermediate member and be arranged on the edge part 52 of planetary carrier 40,140; Elastic pressing part 76d, 176d, abutment wall 72a, 172a as service portion when it is opened expansion with pushing force F1c, the F2c that produces because of centrifugal force suppress; Non-working side abutting part 76b, 176b, it is connected on block 72b, the 172b when inoperative; Expand and open side abutting part 76c, 176c, it is connected on block 72c, the 172c when opening in the maximum expansion.By the chimeric and carrier 47,147 that be provided with respect to the outer lateral body 72,172 of clutch of spline, its belleville spring 48,148 that is configured between this carrier 47,147 and fixed wall 45c, the 146c that moves through in the axial direction is restricted.

In addition, gearbox case 16 (with reference to Fig. 1) with once, secondary centrifuging counterweight 76,176 has the high rigid portion that is made of heavy section on the diametrically opposed position.

And, in clutch 70, pushing force F1c makes clutch 70 become the connection power that connects finishing stage, the second axial force F 1a are that power is removed in the connection that makes clutch 70 become notconnect state, similarly, in secondary clutch 170, the second secondary pushing force F2c makes clutch 170 become the connection power that connects finishing stage, and axial force F 2a is that power is removed in the connection that makes clutch 170 become notconnect state.

When pushing force F1c, F2c become above axial force F 1a, F2a big or small because of the increase of centrifugal force, it is that the center swing is expanded out that each governor weight 76,176 is connected under the state on the carrier 47,147 with this fulcrum 76a, 176a at fulcrum 76a, 176a, elastic pressing part 76d, 176d so that the mobile in the axial direction mode of the outer lateral body 72,172 of clutch with pushing force F1c, F2c abutment wall 72a, 172a are suppressed.And, at this moment, the outer lateral body 72,172 of push part 75,175 and clutch together moves in the axial direction, make each clutch plate 73,74,173,174 push in the axial direction and be in contact with one another towards fixed wall 45c, the 146c that one is located on the outside axial region 45b, 146, because the friction that the clutch plate that is in contact with one another is 73,74,173,174, the rotation of ring gear 50 or central gear 130 is passed to outer lateral body 72,172 of clutch and planetary carrier 40,140 via each clutch plate 73,74,173,174.

In addition, outside clutch under the situation of lateral body 72,172 with the rotation of identical rotational speed, the governor weight 176 of secondary clutch 170 becomes the counterweight structure that produces secondary pushing force F2c, and this secondary pushing force F2c is bigger than the pushing force F1c that the governor weight 76 by a clutch 70 produces.This counterweight structure is must be than the quality of each governor weight 76 big structure of the quality settings of each governor weight 176 in the present embodiment.Specifically, the quality of two governor weights 76,176 is set to: when input rotational speed Ni becomes the second fixing speed N2 (with reference to Fig. 6) described later as the first specific rotational speed, it is bigger than a pushing force F1c that secondary pushing force F2c becomes, the push part 175 of Yi Donging makes and places the push part 75 that connects finishing stage to move to the right on clutch 70 to the right, can remove the connection finishing stage of clutch 70.

In addition, as other embodiment, described counterweight structure can also adopt following structure: must be littler with the fulcrum 176a and the distance setting between the elastic pressing part 176d of governor weight 176 than the fulcrum 76a and the distance between the elastic pressing part 76d of governor weight 76, can and use these counterweight structures in addition.

And when governor weight 76,176 occupied described idle position, each clutch 70,170 was in the notconnect state that is not rotated transmission via clutch plate 73,173,74,174; When governor weight 76,176 occupies described maximum when expanding open position, each clutch 70,170 is in that 73,74,173,174 of clutch plate do not produce slidably, lateral body 71,171 and the outer lateral body 72,172 of clutch in the clutch (and then ring gear 50 and planetary carrier 40, or central gear 130 and planetary carrier 140) be with the finishing stage that is connected of constant speed rotation; When governor weight 76,176 that expansion is opened at described idle position and describedly maximumly expand between the open position and occupy when 73,74,173,174 of the clutch plate that is in contact with one another produce the neutral position of sliding, each clutch 70,170 is in the semi-connection state (or half-clutch state) that is passed to the outer lateral body 72,172 (and then planetary carrier 40,140) of clutch under the state that is rotated in the slip of following 73,74,173,174 of clutch plate of lateral body 71,171 (and then ring gear 50 or central gear 130) in the clutch.

Speed changer M has the clutch cancel system D as gear ratio change mechanism, in a plurality of variable-speed unit M1, M2 that this speed changer M is had, this clutch cancel system D is that the gear ratio r1 of variable-speed unit M1 changes to the variable-speed unit that is configured in input shaft 20 sides in described bang path.Clutch cancel system D is used for the connection finishing stage that is in the clutch 70 that connects finishing stage is removed, made its mechanism that becomes notconnect state, and clutch cancel system D has: elastic pressing part 134, and it is as drive portion; Intermediate transfer parts 36, it is passed to the driving force of elastic pressing part 134 push part 75 of clutch 70 as the releasing power that is used to remove clutch 70.

Intermediate transfer parts 36 have: the first intermediate transfer parts 37 of tubulose, and it can be connected on the elastic pressing part 134 in the axial direction; The second intermediate transfer parts 38 of tubulose, its can with the first intermediate transfer parts 37 butt in the axial direction.First, second intermediate transfer parts 37,38 are bearing on the output shaft 23 in the mode that can rotate and can move in the axial direction.

The second intermediate transfer parts 38 have pars contractilis 39, this pars contractilis 39 axially on two end part between to have as control be spring members 39a with the elastic member that suppresses parts.Elastic member is that described spring members 39a is made of one or more for example four belleville spring 39b in the present embodiment.The butt first intermediate transfer parts 37 on an end that constitutes by pars contractilis 39 of the second intermediate transfer parts 38, the inboard axial region 51 of butt ring gear 50 on another end that constitutes by thrust-bearing B13 of the second intermediate transfer parts 38.

And, when two clutches 70,170 are in notconnect state, interval on being formed with axially between the two intermediate transfer parts 37,38, the interval on this is axial is used for making two intermediate transfer parts 37,38 become mutual butt state when clutch 70 becomes the connection finishing stage.

Be connected on the second intermediate transfer parts 38 at the first intermediate transfer parts 37 that suppressed by elastic pressing part 134, under the mobile state that is prevented to the left of these second intermediate transfer parts 38, so that push part 75 occupies the mode that the position is removed in described pushing, suppress via 50 pairs of push part 75 of ring gear by the mode that makes governor weight 76 occupy described idle position with opposing pushing force F1c by its spring force for spring members 39a.

When a clutch 70 is in the connection finishing stage, because the increase of the rotational speed of the planetary carrier 140 of planetary gears P2, fly away from governor weight 176, secondary clutch 170 becomes from notconnect state the process that connects finishing stage, with the mobile phase to the right of push part 175 concomitantly, central gear 130 moves to the right, elastic pressing part 134 pushes first, second intermediate transfer parts 37,38, and the second intermediate transfer parts 38 are connected on the inboard axial region 51.At this moment, the pushing force F2c that 176 pairs of push part 175 of governor weight apply is bigger than the pushing force F1c that 76 pairs of push part 75 of governor weight apply, therefore, because described driving force, planetary carrier 40 and push part 75 are pushed by elastic pressing part 134 via first, second intermediate transfer parts 37,38 and move to the right.Because this of push part 75 moves axially, clutch 70 becomes notconnect state through semi-connection state.

And in order to remove the connection finishing stage of a clutch 70, pushing force F2c is so long as to surpass the stool and urine of pushing force F1c be sufficient.On the other hand, suppressed by elastic pressing part 134 and after temporarily becoming notconnect state at clutch 70, input rotational speed Ni increases and surpasses the 3rd fixing speed N3 (with reference to Fig. 6) as the second specific rotational speed, when clutch 70 becomes the connection finishing stage once more, the spring force of pushing force F1c antagonistic spring parts 39a, pars contractilis 39 dwindles in the axial direction, thus, push part 75 is moved to the left, and clutch 70 becomes the connection finishing stage.Therefore, the spring force of spring members 39a is the control elastic force pressure that the input rotational speed Ni that governor weight 76 is expanded once more open is limited.

With reference to Fig. 3, Fig. 4, overrunning clutch 80,180 is described.In addition, two overrunning clutchs 80,180 have identical structure basically, and therefore, in Fig. 4, record simultaneously relates to the reference character of the parts of overrunning clutch 80.

The central gear 30 of 80 couples of planetary gears P1 of overrunning clutch stops to the rotation of a direction A1,180 pairs of planetary carriers 140 of secondary overrunning clutch stop to the rotation of a direction A1, this overrunning clutch 80 and secondary overrunning clutch 180 have respectively: more than one rotary side engagement portion, it is bearing on the supporting axle of being located on the annulus 33,152 89,189 in the mode that can swing, here is as two groups of a plurality of a pair of ratchet pawls 81,82; 181,182; As the outside body component T of rotation restricting unit, which is provided with rotation constrained side fastening body is a plurality of claws 83; 183, each ratchet pawl 81,82; 181,182 engage this claw 83 on a direction A1; 183, thus, the rotation to a direction A1 of central gear 30 or ring gear 150 is stoped; As the spring 84 that suppresses parts; 184, it is to ratchet pawl 81,82; 181,182 suppress with the direction that claw 83,183 engages to each ratchet pawl 81,82,181,182.Spring 84; 184 are being led in being located at annulus 33 respectively by slotting; 152 and ratchet pawl 81,82; 181, after among fastening hole K1, the K2 on 182, be maintained at annulus 33; 152 and ratchet pawl 81,82; 181, on 182.

From radial outside with each ratchet pawl 81,82; 181,182 outside body component T that cover are for the shared single tubular part of two overrunning clutchs 80,180, the space S 1 of this outside body component T formation ring-type diametrically and between the inboard axial region 44b.Outside body component T is by being located at this outside body component T in one piece and going up and being supported on the gearbox case 16 to the support unit 65 of radial outside extension from the periphery of outside body component T.Support unit 65 is installed on the assembly department 16a (with reference to Fig. 1) of gearbox case 16 by bolt.

Ratchet pawl 81,82; 181,182 have: with claw 83; Engagement portion 81a, the 82al of 183 engagings; 81a, 182a; And the 81b of counterweight portion, 82b; 181b, 182b.By acting on the 81b of counterweight portion, 82b; Centrifugal force on 181b, the 182b, ratchet pawl 81,82; 181,182 can antagonistic spring 84; 184 elastic force pressure and be rocked to and occupy non-contacting position and (in Fig. 4, represent by double dot dash line.), this non-contacting position is engagement portion 81a, 82a; 181a, 182a not with claw 83; The position of 183 the 85a of fastening portion, 185a engaging.This non-contacting position is by block 87,187 regulations that are located on each annulus 33,152.When ratchet pawl 81,82; 181,182 when being in described non-contacting position, each ratchet pawl 81,82; 181, in 182, at radial outside, claw 83; 183 or outer circumferential face 81c, the 82c relative with outside body component T; The integral body of 181c, 182c from end on observation be positioned at a concentric imaginary circle 88 of rotation centerline L1, L2 on and the radially inner side of this imaginary circle 88.

Claw 83; 183 project to ratchet pawl 81,82 diametrically; 181, near 182, this claw 83; 183 have: have the 85a of fastening portion; The main part 85 of 185a; 185; Sense of rotation towards the rotation that allows central gear 30 or ring gear 150 is the slowly outstanding diametrically rake 86 of opposite direction A2; 186.When ratchet pawl 81,82; 181,182 not with the 85a of fastening portion; During the 185a butt, ratchet pawl 81,82; 181,182 by spring 84; 184 suppress and with rake 86; 186 contacts.Rake 86; 186 by be located at the 85a of fastening portion by sintering; The rubber material as elastic material on the 185a forms, therefore, and this rake 86; 186 constitute the buffer part that impact relaxes, and reduction results from and ratchet pawl 81,82; 181, the noise of 182 contact.

A pair of ratchet pawl 81; 181 with respect to rotation centerline L1, the configuration of L2 point symmetry ground, a pair of in addition ratchet pawl 82; 182 with respect to rotation centerline L1, the configuration of L2 point symmetry ground, and is configured to: when occupying each ratchet pawl 81,82; 181,182 and the 85a of fastening portion; During the clamped position of 185a engaging, a pair of in addition ratchet pawl 82; 182 occupy not and the 85a of fastening portion; The non-clamped position of 185a engaging.Thus, can increase whole ratchet pawls 81,82; 181,182 from the state that is positioned at non-clamped position with respect to outside body component T when a direction A1 rotates with the 85a of fastening portion; The chance of the engaging of 185a can become the rotation stopping state rapidly.

With reference to Fig. 2, Fig. 3, the integral body of the integral body of an engaging piece H1 and secondary engaging piece H2 is housed in the gear chamber 19, and this gear chamber 19 is by constituting with the bottom: be separated from each other in the axial direction as the push part 75 of the first side wall and as the push part 175 of second sidewall; By lateral body 72,172 outside the clutch that extends between two push part 75,175 and in the axial direction, as two outside axial region 45b of gear perisporium, 146 and the perisporium of the tubulose that constitutes as the outside body component T of periphery wall.This gear chamber 19 is formed in the space in the gearbox case 16.

Push part 75 and gear sidewall 54 associations that are presented axially between this push part 75 and the engaging piece H1 are moving, from end on observation, constitute dual-layer wall in comprising the radial extension whole or roughly integral body of two engaging piece H1, H2; Push part 175 and gear sidewall 133 associations that are presented axially between this push part 175 and the engaging piece H2 are moving, from end on observation, constitute dual-layer wall in comprising the radial extension whole or roughly integral body of two engaging piece H1, H2.

In addition, in two outside axial region 45b, 146, across two outside axial region 45b, 146 and dispose first, second limiting part 61,62, described two outside axial region 45b, 146 cover outside body component T from radial outside in the axial direction near relative end promptly is supported the 45d of portion, 146d mutually.And, this first, second limiting part 61,62 and support unit 65 two outside axial region 45b in the axial direction, 146 and the scope of outside body component T in, with comprise two outside axial region 45b, 146 and the mode on the border of outside body component T cover two outside axial region 45b, 146 and outside body component T from radial outside, therefore, can further reduce the noise based on the engagement sound at two engaging piece H1, H2 place.

In addition, outer lateral body 72 of clutch and outside axial region 45b, the outer lateral body 172 of clutch and outside axial region 146, each outside axial region 45b, 146 and outside body component T, position on it is axial has overlapped intersection, therefore, the wall that makes progress in the footpath of gear chamber 19 is also to constitute dual-layer wall on the described perisporium partly, thus, can improve the reduction effect of the noise that resulting from of two engaging piece H1, H2 place meshed, the width of the described perisporium on can reducing axially can dispose two variable-speed unit M1, M2 in the axial direction compactly.

With reference to Fig. 1, Fig. 2, output shaft 23 has the extension axial region 27 that extends to the left in the axial direction from variable-speed unit M2, and the output that 23 pairs of outlet side driving mechanisms 90 of this output shaft are had is taken out axle 91 and is rotated driving.Driving mechanism 90 also has except that axle 91 is taken out in output: as the output gear 92 of rotary driving body, this output gear 92 extends on the axial region 27 forming to be located on the position of space S 2, space S 2 its with variable-speed unit M2 between extending its outer circumferential face 27a being surrounded of axial region 27 on every side in the axial direction the predetermined range W; As the driven gear 93 of passive solid of rotation, it is located at output in the mode that can rotate and takes out on the axle 91, is driven by the engagement with output gear 92; Neutral gear clutch 95, its rotation with output gear 92 is taken out axle 91 with respect to output and is transmitted and block.

The integral body that axle 91 is taken out in output from end on observation be configured in variable-speed unit M2 position overlapped on.Output is taken out axle 91 and had the rotation centerline parallel with rotation centerline L1, L2, and this output is taken out axle 91 and had: the inside of extending in the axial direction in predetermined range W with respect to driven gear 93 prolongs axial region 93a; The outside that connects case halfbody 3b and extend outside the 15a of crankshaft room prolongs axial region 93b.Externally prolong axial region 93b and be provided with driving sprocket wheel 97a, be wound with chain 97b on this driving sprocket wheel 97a as whole carry-out part.

It is on the 16b of bearing portion on the gearbox case 16 that the inner shaft end that prolongs axial region 93a is bearing in the parts of being located at crankcase 3 splits via bearing B 14.Output is taken out axle 91 between driving sprocket wheel 97a and driven gear 93, is bearing on the case halfbody 3b in the mode that can rotate via bearing B15.

Output gear 92 and driven gear 93 constitute reducing gear, and this reducing gear is stipulated the outlet side gear ratio that the rotational speed No deceleration of output shaft 23 also further will be exported rotational speed No speed change.And it is in the axial direction two variable-speed unit M1 of reducing gear 18 separate configuration, the both sides of M2 that the rotation of output shaft 23 is passed to the outlet side driving mechanism 90 of driving sprocket wheel 97a and input side driving mechanism.

Neutral gear clutch 95 is configured in and prolongs on the axial region 93a, and is configured in the predetermined range W.Neutral gear clutch 95 has: selector 95a, and it is chimeric and take out the rotation of axle 91 one with output and can be fastened on the driven gear 93 by spline; Selector fork 95b, it is operated by clutch operating parts (not shown) and can drive selector 95a it is moved in the axial direction.

When the selector 95a that can move in the axial direction on prolonging axial region 93a occupies among Fig. 2 the activation point shown in the solid line, make the rotation of transmitting via driven gear 93 input to output taking-up axle 91 from output gear 92, and be rotated with following rotational speed, this rotational speed is that output takes out that axle 91 has carried out adjusting than the rotational speed No to output shaft 23 with the speed of being set by driving mechanism 90 and the rotational speeies that obtained.In addition, when selector 95a occupies among Fig. 2 the neutral position shown in the double dot dash line, output shaft 23 taken out the transmission blocking-up of the rotation of axle 91 to output.

With reference to Fig. 1, Fig. 5, Fig. 6, the action of speed changer M is described.

Mainly with reference to Fig. 5 (a), after the internal-combustion engine E starting, when the rotational speed of bent axle 6 is that the internal-combustion engine rotational speed surpasses the idle running rotational speed, centrifugal clutch 17 becomes coupled condition, then input shaft 20 and ring gear 50 are rotated with the input rotational speed Ni that transmits via reducing gear 18.At this moment, when input rotational speed Ni is first fixing speed N1 when following, in variable-speed unit M1, a direction A1 (with reference to Fig. 4) of the central gear 30 of planetary gears P1 thus on rotation stoped by unidirectional clutch 80 and be in halted state.Therefore, in planetary gears P1, planetary carrier 40 is with according to based on the gear ratio r1 of planetary gears P1 the input rotational speed Ni rotational speed that obtains of having carried out slowing down being rotated, in clutch 70, by based on planetary pinion 41 axial force F 1a with the engagement of ring gear 50, ring gear 50 suppresses push part 75 to the right, push part 75 occupies described pushing and removes the position, therefore, clutch plate 73,74 occupies the position of separation each other, governor weight 76 occupies described idle position, and clutch 70 is in notconnect state.

On the other hand, in variable-speed unit M2, a direction A1 (with reference to Fig. 4) of the ring gear 150 of planetary gears P2 thus on rotation stoped by unidirectional clutch 180 and be in halted state.Therefore, in planetary gears P2, planetary carrier 140 is to be rotated according to the rotational speed that obtains of having carried out slowing down based on the gear ratio r2 pair of rotational speed with the central gear 130 of the planetary carrier 40 constant speed rotation of planetary gears P1 of planetary gears P2, in clutch 170, by based on planetary pinion 141 axial force F 2a with the engagement of central gear 130, central gear 130 suppresses push part 175 to the left, push part 175 occupies described pushing and removes the position, therefore, clutch plate 173,174 occupy the position of separation each other, governor weight 176 occupies described idle position, and clutch 170 is in notconnect state.

Under this state, speed changer M establishes the long-pending i.e. gear ratio R1 of 1 speed of two gear ratio r1, r2, output shaft 23 with according to the maximum gear ratio of speed changer M promptly this 1 gear ratio R the rotational speed that 1 input rotational speed Ni has carried out speed change is rotated.And when occupying described activation point, the rotation of output shaft 23 inputs to output via output gear 92 and driven gear 93 and takes out axle 91 at neutral gear clutch 95 (with reference to Fig. 2).

Mainly with reference to Fig. 5 (b), when input rotational speed Ni surpasses the first fixing speed N1 and is that the second fixing speed N2 bigger than this first fixing speed N1 is when following, in variable-speed unit M1, because the increase of the rotational speed of planetary carrier 40, in clutch 70, surpass axial force F 1a according to the pushing force F1c that acts on the centrifugal force on the governor weight 76, governor weight 76 expands to be opened.And governor weight 76 occupies the described maximum open position that expands, and push part 75 is so that ring gear 50 mode mobile to the left and that clutch plate 73,74 is contacted each other pushes, and clutch 70 becomes the connection finishing stage.Therefore, to direction A2 (with reference to Fig. 4) rotation opposite with a direction A1, gear ratio r1 is 1, promptly becomes direct connecting state with input rotational speed Ni for ring gear 50, planetary carrier 40 and central gear 30.

On the other hand, in variable-speed unit M2,, be below the axial force F 2a because basis acts on the pushing force F2c of the centrifugal force on the governor weight 176, so governor weight 176 occupy described idle position though the rotational speed of planetary carrier 140 increases.Therefore, planetary gears P2 and clutch 170 are in state identical when establishing 1 fast gear ratio R1.

Under this state, speed changer M establishes the gear ratio R2 of 2 speed.

Mainly with reference to Fig. 5 (c), surpass the second fixing speed N2 and be that the three fixing speed N3 bigger than this second fixing speed N2 is when following at input rotational speed Ni, in secondary variable-speed unit M2, because the increase of the rotational speed of planetary carrier 140, in secondary clutch 70, surpass axial force F 2a according to the pushing force F2c that acts on the centrifugal force on the governor weight 176, governor weight 176 expands to be opened.And governor weight 176 occupies the described maximum open position that expands, and push part 175 is so that central gear 130 mode mobile to the right and that clutch plate 173,174 is contacted each other pushes, and secondary clutch 170 becomes the connection finishing stage.Therefore, ring gear 150, planetary carrier 140 and central gear 130 are promptly once exported rotational speed Na to direction A2 (with reference to Fig. 4) rotation opposite with a direction A1 with the rotational speed of planetary carrier 40, gear ratio r2 is 1, promptly becomes direct connecting state.

And, from as 2 fast gear ratio R2 of low speed side gear ratio to as the 3rd gear ratio R3 transition of the high-speed side gear ratio of comparing high-speed side with this 2 fast gear ratio R2 the time, reach through semi-connection state from notconnect state the process that connects finishing stage at clutch 170, central gear 130 moves integratedly to the right with the push part 175 that moves to the right, elastic pressing part 134 makes first, the second intermediate transfer parts 37,38 move to the right, and move to the right via the push part 75 that ring gear 50 makes clutch 70, this push part 75 is moved to the direction of the connection finishing stage of removing clutch 70.

Therefore, in clutch 70, governor weight 76 moves to described idle position from the described maximum open position that expands, clutch 70 becomes notconnect state from connecting finishing stage through semi-connection state, and the rotational speed that has obtained with gear ratio r1 input rotational speed Ni has been carried out slowing down with lateral body 72 and planetary carrier 40 outside the clutch of input rotational speed Ni rotation is rotated before this.The block 135 that the amount of movement of push part 175 and central gear 130 is limited is connected on the end of left of inboard axial region 44b of planetary carrier 40, stops the moving to the right of push part 175 and central gear 130 thus.

Under this state, speed changer M establishes 3 fast gear ratio R3, and this 3 fast gear ratio R3 equates with gear ratio r1 based on variable-speed unit M1.

In addition, control gear 13 carries out following control: from 2 fast gear ratio R2 when the 3 fast gear ratio R3 transition, detecting two clutches 70 by the clutch coupled condition 13b of feeler mechanism, 170 at least one sides become semi-connection state, and detect time that this semi-connection state continues when exceeding schedule time by the 13c of time detecting mechanism, by the rotational speed control mechanism is throttle valve 8a, in Fuelinjection nozzle 9 and the ignition mechanism 10 at least one, to air inflow, fuel feed and igniting opportunity and the output controlled quentity controlled variable of at least one are controlled, thus, become the connection finishing stage in order to carry out the transition to the clutch 170 that is in semi-connection state, or the clutch 70 that is in semi-connection state becomes the input rotational speed Ni of notconnect state, the mode that increases with input rotational speed Ni changes this input rotational speed Ni, therefore, can eliminate the semi-connection state of clutch 70 or clutch 170 rapidly, quicken from the transition of 2 fast gear ratio R2 to 3 fast gear ratio R3.

On the contrary, from 3 fast gear ratio R3 when the 2 fast gear ratio R2 transition, the described rotational speed control mechanism that control gear 13 is controlled, become the input rotational speed Ni that the clutch 170 that connects finishing stage or be in semi-connection state becomes notconnect state in order to carry out the transition to the clutch 70 that is in semi-connection state, the mode that reduces with input rotational speed Ni changes this input rotational speed Ni.

Equally, from 1 fast gear ratio R1 to 2 fast gear ratio R2 transition, from 3 fast gear ratio R3 when the 4 fast gear ratio R4 transition, when the time 13c of feeler mechanism detects the situation that endurance of the semi-connection state by the detected clutch 70 of the clutch coupled condition 13b of feeler mechanism exceeds schedule time, control gear 13 carries out following control: described rotational speed control mechanism is controlled, thus, become the input rotational speed Ni that connects finishing stage in order to carry out the transition to clutch 70, so that the mode that input rotational speed Ni increases changes this input rotational speed Ni; In addition, from 2 fast gear ratio R2 to 1 fast gear ratio R1 transition, from 4 fast gear ratio R4 when the 3 fast gear ratio R3 transition, when the time 13c of feeler mechanism detects the situation that endurance of the semi-connection state of the clutch 70 that detects by the clutch coupled condition 13b of feeler mechanism exceeds schedule time, control gear 13 carries out following control: described rotational speed control mechanism is controlled, thus, become the input rotational speed Ni of notconnect state in order to carry out the transition to clutch 70, change this input rotational speed Ni so that import the mode of rotational speed Ni minimizing by described rotational speed control mechanism.

Mainly with reference to Fig. 5 (d), when input rotational speed Ni surpasses the 3rd fixing speed N3, in variable-speed unit M2, planetary gears P2 and clutch 170 identical state when being in the fast gear ratio R3 of establishment aforesaid 3.

On the other hand, in variable-speed unit M1, be pushed under the state that pressure F2c suppresses to the right at first, second intermediate transfer parts 37,38, is the push part 75 that suppress on the right side by the spring force of spring members 39a to connecting the releasing direction, because increase with the rotational speed of importing the corresponding planetary carrier 40 of rotational speed Ni, in clutch 70, pushing force F1c surpasses the spring force of spring members 39a, and governor weight 76 expands to be opened.And governor weight 76 occupies the described maximum open position that expands, and push part 75 is so that ring gear 50 mode mobile to the left and that clutch plate 73,74 is contacted with each other pushes, and clutch 70 becomes the connection finishing stage.Therefore, gear ratio r1 is 1, and promptly variable-speed unit M1 becomes direct connecting state.

And owing to all become 1 based on two gear ratio r1, the r2 of two variable-speed unit M1, M2, therefore, speed changer M becomes direct connecting state, and minimum gear ratio i.e. 4 fast gear ratio R4 is established, and output shaft 23 is rotated with input rotational speed Ni.

Next, effect and the effect to the mode of execution that constitutes like that as described above describes.

In speed changer M, the engaging piece H1 of planetary gears P1 and the engaging piece H2 of planetary gears P2 are housed in the gear chamber 19, this gear chamber 19 is by the push part 75 of the clutch 70 that is separated from each other in the axial direction and the push part 175 of clutch 170, with be formed in two push part 75, between 175 (promptly, two push part 75 in the axial direction, 175 inboard) two planetary carriers 40 of the perisporium that extends in the axial direction, 140 outside axial region 45b, 146 and overrunning clutch 80,180 outside body component T forms, the ring gear 50 of planetary gears P1 has the gear sidewall 54 between push part of being presented axially in 75 and the engaging piece H1, the central gear 130 of planetary gears P2 has the gear sidewall 133 between push part of being presented axially in 175 and the engaging piece H2, and push part 75 and gear sidewall 54 and push part 175 and gear sidewall 133 are comprising two engaging piece H1 respectively from end on observation, constitute dual-layer wall in the radial extension of H2.

By this structure, because have once, secondary planetary gears P1, P2 and once, secondary clutch 70,170 once, secondary variable-speed unit M1, M2 be housed in the shared gear chamber 19, therefore, the component parts sharing of two variable-speed unit M1, M2 can be realized, cost cutting can be realized based on the reduction of number of spare parts.And, by the sharing of this component parts, can make the compactness of the configuration of this component parts become possibility, the miniaturization of speed changer M becomes possibility.

In addition, in crankcase 3 and be housed in two engaging piece H1 in the gear chamber 19 that is formed in the gearbox case 16, H2, from radial outside by two outside axial region 45b, 146 and outside body component T cover, both sides on axially are to two variable-speed unit M1, the component parts of M2 utilizes, thus, covered by the dual-layer wall that forms of push part 75 and gear sidewall 54 with by the dual-layer wall that push part 175 and gear sidewall 133 form, therefore, not only have based on two outside axial region 45b, 146 and the noise of outside body component T reduce effect, and, because the double-wall structure of the sidewall axially can improve resulting from each engaging piece H1, the reduction effect of the noise of the engagement of H2.

Cover two engaging piece H1 from radial outside, the described perisporium of H2, by two planetary gears P1, each planetary carrier 40 of P2,140 outside axial region 45b, 146 and two overrunning clutchs 80,180 common component that had i.e. outside body component T constitute, thus, utilize two variable-speed unit M1, the component parts of M2 and the described perisporium of the gear chamber 19 that forms, remove two planetary gears P1, each planetary carrier 40 of P2,140 conduct once, the outside axial region 45b of secondary gear perisporium, outside 146, also pass through for two overrunning clutchs 80,180 periphery walls as shared component parts are that outside body component T constitutes, therefore, by two variable-speed unit M1, two overrunning clutchs 80 that M2 had, the sharing of 180 component parts, can make the simplifying the structure of described perisporium of formative gear chamber 19, the compactness that helps the configuration of component parts, and, can make two overrunning clutchs 80,180 configuration compactness.

Gear ratio control unit C1 has clutch 70, this clutch 70 have allow to connect from a plurality of clutch plate 73,74 rotational speed Ni according to input shaft 20 connect from push part 75, gear ratio control unit C2 has clutch 170, this clutch 170 have allow to connect from a plurality of clutch plate 173,174 according to planetary carrier 40 once export rotational speed Na connect from push part 175, formative gear chamber 19 axially on the two side respectively by two clutches 70,170 push part 75,175 constitute, thus, owing to can utilize two clutches 70,170 two push part 75,175 constitute the wall in the double walled outside of gear chamber 19, therefore, needn't make planetary gears P1 in order to reduce noise, the ring gear 40 of P2, central gear 130 grades once, secondary key element gear maximizes diametrically, can reduce to result from two engaging piece H1, the noise of the engagement of H2.

The secondary output solid of rotation that will input to output shaft 23 with the rotation that obtains based on the gear ratio R of variable-speed unit M1, M2 is push part 175 of clutch 170, thus, the push part 175 that the coupled condition of clutch 170 is controlled have reduce result from each engaging piece H1, H2 engagement noise effect and will rotate effect to output shaft 23 transmission, therefore, can cut down number of spare parts.

In speed changer M, overrunning clutch 80,180 have the shared outside body component T between the engaging piece H2 of the engaging piece H1 that is configured in planetary gears P1 in the axial direction and planetary gears P2, thus, has planetary gears P1, P2 and gear ratio control unit C1, the variable-speed unit M1 of C2, among the M2, because overrunning clutch 80,180 have the formation of utilizing two engaging piece H1 in the axial direction, the outside body component T of the rotation restricting unit that the space between the H2 and the conduct of disposing are shared, therefore, can realize overrunning clutch 80, the sharing of 180 component parts can be realized the cost cutting of cutting down based on number of spare parts.

Has the limiting part 60 that limits that moves axially to the ring gear 150 of the central gear 30 of planetary gears P1 and planetary gears P2, outside body component T is fixed on this limiting part 60 that is fixed on the gearbox case 16, therefore, in planetary gears P1, P2, utilization is fixed central gear 30 and the ring gear 150 mobile limiting part that limits 60 external lateral body parts T in the axial direction, therefore, the support unit of the special use of body component T outside not needing to be used to support, the reduction of number of spare parts becomes possibility.

Among the speed changer M, effect has the central gear 30 of the axial force F 1b that the central gear 30 by planetary gears P 1 produces with planetary pinion 41 engagements of planetary carrier 40 and effect that the planetary carrier 140 of the axial force F 2b that the ring gear 150 by planetary gears P2 produces with planetary pinion 141 engagements of planetary carrier 140 is arranged, have a thrust that pushes the other way around mutually in the axial direction and bear portion 46, this thrust is born portion 46 and is configured in the axial direction between the pushing portion 153 of the pushing portion 34 of central gear 30 and planetary carrier 140, thus, has planetary gears P1, the variable-speed unit M1 of P2, among the M2, bear 46 pairs of central gears 30 of portion and moving axially of planetary carrier 140 stops with a shared thrust, on described central gear 30 and the planetary carrier 140 there be by planetary gears P1 effect, the engagement at P2 place and the axial force F 1b that produces, F2b, therefore, with respect to planetary gears P1, P2, thrust is born portion 46 and is realized sharing, can realize the cost cutting of cutting down based on number of spare parts.

In addition, central gear 30 that axial force F 1b, F2b are applied to it respectively and planetary carrier 140 bear portion 46 to shared thrust the other way around mutually in the axial direction and push, therefore, bear portion 46 for a thrust, two axial force F1b, F2b cancel out each other in the mode of making a concerted effort to diminish, therefore, can make thrust bear the designs simplification of portion 46.

Ring-shaped member is that thrust is born on the inboard axial region 44b that portion 46 only is located at planetary carrier 40, central gear 30 and planetary carrier 140 are configured in the both sides that thrust is born portion 46 in the axial direction respectively, thus, because only the inboard axial region 44b that utilizes conduct once to export solid of rotation is provided with thrust and bears portion 46, wherein, once export solid of rotation and will input to variable-speed unit M2 by the rotation that variable-speed unit M1 has carried out speed change, therefore, bear portion 46 in order to support thrust, need not the parts except that inboard axial region 44b, number of spare parts can be cut down, the designs simplification of speed changer M can be made in addition.

In addition, because central gear 30 and planetary carrier 140 bear portion 46 with respect to thrust in the axial direction and are configured in both sides, therefore, can be in the axial direction configuration center gear 30 and planetary carrier 140 compactly, and then can dispose two variable-speed unit M1, M2 in the axial direction compactly.

Thrust is born portion 46 and is configured in the space S 1, this space S 1 is that the outside body component T by the overrunning clutch 80,180 that the rotation on the direction A1 of central gear 30 and planetary carrier 140 is stoped surrounds, thus, thrust is born portion 46 and is configured by the space S 1 that the outside body component T of the overrunning clutch 80,180 that limits by the sense of rotation to central gear 30 and planetary carrier 140 forms, therefore, can be in the axial direction configuration center gear 30 and planetary carrier 140 compactly.

Speed changer M has shared limiting part 60, the planetary carrier 40 of 60 couples of planetary gears P1 of this limiting part and the moving axially of planetary carrier 140 of planetary gears P2 are limited, this limiting part 60 have to planetary carrier 40 axially on two directions the mobile support lug 61b that limits and to planetary carrier 140 axially on the mobile support lug 62b that limits of two directions, thus, has planetary gears P1, P2 and gear ratio control unit C1, the variable-speed unit M1 of C2, among the M2, because by shared 60 couples of planetary gears P1 of limiting part, two planetary carriers 40 of P2,140 move axially limits, therefore, with respect to planetary gears P1, P2, limiting part 60 is realized sharing, and the cost cutting of cutting down based on number of spare parts becomes possibility.

In addition, since support lug 61b, 62b that can be by split respectively to two planetary carriers 40,140 axially on moving axially of two directions limit, therefore, can increase the degrees of freedom that moves axially the configuration of two planetary carriers 40,140 that limit by 60 pairs of limiting parts.

Limiting part 60 is made of with second limiting part 62 with second support lug 62b first limiting part 61 with first support lug 61b, first limiting part 61 and second limiting part 62 are being installed under the state that mutually combines on the assembly department 16a that is located on the gearbox case 16, thus, first, second limiting part 61,62 is being installed under the incorporate state on the gearbox case 16, therefore, the mounting structure of limiting part 60 is simplified.

First, second limiting part 61,62 has respectively: the 61a of tube portion, the 62a of Yan Shening in the axial direction; Support lug 61b, 62b that the forward end of the 61a of tube portion, 62a on is axially radially extended; The 61a of tube portion in the axial direction, the cardinal extremity flange 61c that the terminal side of 62a radially extends, 62c, first, second limiting part 61,62 this first, second limiting part 61,62 cardinal extremity flange 61c, be installed under the state that 62c is bonded to each other on the assembly department 16a, thus, has a 61a of portion, 62a and support lug 61b, first of 62b, second limiting part 61,62 with base flange 61c, 62c mutually combines and constitutes, therefore, with limiting part is that the situation of flat-shaped part is compared, the rigidity of limiting part 60 improves, in addition, because the rigidity height, thereby can form limiting part 60 with the material of the thin thickness of easy processing.

Limiting part 60 together is installed on the gearbox case 16 with the support unit 65 that outside body component T to overrunning clutch 80,180 supports, and therefore, number of spare parts, installation position tail off, and the mounting structure of limiting part 60 and support unit 65 is simplified.

In speed changer M, the clutch 70 of variable-speed unit M1 has: can the phase mutual connection from a plurality of clutch plate 73,74; Governor weight 76, when the centrifugal force that produces according to input rotational speed Ni increased, this governor weight 76 was in contact with one another a plurality of clutch plate 73,74, the clutch 170 of variable-speed unit M2 has: can the phase mutual connection from a plurality of clutch plate 173,174; Governor weight 176, when according to once the exporting centrifugal force that rotational speed Na produces and increase of variable-speed unit M1, this governor weight 176 is in contact with one another a plurality of clutch plate 173,174, the control gear 13 that internal-combustion engine E is had has: the clutch coupled condition 13b of feeler mechanism, and the situation that its at least one side to clutch 70 and clutch 170 is in semi-connection state detects; The 13c of time detecting mechanism, it is to detecting by the endurance of the detected semi-connection state of the clutch coupled condition 13b of feeler mechanism, control gear 13 is controlled as follows: when exceeding schedule time by the detected endurance of the 13c of time detecting mechanism, in order to change input rotational speed Ni and to make it carry out the transition to the rotational speed of removing semi-connection state, and the described rotational speed control mechanism of control input rotational speed Ni is controlled, thus, at two clutches 70, at least one side in 170 continues semi-connection state during the stipulated time, this rotational speed control mechanism of being controlled by control gear 13, the rotational speed Ni of input shaft 20 is changed to become the mode that connects finishing stage, therefore, can remove clutch plate 73 under the semi-connection state in early days, 74,173,174 each other sliding modes.Consequently, can suppress the wearing and tearing of clutch plate 73,74,173,174, can improve the durability of centrifugal clutch 70,170, in addition, drive sense thereby travelling becomes well can promote.

Make clutch 170 from notconnect state to the process that connects the finishing stage transition, governor weight 176 makes clutch 70 from connecting finishing stage to the notconnect state transition, thus, can remove in early days clutch 170 from notconnect state to the way that connects the finishing stage transition semi-connection state and clutch 70 from connecting the semi-connection state of finishing stage to the way of notconnect state transition, therefore, can improve the durability of each clutch 70,170, in addition, good can the lifting driven sense thereby travelling becomes.

In addition, connect finishing stage when clutch 170 becomes, when gear ratio r2 is changed, be in the clutch 70 that connects finishing stage and become notconnect state, thus, can access the gear ratio of the combination of the gear ratio r1 when being in secondary gear ratio r2 when connecting finishing stage and clutch 70 and being in notconnect state based on clutch 170.Consequently, compare, can obtain the quantity of the gear ratio of establishing by quantity planetary gears still less by speed changer M with being in the clutch 70 that is connected finishing stage can not become notconnect state when input rotational speed Ni increases speed changer.

The speed change state feeler mechanism that be based on the clutch coupled condition 13b of feeler mechanism actual speed change and predefined setting gear ratio detect speed change state, wherein, actual speed change is that the output rotational speed No according to the reality of the input rotational speed Ni of reality and output shaft 23 calculates, thus, to be actual gear ratio detect the semi-connection state of each clutch 70,170 gear ratio by reality, therefore, can improve the control accuracy that is used to remove semi-connection state.

The rotational speed control mechanism is throttle valve 8a, Fuelinjection nozzle 9 or ignition mechanism 10, by at least one the output controlled quentity controlled variable in the air inflow of internal-combustion engine E, fuel feed and igniting opportunity is controlled, and be that the internal-combustion engine rotational speed is controlled to controlling object, thus, can the rotational speed Ni of input shaft 20 be controlled, can remove the semi-connection state of each clutch 70,170.

For example, control gear 13 is according to the testing result of the clutch coupled condition 13b of feeler mechanism, internal-combustion engine rotational speed when not being in semi-connection state and the internal-combustion engine rotational speed when being in semi-connection state compare, when the internal-combustion engine rotational speed under the semi-connection state is big (or hour), make the judgement that is in the transition of shift-up direction (or downshift direction), by to throttle valve 8a, in Fuelinjection nozzle 9 or the ignition mechanism 10 at least one controlled, can be to air inflow, in fuel feed and igniting opportunity at least one controlled, and makes the internal-combustion engine rotational speed increase (or minimizing) and breaks away from semi-connection states until clutch 70 or clutch 170.

In speed changer M, gear ratio control unit C1, C2 have overrunning clutch 80,180, between input shaft 20 on the rotation bang path and output shaft 23, has overrunning clutch 25, this overrunning clutch 25 only is passed to input shaft 20 with the rotation of output shaft 23 when output rotational speed No surpasses input rotational speed Ni, thus, when two-wheeled motor vehicle slows down when the rotation of trailing wheel 98 is rotated driving by 23 pairs of input shafts 20 of output shaft, being rotated among planetary gears P1, the P2 of output shaft 23 shunted, and is passed to input shaft 20 via overrunning clutch 25.Consequently, even during the gear ratio R1～R3 beyond speed changer M is in the 4 fast gear ratio R4 that become direct connecting state, also can bring into play the effect of engine braking, therefore, can (bring into play the effect of engine braking among or the gear ratio R1～R4) in whole speed change levels.

Input shaft 20 and planetary gears P1, P2 are bearing in the radial outside of output shaft 23 in the mode that can rotate, on the shaft end 21a of input shaft 20, be provided with wide diameter portion to axially open, overrunning clutch 25 is configured in the radially inner side of this wide diameter portion, thus, because overrunning clutch 25 is located on the shaft end 21a of input shaft 20, and can install and remove with respect to the described wide diameter portion to axially open, therefore, the mounting or dismounting of overrunning clutch 25 are easy.

In speed changer M, output shaft 23 has the extension axial region 27 that extends in the axial direction from secondary variable-speed unit M2, outlet side driving mechanism 90 between itself and variable-speed unit M2 axially on predetermined range W in, extend axial region 27 around having: forming on the position of the space S 2 of surrounding the outer circumferential face that extends axial region 27 and be located at the output gear 92 that extends on the axial region 27; Be located at the driven gear 93 that output is taken out on the axle 91 and is output gear 92 drivings; The rotation of output gear 92 is taken out the axle 91 neutral gear clutches 95 that transmit and block with respect to output, the integral body that axle 91 is taken out in output from end on observation be configured in variable-speed unit M2 position overlapped on, neutral gear clutch 95 is configured in the predetermined range W in the axial direction, thus, be formed on the space S 2 of the radial outside that extends axial region 27 by utilization, can be configured in from end on observation with variable-speed unit M2 position overlapped on output take out axle 91 configurations diametrically on the position near output shaft 23, in addition, owing to neutral gear clutch 95 can be disposed near output shaft 23 ground diametrically, therefore, can make outlet side driving mechanism 90 diametrically near output shaft 23 ground compact arrangement, can make speed changer M miniaturization diametrically with output taking-up axle 91 and neutral gear clutch 95.

Variable-speed unit U is made of with the secondary variable-speed unit M2 with secondary planetary gears P2 and secondary gear ratio control unit C2 a variable-speed unit M1 with a planetary gears P1 and a gear ratio control unit C1, input has the rotation of the push part 175 of secondary variable-speed unit M2 on output shaft 23, gear ratio control unit C1 has the overrunning clutch 80 that central gear 30 is stoped to the rotation of a direction, secondary gear ratio control unit C2 has secondary overrunning clutch 180, two overrunning clutchs 80 that ring gear 150 is stoped to the rotation of a direction, 180 have the outside body component T of the shared rotation restricting unit of conduct between the secondary engaging piece H2 of engaging piece H1 being configured in a planetary gears P1 in the axial direction and secondary planetary gears P2.

According to this structure, have once, secondary planetary gears P1, P2 and once, secondary gear ratio control unit C1, C2 once, secondary variable-speed unit M1, among the M2, once, secondary overrunning clutch 80,180 have the formation of utilization in the axial direction once, secondary engaging piece H1, space between the H2 and the shared outside body component T that disposes, therefore, with have each the outside body component once, the secondary overrunning clutch in the axial direction separate configuration once, the speed changer in the outside of secondary planetary gears is compared, in speed changer M, can be with two variable-speed unit M1, M2 disposes in the axial direction compactly, therefore, the neutral gear clutch 95 that is configured in the described predetermined range W can be disposed in the axial direction compactly, described predetermined range W depends on from the length of the extension axial region 27 of variable-speed unit M2 extension.

Below, the mode that a part of structure of aforesaid mode of execution is changed just describes after changing structure.

Speed changer M has two variable-speed unit M1, M2 in said embodiment, but a plurality of same variable-speed unit M1, M2 beyond can also having two in this case, can be suitable for the present invention at least two variable-speed unit M1, M2.

The main shaft of speed changer can be a supporting axle coaxial with the rotation centerline of input shaft or output shaft or that have parallel central axis and variable-speed unit is supported, and in addition, this supporting axle can also be non-rotary axle.

In planetary gears, can the first one times the key element gear be that central gear, the second key element gears are ring gears, in the secondary planetary gears, can the first secondary key element gear be that ring gear, the second secondary key element gear are central gears.

Can replace governor weight 76,176, and constitute the driver part that each push part 75,175 is driven by the pressure type actuator or the electromagnetic type actuator that utilize hydraulic pressure etc.

It can be so that the spring force of the spring that the mode that governor weight 76,176 occupies described idle position is suppressed governor weight 76,176 that power is removed in the connection of clutch 70,170.

Limiting part 60 can only be made of parts.

The clutch coupled condition 13b of feeler mechanism that control gear 13 has can detect the temperature of the lubricant oil that clutch 70,170 is lubricated.For example, because when at least one side of two clutches 70,170 slides, the temperature of lubricant oil rises, therefore, temperature according to the detected lubricant oil of temperature transducer that is had by control gear 13, when the temperature of lubricant oil is higher than set point of temperature, or when the climbing of the temperature of lubricant oil was bigger than specified value, the clutch coupled condition 13b of feeler mechanism detected the semi-connection state of each clutch 70,170.And, in this case,, therefore, can realize the cost cutting of cutting down based on number of spare parts owing to can utilize the temperature transducer of the temperature that detects lubricant oil to detect the semi-connection state of each clutch 70,170.

Internal-combustion engine E can be the multi-cylinder internal-combustion engine with a plurality of cylinders.

Prime mover can be the device beyond the internal-combustion engine, for example can be electric motor.

Claims (5)

1. automatic transmission has:

Input shaft by prime mover rotation driving;

A variable-speed unit, this variable-speed unit has: a planetary gears, it has three key element gears, the i.e. planetary carrier of central gear, planetary gear bearing and ring gears; A gear ratio control unit, its gear ratio to a described planetary gears of rotation that described input shaft is arranged based on input is controlled;

The secondary variable-speed unit, this secondary variable-speed unit has: the secondary planetary gears, it has three secondary key element gears, the i.e. planetary carrier of central gear, planetary gear bearing and ring gears; The secondary gear ratio control unit, its secondary gear ratio to the described secondary planetary gears of the rotation of once exporting solid of rotation that a described variable-speed unit is arranged based on input is controlled;

Output shaft is imported the rotation of the secondary output solid of rotation of described secondary variable-speed unit to this output shaft;

Gearbox case, this gearbox case are accommodated a described variable-speed unit and described secondary variable-speed unit,

It is characterized in that,

The engaging piece of a described planetary gears and the secondary engaging piece of described secondary planetary gears are housed in the gear chamber, this gear chamber is formed in the described gearbox case by the first side wall that is separated from each other in the axial direction and second sidewall and the perisporium that extends in the axial direction between described the first side wall and described second sidewall

Described the first side wall and described second sidewall are made of the described secondary sidewall that described one time gear ratio control unit had sidewall and secondary gear ratio control unit had respectively,

The first key element gears in described three key element gears have a gear sidewall that is presented axially between a described sidewall and the described engaging piece,

The first secondary key element gear in described three secondary key element gears has the secondary gear sidewall that is presented axially between described secondary sidewall and the described secondary engaging piece,

A described sidewall and a described gear sidewall and described secondary sidewall and described secondary gear sidewall constitute dual-layer wall at the radial extension that comprises a described engaging piece and described secondary engaging piece respectively from end on observation.

2. automatic transmission as claimed in claim 1 is characterized in that:

Described perisporium is by constituting with the bottom: the gear perisporium that the three key element gear in described three key element gears had; The secondary gear perisporium that the 3rd secondary key element gear in described three secondary key element gears is had; The shared periphery wall that a described gear ratio control unit and described secondary gear ratio control unit are had.

3. automatic transmission as claimed in claim 2 is characterized in that:

A described gear ratio control unit has once rotation restriction overrunning clutch, and this once rotates restriction and stops the second key element gears in described three key element gears to the rotation of a direction with overrunning clutch,

Described secondary gear ratio control unit has secondary rotation restriction overrunning clutch, and this secondary rotation limits with overrunning clutch and stops the second secondary key element gear in described three secondary key element gears to the rotation of a direction,

Described periphery wall is for described restriction overrunning clutch and the described secondary rotation restriction shared outside body component of overrunning clutch of once rotating.

4. as each described automatic transmission of claim 1～3, it is characterized in that:

A described gear ratio control unit has the speed change clutch one time, this speed change with clutch have allow to connect from a plurality of clutch plate according to the rotational speed of described input shaft connect from a push part,

Described secondary gear ratio control unit has secondary speed change clutch, this secondary speed change with clutch have allow to connect from a plurality of clutch plate according to the described rotational speed of once exporting solid of rotation connect from the secondary push part,

A described sidewall and described secondary sidewall are made of a described push part and described secondary push part respectively.

5. automatic transmission as claimed in claim 4 is characterized in that: described secondary output solid of rotation is described secondary push part.

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