CN101839313B - Automatic transmission with planetary gear mechanism - Google Patents

Abstract

The present invention provides an automatic transmission. In the automatic transmission which comprises a plurality of speed changing units comprising planetary gear mechanisms, the cost can be reduced based on the reduction of the number of components. Furthermore, a noise reduction effect based on engagement sound can be obtained. In the transmission (M), the engagement parts (H1, H2) of the planetary gear mechanisms (P1, P2) are accommodated in a gear chamber (19) which is composed of the following components: pushing components (75, 175) of clutches (70, 170) which are spaced from each other in the axial direction, outer shafts (45b, 146) of two planetary gear carriers (40, 140) and the outer component (T) of unidirectional clutches (80, 180), which form a peripheral wall that extends in the axial direction. The gear side wall (54) of the pushing component (75) and an annular gear (50) and the gear side wall (133) of the pushing component (175) and a central gear (130) respectively form a double-layer wall in an axial range comprising two engagement parts (H1, H2) when observed from the axial direction.

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 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, because a plurality of gears are normal in the planetary gears of each variable-speed unit time engagement, can make the noise that automatic transmission produces become large owing to resulting from the engagement sound of this engagement.Therefore, in order to reduce noise, form the locular wall of the engaging piece of planetary gears being accommodated gear chamber in the situation that be provided with, because each planetary gears 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 be all identical in each variable-speed unit, thereby more difficult based on the reduction of the part number of the sharing of the parts in a plurality of variable-speed units, have room for improvement aspect the cost cutting of the reduction of number of spare parts.

Summary of the invention

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

Technological scheme 1 of the present invention is described is a kind of automatic transmission, has: by the input shaft (20) of prime mover (E) rotary actuation; 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), the rotation of the secondary of this output shaft described secondary variable-speed unit of input (M2) being exported solid of rotation (175); 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 a 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 the second sidewall (175) and the perisporium (45b that extends in the axial direction between described the first side wall (75) and described the second sidewall (175), 146, T) be formed in described gearbox case (16), the described secondary sidewall (175) that the sidewall (75) that described the first side wall (75) and described the second sidewall (175) are had by a described gear ratio control unit (C1) respectively and secondary gear ratio control unit (C2) have consists of, 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 a 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 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), consist of 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 the described automatic transmission of technological scheme 1, and described perisporium (45b, 146, T) is made of following part: the gear perisporium (45b) that the three the key element gear (40) in described three key element gears has, the secondary gear perisporium (146) that the 3rd secondary key element gear (140) in described three secondary key element gears has; The periphery wall (T) that shares that a described gear ratio control unit (C1) and described secondary gear ratio control unit (C2) have.

the invention of technological scheme 3 is in the described automatic transmission of technological scheme 2, 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 rotating restriction overrunning clutch (180), this secondary rotating limits with the rotation of the second secondary key element gear (150) in described three the secondary key element gears of overrunning clutch prevention to a direction, described periphery wall (T) is for described once rotation restriction overrunning clutch (80) and the described secondary rotating restriction shared outside body component (T) of overrunning clutch (180).

the invention of technological scheme 4 is in the described automatic transmission of any one 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 the described automatic transmission of technological scheme 4, and described secondary output solid of rotation (175) is 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 a 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 due to 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 a gear chamber that is formed in 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 the dual-layer wall that is formed by sidewall and gear sidewall with covered by the dual-layer wall that secondary sidewall and secondary gear sidewall form, therefore, not only has the reducing noise effect based on perisporium, and, double-wall structure due to the sidewall on axial, 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, secondary gear perisporium, also by once, the component parts that shares of secondary gear ratio control unit is that periphery wall consists of, therefore, due to 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 outside body component that shared of secondary overrunning clutch consists of, therefore, due to 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, secondary clutch once, the secondary push part consists of 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 reducing 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 diagram 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 ... the thrust receiving 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 is taken out in output, 95 ... 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 vehicle automatic transmission, this automatic transmission M and consist of together the power plant that are loaded in as on the two-wheeled motor vehicle of vehicle 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 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 vertical direction.

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

In addition, the gear ratio of speed changer is 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 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 to the air inlet system 8 on 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 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 the burning because of the mixed gas in firing chamber 7 produces, moves back and forth, and the rotary actuation 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 has.) input to speed changer M.And, take out from the output of speed changer M the power that axle 91 is removed, via consisting of the chain 97b that drives with driving mechanism 97, be that trailing wheel 98 drives to the driving wheel as driven object.

The throttle valve 8a that air inlet system 8 has is that air inflow is controlled to the flow of the combustion air that is inhaled into firing chamber 7; Form the Fuelinjection nozzle 9 of mechanism as mixed gas, for the air fuel ratio of controlling mixed gas, the delivery volume that is ejected into the fuel in combustion air is controlled; Ignition mechanism 10 with spark plug 10a is controlled igniting opportunity.

Throttle valve 8a, Fuelinjection nozzle 9 and ignition mechanism 10 are controlled by the control gear 13 that internal-combustion engine E has respectively, it is the output control mechanism that to control according to the output of the working state combustion motor E of the operating condition of internal-combustion engine E and speed changer M, and, or the control of the output by internal-combustion engine E is to 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.

The state detection mechanism that the working state of the operating condition of combustion motor E and speed changer M of having control gear 13 detects and for the 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, its endurance to the semi-connection state that detects by the clutch coupled condition 13b of feeler mechanism is detected.

The clutch coupled condition 13b of feeler mechanism is by comparing to detect above-mentioned half connection state to 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 detect by rotational speed feeler mechanism.For example, when at least one party in two clutches 70,170 is skidded, because above-mentioned actual gear ratio becomes less than above-mentioned setting gear ratio, therefore, the clutch coupled condition 13b of 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 in the endurance that detects by the time detecting 13c of 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.Control by this, input rotational speed Ni is changed in the mode that increases or reduce, and being transitioned into 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 respectively a pair of cover 3c of section, 3d on each case halfbody 3a, 3b by a plurality of bolts.Bent axle 6 is bearing on a pair of case halfbody 3a, 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 in the 15a of this crankshaft room as the bent axle 6 that drives running shaft; Gearbox chamber 15b disposes speed changer M in this gearbox chamber 15b.In this embodiment, gearbox case 16 is so that the mode that the 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 cover 3d of section in the bottom of containing room 15.In addition, as other example, gearbox case 16 also can be so that the 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 rotation of bent axle 6 to the start clutch of transmission and the blocking-up of speed changer M.Centrifugal clutch 17 has governor weight 17a, and the coupled condition of centrifugal clutch 17 is controlled in the variation of this governor weight 17a and internal-combustion engine rotational speed servo-actuatedly.

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 consists of by the actuation gear 18a of the rotation of transmitting centrifugal clutch 17 with the driven gear 18b of input shaft 20 one rotations, be centrifugal clutch 17 with the rotation input speed changer M of the bent axle 6 that passes over via the input side clutch, 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 the bent axle 6 via driven gear 18b by internal-combustion engine E is driven in rotation; 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 the 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, are for example that non-rotary parts are the fixed side parts.

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

The first input shaft 21 is by on the chimeric periphery that is attached at the 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 second large wide diameter portion of input shaft 22 diameters in input shaft 20.

A shaft end 23b of output shaft 23 is bearing on case halfbody 3b in the mode that can rotate via bearing B3, and near the part another shaft end 23a is bearing on gearbox case 16 in the mode that can rotate via bearing B4 and the second input shaft 22.With input shaft 20 arranged coaxial and have the output shaft 23 of the rotation centerline L2 consistent with the rotation centerline L1 of this input shaft 20, connect in the axial direction variable-speed unit U, input shaft 20 and shell 16 and extend in the 15a of crankshaft room.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 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 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 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 is configuring between lateral body 25b outside lateral body 25a and clutch in clutch diametrically with making progress devices spaced apart week.In addition, in other example, the outer lateral body 25b of clutch can also be made of the miscellaneous part different from shaft end 21a and be located on this shaft end 21a, and in clutch, lateral body 25a also can itself be made of shaft end 23a.

When the rotational speed No of output shaft 23 surpasses input rotational speed Ni, in clutch element 25c and 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; For input rotational speed Ni when following, in clutch element 25c and clutch, the outer lateral body 25b of lateral body 25a and clutch becomes non-fastening state at output rotational speed No, 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, establishing speed changer M in the situation that i.e. gear ratio R1 beyond the 4 fast gear ratio R4～R3 (with reference to Fig. 6) of the minimum gear ratio under direct connecting state described later, power combustion motor E by the trailing wheel that only do not transmit via output shaft 23 via variable-speed unit U drives, 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 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 be near near in the axial direction arranged sequentially with variable-speed unit M1 and variable-speed unit M2 from (or shaft end 23a of output shaft 23) reducing gear 18 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, namely central gear 30,130, support a plurality of planetary pinions 41,141 planetary carrier 40,140 and ring gear 50,150 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 consist of 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 the second input shaft 22 by spline is chimeric; Edge part 52, it is as being 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 section 53 with tooth section 42 engagements of each planetary pinion 41 on interior week; As a gear sidewall 54 of discoid annular wall, it extends diametrically, is connected with inboard axial region 51 and is connected with edge part 52 in outer periphery at inner circumference edge.In planetary gears P1, ring gear 50 is input gears that the rotation of input shaft 20 is inputted, and this ring gear 50 is the first key element gears in three key element gears in 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.The first row gear rack 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 are connected and are bearing on output shaft 23 in the mode that can rotate via the central gear 130 of inboard axial region 51 and secondary planetary gears P2.The 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 are connected.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 in planetary gears P1.

The inboard axial region 44b of planetary carrier 40 inputs to the rotation of input shaft 20 via variable-speed unit M1 the once output solid of rotation of planetary gears P2.Outside axial region 45b has fixed wall 45c in the axial direction on a near end 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 section of being supported on another end, this is supported that the 45d of section is provided with in the axial direction across the first limiting part 61 and a pair of thrust-bearing B5 that configures.Therefore, by the first limiting part 61, planetary carrier 40 with respect to output shaft 23 and gearbox case 16 axially on movement be prevented from.

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

These teeth section 32,42,53 of planetary gears P1, in planetary gears P1, be three key element gears intermeshing, that is to say time key element gear one to one be each planetary pinion 41 of planetary carrier 40 with ring gear 50 intermeshing and in addition one to one time key element gear be each planetary pinion 41 and the intermeshing engaging piece H1 of central gear 30 of planetary carrier 40.

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 secondary gear sidewall 133, and it extends diametrically, is connected with inboard axial region 131 and is connected 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 output shaft 23 via bearing B7, be provided with the tooth 131a of section with the tooth 142a of section of each planetary pinion 141 engagement.

Inboard axial region 131 has: elastic pressing part 134, and it extends in the axial direction at the radially inner side of the inboard axial region 44b of the planetary carrier 40 inboard axial region 51 to the ring gear 50 of planetary gears P1; Block 135, it stops the movement to the right of central gear 130 in the axial direction, inboard axial region 131 on this elastic pressing part 134 by spline chimeric being attached on inboard axial region 44b.Move to the right at central gear 130, when elastic pressing part 134 suppresses push part 75 described later, 175 to the right, block 135 in the axial direction with inboard axial region 44b butt, thus, stop central gear 130 movement to the right, the amount of movement of the central gear 130 on axial is 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 in 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 is connected 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 in planetary gears P2.

Outside axial region 146 is with the rotation speed change of inboard axial region 44b and export it to output shaft 23, and this outside axial region 146 is the whole output shafts in speed changer the M whole planetary gears P 1, the P2 that have.In addition, outside axial region 146 has fixed wall 146c on the end of that side near 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 section of being supported on the end of opposite side, this is supported that the 146d of section is provided with in the axial direction across the second limiting part 62 and a pair of thrust-bearing B8 that configures.Therefore, by the second limiting part 62, the axial movement with respect to output shaft 23 and gearbox case 16 of planetary carrier 140 is prevented from.

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

Each planetary pinion 141 is made of the first gear 142 and the second gear 143, wherein, the first gear 142 has the first tooth 142a of section with the tooth 131a of section of central gear 130 engagement, the second gear 143 to the first gear 142 diameters are large, and have the second tooth 143a of section with the tooth 151a of section 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 large 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 the footpath makes progress.

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

Therefore, at the torsional interaction of formed objects in the situation that on planetary pinion 41 and 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 large.

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

These teeth 131a of section 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 and the intermeshing secondary engaging piece of central gear 130 H2 that each planetary pinion 141 that a pair of secondary key element gear is planetary carrier 140 and the intermeshing and other a pair of secondary key element gear of ring gear 150 are planetary carrier 140.

And, from axially observing, two gear sidewalls 54,133 comprise once, secondary engaging piece H1, H2 whole or roughly form in whole radial extension.

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

And each limit material parts 61,62 have: the cylinder 61a of section, the 62a that extend in the axial direction; The forward end of the cylinder 61a of section, 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 cylinder 61a of section, 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 the state of these support unit 65 combinations under, be mounted by means of bolts on a plurality of assembly department 16a (with reference to Fig. 1), these a plurality of assembly department 16a are arranging on gearbox case 16 with making progress devices spaced apart week.

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

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

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 that once transmits 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 inputted rotational speed Ni less low speed rotation territory and become the connection finishing stage becoming with clutch 170 the High Rotation Speed territory that is connected finishing stage with secondary speed change described later, this clutch 70 is centrifugal friction clutches, have: as lateral body 71 in a clutch of input block, its input is had rotation from input shaft 20, and in this clutch, lateral body 71 is that edge part 52 consists of by the part of ring gear 50; 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 clutch, to be combined with the mode of planetary carrier 40 one rotations; Once control device is transmitted in rotation, it comprise diametrically with can the phase mutual connection from the mode interaction cascading be configured in clutch a more than one input side clutch plate 73 and the more than one outlet side clutch plate 74 between lateral body 72 outside 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 arranges as follows: by the spline on the periphery of lateral body in clutch 71 chimeric and with clutch in lateral body 71 one rotations and can moving in the axial direction, outlet side clutch plate 74 arranges 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 movement to the right is restricted.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 ring gear 50 is inboard axial region 51 over edge part 52 until outside clutch in the radial extension of lateral body 72, in the axial direction from right side cover ring generating gear 50 and clutch plate 73, a sidewall of 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 wall section, 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: the secondary speed change clutch 170 that transmits control mechanism as secondary, it is according to input rotational speed Ni, more particularly according to by variable-speed unit M1, the rotational speed that input rotational speed Ni has carried out the inboard axial region 44b that speed change obtains namely once being exported rotational speed Na, to central gear 130 not via planetary pinion 140 direct transmission and the blocking-up to the rotation of planetary carrier 140 control, secondary rotating restriction overrunning clutch 180 as the secondary rotating limiting part, 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 secondary clutch 170 becomes the connection finishing stage in the High Rotation Speed 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 namely outside axial region 132 consist of; 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 clutch, to be combined with the mode of planetary carrier 140 one rotations; Secondary rotating transmits control device, it comprise diametrically with can the phase mutual connection from the mode interaction cascading be configured in clutch more than one secondary input side clutch plate 173 and the more than one secondary outlet side clutch plate 174 between lateral body 172 outside 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 arranges as follows: by the spline on the periphery of lateral body in clutch 171 chimeric and with clutch in lateral body 171 one rotations and can moving in the axial direction, outlet side clutch plate 174 arranges 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.

Two clutches 70,170 clutch plate 73,74,173,174 are 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 movement to the left is restricted.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 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 is to be that spline 175a begins to surpass outside axial region 132 until clutch outside in the radial extension of lateral body 172, in the axial direction from left side covering central gear 130 and clutch plate 173,174 secondary sidewall from the linking department with output shaft 23.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 wall section, 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 periphery in the mode that can move by sliding in the axial direction; Block 72b, 172b during non-expanding, its during to inoperative the governor weight 76,176 idle position of (during non-expanding) limit; Block 72c, 172c when expanding, its maximum when at utmost expanding expands the position and (is represented by double dot dash line in Fig. 2, Fig. 3.) limit.

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

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

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

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 over axial force F 1a, F2a big or small because of the increase of centrifugal force, each governor weight 76,176 is connected at fulcrum 76a, 176a and swings centered by this fulcrum 76a, 176a under state on carrier 47,147 and expand, 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, push part 75,175 and the outer lateral body 72,172 of clutch together move in the axial direction, make each clutch plate 73,74,173,174 fixed wall 45c, the 146c that are located on outside axial region 45b, 146 towards one push in the axial direction and be in contact with one another, due to the clutch plate 73 that is in contact with one another, the friction of 74,173,174, the rotation of ring gear 50 or central gear 130 is passed to the outer lateral body 72 of clutch, 172 and planetary carrier 40,140 via each clutch plate 73,74,173,174.

In addition, in the situation that outside clutch, lateral body 72,172 rotates with 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 larger 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 large structure of the quality settings of each governor weight 176 in the present embodiment.Specifically, two governor weights 76,176 quality are 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 larger than a pushing force F1c that secondary pushing force F2c becomes, mobile push part 175 makes and clutch 70 is placed in the push part 75 that connects finishing stage moves to the right 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: set fulcrum 176a and the distance between elastic pressing part 176d of governor weight 176 less than fulcrum 76a and the distance between elastic pressing part 76d of governor weight 76, may be used in addition these counterweight structures.

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 and expands the position, each clutch 70,170 is in that clutch plate 73,74,173,174 do not produce slidably, lateral body 71 in clutch, 171 and the outer lateral body 72,172 of clutch (and then ring gear 50 and planetary carrier 40, or central gear 130 is connected with planetary carrier) with the connection finishing stage of constant speed rotation; When the governor weight 76 that expands, 176 expands between the position and occupies when the clutch plate 73 that is in contact with one another, 74,173,174 produce the neutral position of sliding in described idle position and described maximum, each clutch 70,170 is in being rotated in of lateral body 71,171 (and then ring gear 50 or central gear 130) in clutch and follows 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 clutch plate 73, the state of slip of 74,173,174.

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

Intermediate transfer parts 36 have: the first intermediate transfer parts 37 of tubulose, and it can be connected on 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 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 the elastic member of controlling with suppressing parts be spring members 39a.Elastic member is that described spring members 39a is made of one or more for example four belleville spring 39b in the present embodiment.Butt the first intermediate transfer parts 37 on an end that is consisted of by pars contractilis 39 of the second intermediate transfer parts 38, the inboard axial region 51 of abutment ring generating gear 50 on another end that is consisted of 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 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.

Under the state that be connected on the second intermediate transfer parts 38 at the first intermediate transfer parts 37 that suppressed by elastic pressing part 134, the movement to the left of these the second intermediate transfer parts 38 is prevented from, 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, increase due to 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, accompany everywhere with the movement to the right of push part 175, 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 inboard axial region 51.At this moment, the pushing force F2c that 176 pairs of push part 175 of governor weight apply is larger than the pushing force F1c that 76 pairs of push part 75 of governor weight apply, therefore, due to described driving force, planetary carrier 40 and push part 75 are pushed and move to the right by elastic pressing part 134 via first, second intermediate transfer parts 37,38.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 at clutch 70 and after temporarily becoming notconnect state, 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 again, 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 to input rotational speed Ni that governor weight 76 expands is again 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 rotation side engagement portion, it is bearing on the supporting axle 89,189 of being located on annulus 33,152 in the mode that can swing, and is here as a plurality of two groups 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 engaging 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 to each ratchet pawl 81,82,181,182 directions that engage with claw 83,183.Spring 84; 184 are located at respectively annulus 33 being inserted through; 152 and ratchet pawl 81,82; 181, after in engaging 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 two overrunning clutchs 80, the 180 single tubular parts that share, the space S 1 of this outside body component T formation ring-type diametrically and between inboard axial region 44b.Outside body component T is supported on gearbox case 16 by being located in one piece the upper and support unit 65 from the periphery of outside body component T to the radial outside extension of this outside body component T.Support unit 65 is mounted by means of bolts on the assembly department 16a (with reference to Fig. 1) of gearbox case 16.

Ratchet pawl 81,82; 181,182 have: with claw 83; Engagement portion 81a, the 82al of 183 engagings; 81a, 182a; And counterweight part 81b, 82b; 181b, 182b.By acting on counterweight part 81b, 82b; Centrifugal force on 181b, 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 (represented by double dot dash line in Fig. 4.), this non-contacting position is engagement portion 81a, 82a; 181a, 182a not with claw 83; The position of 183 engaging portion 85a, 185a engaging.This non-contacting position is by the 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 engaging portion 85a; The main part 85 of 185a; 185; Sense of rotation towards the rotation that allows central gear 30 or ring gear 150 is the rake 86 that opposite direction A2 slowly gives prominence to diametrically; 186.When ratchet pawl 81,82; 181,182 not with engaging portion 85a; 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 engaging portion 85a by sintering; The rubber material as elastic material on 185a forms, therefore, and this rake 86; 186 consist of 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 ground configuration of L2 point symmetry, a pair of ratchet pawl 82 in addition; 182 with respect to rotation centerline L1, the ground configuration of L2 point symmetry, and is configured to: when occupying each ratchet pawl 81,82; 181,182 and engaging portion 85a; During the clamped position of 185a engaging, a pair of ratchet pawl 82 in addition; 182 occupy not and engaging portion 85a; 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 during to a direction A1 rotation with engaging portion 85a; The chance of the engaging of 185a can become rapidly the rotation stopping state.

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 a gear chamber 19, and this gear chamber 19 is made of following part: 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 the 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 consists of as the outside body component T of periphery wall.This gear chamber 19 is formed in the space in gearbox case 16.

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

In addition, in two outside axial region 45b, 146, across two outside axial region 45b, 146 and configure 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 namely is supported the 45d of section, 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, the 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 consist of partly on described perisporium dual-layer wall is arranged, thus, can improve the reduction effect of noise that results from engagement to two engaging piece H1, H2 place, the width of the described perisporium on can reducing axially can configure 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 have is taken out axle 91 and is rotated driving.Driving mechanism 90 also has except axle 91 is taken out in output: as the output gear 92 that drives solid of rotation, this output gear 92 extends on 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 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 axle 91, by driven with the engagement of output gear 92; Neutral gear clutch 95, its rotating photo with output gear 92 takes out axle 91 for output and transmits and block.

The integral body that axle 91 is taken out in output from end on observation be configured in variable-speed unit M2 overlapping position 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 extends axial region 93a; Connect case halfbody 3b and extend axial region 93b to the outside of the 15a of crankshaft room extension.Externally extend axial region 93b and be provided with driving sprocket wheel 97a as whole carry-out part, be wound with chain 97b on this driving sprocket wheel 97a.

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

Output gear 92 and driven gear 93 consist of 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 extends on axial region 93a, and is configured in predetermined range W.Neutral gear clutch 95 has: selector 95a, and it is chimeric and take out axle 91 one rotations and can be fastened on driven gear 93 with output by spline; Selector fork 95b, it operates and can drive selector 95a by clutch operating parts (not shown) it is moved in the axial direction.

During activation point in can mobile in the axial direction selector 95a occupies Fig. 2 on extending axial region 93a shown in solid line, make the rotation of transmitting via driven gear 93 from output gear 92 input to output taking-up axle 91, and be rotated with following rotational speed, this rotational speed is that the rotational speed that axle 91 has obtained to have been carried out adjusting than the rotational speed No to output shaft 23 by the speed of driving mechanism 90 settings is taken out in output.In addition, when selector 95a occupies in Fig. 2 the neutral position shown in 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 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, 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 the 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 the 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 carried out the rotational speed that deceleration obtains based on the gear ratio r2 pair of rotational speed with the central gear 130 of planetary carrier 40 constant speed rotations of planetary gears P1 of planetary gears P2, in clutch 170, by based on the 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, 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 namely 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 than large the second fixing speed N2 of this first fixing speed N1 when following, in variable-speed unit M1, increase due to 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 governor weight 76, governor weight 76 expands.And governor weight 76 occupies described maximum and expands the position, and push part 75 is so that ring gear 50 moves to the left and mode 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, namely 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, although the rotational speed of planetary carrier 140 increases, the pushing force F2c that acts on the centrifugal force on governor weight 176 due to basis is below axial force F 2a, so governor weight 176 occupies described idle position.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 than large the 3rd fixing speed N3 of this second fixing speed N2 when following at input rotational speed Ni, in secondary variable-speed unit M2, increase due to 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 governor weight 176, governor weight 176 expands.And governor weight 176 occupies described maximum and expands the position, and push part 175 is so that central gear 130 moves to the right and mode 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 namely 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, namely 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 at clutch 170 process that connects finishing stage, 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 via ring gear 50, the push part 75 of clutch 70 is moved to the right, 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 expands the position from described maximum and moves to described idle position, 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 before this is rotated.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 thus the movement to the right of push part 175 and central gear 130.

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: during from 2 fast gear ratio R2 to 3 fast gear ratio R3 transition, detecting two clutches 70 by the clutch coupled condition 13b of feeler mechanism, 170 at least one party become semi-connection state, and detect time that this semi-connection state continues when exceeding schedule time by the time detecting 13c of mechanism, be throttle valve 8a by the rotational speed control mechanism, at least one in Fuelinjection nozzle 9 and ignition mechanism 10, 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 be transitioned into 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 rapidly the semi-connection state of clutch 70 or clutch 170, the transition of acceleration from 2 fast gear ratio R2 to 3 fast gear ratio R3.

On the contrary, during from 3 fast gear ratio R3 to 2 fast gear ratio R2 transition, the described rotational speed control mechanism that control gear 13 is controlled, become in order to be transitioned into the clutch 70 that is in semi-connection state the input rotational speed Ni that the clutch 170 that connects finishing stage or be in semi-connection state becomes notconnect 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, during from 3 fast gear ratio R3 to 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 in order to be transitioned into clutch 70 the input rotational speed Ni that connects finishing stage, 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, during from 4 fast gear ratio R4 to 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 be transitioned into clutch 70, change this input rotational speed Ni by described rotational speed control mechanism so that input the mode of rotational speed Ni minimizing.

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

On the other hand, in variable-speed unit M1, be urged under the state that power F2c suppresses to the right at first, second intermediate transfer parts 37,38, be the push part 75 that suppress on the right side by the spring force of spring members 39a to connecting the releasing direction, due to the increase of the rotational speed of input rotational speed Ni corresponding planetary carrier 40, in clutch 70, pushing force F1c surpasses the spring force of spring members 39a, and governor weight 76 expands.And governor weight 76 occupies described maximum and expands the position, and push part 75 is so that ring gear 50 moves to the left and mode 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 namely variable-speed unit M1 becomes direct connecting state.

And because two gear ratio r1, r2 based on two variable-speed unit M1, M2 become 1, 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, to effect and the effect of the mode of execution of formation describe as described above.

in speed changer M, the engaging piece H1 of planetary gears P1 and the engaging piece H2 of planetary gears P2 are housed in a 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 (namely, two push part 75 in the axial direction, two planetary carriers 40 of the perisporium that 175 inboard) 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 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 engaging piece H2, 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, consist of dual-layer wall in the radial extension of H2.

By this structure, due to have once, secondary planetary gears P1, P2 and once, secondary clutch 70,170 once, secondary variable-speed unit M1, M2 be housed in a shared gear chamber 19, therefore, the component parts sharing of two variable-speed unit M1, M2 can be realized, the cost cutting based on the reduction of number of spare parts can be realized.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 a gear chamber 19 that is formed in 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 reducing noise effect of outside body component T, and, double-wall structure due to the sidewall on axial, 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 have i.e. outside body component T consist of, thus, utilize two variable-speed unit M1, the component parts of M2 and the described perisporium of the gear chamber 19 that forms, except 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 the component parts that shares are that outside body component T consists of, therefore, by two variable-speed unit M1, two overrunning clutchs 80 that M2 has, 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, the 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 consist of, thus, owing to can utilizing two clutches 70, 170 two push part 75, wall outside the double walled of 175 formation gear chamber 19, therefore, needn't make in order to reduce noise planetary gears P1, the ring gear 40 of P2, central gear 130 grades once, secondary key element gear maximizes diametrically, can reduce and result from two engaging piece H1, the noise of the engagement of H2.

The secondary output solid of rotation that will input to the rotation that obtains based on the gear ratio R of variable-speed unit M1, M2 output shaft 23 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 to the effect of output shaft 23 transmission, therefore, can cut down number of spare parts.

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

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 gearbox case 16, therefore, in planetary gears P1, P2, utilization is fixed the external lateral body parts T of limiting part 60 that central gear 30 and ring gear 150 movement in the axial direction limit, therefore, do not need the support unit for the special use of supporting outside body component T, the reduction of number of spare parts becomes possibility.

in 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, has a thrust receiving portion 46 that mutually pushes the other way around in the axial direction, this thrust receiving portion 46 is configured between the pushing section 153 of the pushing section 34 of central gear 30 and planetary carrier 140 in the axial direction, thus, has planetary gears P1, the variable-speed unit M1 of P2, in M2, stop with 46 pairs of central gears 30 of a thrust receiving portion and the moving axially of planetary carrier 140 that shares, on described central gear 30 and 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 receiving portion 46 realizes sharing, can realize the cost cutting based on the number of spare parts reduction.

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

ring-shaped member is that thrust receiving portion 46 only is located on the inboard axial region 44b of planetary carrier 40, central gear 30 and planetary carrier 140 are configured in respectively the both sides of thrust receiving portion 46 in the axial direction, thus, owing to only utilizing as the inboard axial region 44b that once exports solid of rotation, thrust receiving portion 46 is set, 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, in order to support thrust receiving portion 46, need not the parts except inboard axial region 44b, can cut down number of spare parts, can make the designs simplification of speed changer M in addition.

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

Thrust receiving portion 46 is configured in space S 1, this space S 1 is to be surrounded by the overrunning clutch 80 that the rotation on a direction A1 of central gear 30 and planetary carrier 140 is stoped, 180 outside body component T, thus, thrust receiving portion 46 is configured by the space S 1 that the overrunning clutch 80 that limits by the sense of rotation to central gear 30 and planetary carrier 140,180 outside body component T form, 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 the support lug 61b that limits of the movement of two directions and to planetary carrier 140 axially on the support lug 62b that limits of the movement of two directions, thus, has planetary gears P1, P2 and gear ratio control unit C1, the variable-speed unit M1 of C2, in M2, due to the 60 couples of planetary gears P1 of limiting part by sharing, two planetary carriers 40 of P2, 140 move axially limits, therefore, with respect to planetary gears P1, P2, limiting part 60 is realized sharing, the cost cutting of cutting down based on number of spare parts becomes possibility.

In addition, due to 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 two planetary carriers 40 that limit, 140 configuration by 60 pairs of limiting parts.

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

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

Limiting part 60 together is arranged on gearbox case 16 with the support unit 65 that overrunning clutch 80,180 outside body component T are supported, 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 has has: the clutch coupled condition 13b of feeler mechanism, and the situation that its at least one party to clutch 70 and clutch 170 is in semi-connection state detects, the 13c of time detecting mechanism, its endurance to the semi-connection state that detects by the clutch coupled condition 13b of feeler mechanism is detected, control gear 13 is controlled as follows: when the endurance that detects by the time detecting 13c of mechanism exceeds schedule time, in order to change input rotational speed Ni and to make it be transitioned into the rotational speed of removing semi-connection state, and the described rotational speed control mechanism of control inputs rotational speed Ni is controlled, thus, at two clutches 70, at least one party in 170 continues semi-connection state during the stipulated time, this rotational speed control mechanism of controlling 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 in early days the clutch plate 73 under semi-connection state, 74, 173, 174 each other sliding modes.Consequently, can suppress clutch plate 73,74,173,174 wearing and tearing, can improve centrifugal clutch 70,170 durability, in addition, drive sense thereby travelling becomes well can promote.

The process that makes clutch 170 from notconnect state to the transition of connection finishing stage, governor weight 176 makes clutch 70 from connecting finishing stage to the notconnect state transition, thus, can remove in early days clutch 170 from semi-connection state from notconnect state to the way that connects the finishing stage transition and clutch 70 from connecting the semi-connection state of finishing stage to the way of notconnect state transition, therefore, can improve each clutch 70,170 durability, 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 with the speed changer that is in the clutch 70 that is connected finishing stage and can become notconnect state when input rotational speed Ni increases, can obtain by quantity planetary gears still less the quantity of the gear ratio of being established by speed changer M.

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 each clutch 70,170 semi-connection state gear ratio by reality, therefore, can improve for the control accuracy of removing semi-connection state.

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

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 semi-connection state is larger (or comparatively hour), make the judgement that is in the transition of shift-up direction (or downshift direction), by to throttle valve 8a, at least one in Fuelinjection nozzle 9 or ignition mechanism 10 controlled, can be to air inflow, at least one in fuel feed and igniting opportunity controlled, make the internal-combustion engine rotational speed increase (or minimizing) until clutch 70 or clutch 170 break away from semi-connection state.

in speed changer M, gear ratio control unit C1, C2 has overrunning clutch 80, 180, has overrunning clutch 25 between the input shaft 20 on the rotation bang path and output shaft 23, 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, output shaft 23 be rotated in planetary gears P1, shunt in P2, and be 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 in or 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, be provided with the wide diameter portion to axially open on the shaft end 21a of input shaft 20, overrunning clutch 25 is configured in the radially inner side of this wide diameter portion, thus, be located at due to overrunning clutch 25 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 axial region 27, being located at output takes out on axle 91 and is output the driven gear 93 that gear 92 drives, the rotating photo of output gear 92 is taken out for output the neutral gear clutch 95 that axle 91 transmits and blocks, the integral body that axle 91 is taken out in output from end on observation be configured in variable-speed unit M2 overlapping position on, neutral gear clutch 95 is configured in 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 take out axle 91 configurations diametrically on the position near output shaft 23 with being configured in from end on observation with the overlapping locational output of variable-speed unit M2, in addition, due to can be with neutral gear clutch 95 diametrically near output shaft 23 ground configurations, therefore, can make the outlet side driving mechanism 90 with output taking-up axle 91 and neutral gear clutch 95 diametrically near output shaft 23 ground compact arrangement, can make speed changer M miniaturization diametrically.

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 the secondary overrunning clutch 180 that ring gear 150 is stoped to the rotation of a direction, two overrunning clutchs 80, 180 have the outside body component T of the rotation restricting unit that the conduct between the secondary engaging piece H2 of engaging piece H1 being configured in the axial direction a planetary gears P1 and secondary planetary gears P2 shares.

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, in M2, once, secondary overrunning clutch 80, 180 have the formation of utilization in the axial direction once, secondary engaging piece H1, space between H2 and the outside body component T that shares that configures, 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 configures in the axial direction compactly, therefore, the neutral gear clutch 95 that is configured in described predetermined range W can be configured 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 just a part of structure of aforesaid mode of execution is changed 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 to the applicable the present invention of at least two variable-speed unit M1, M2.

The main shaft of speed changer can be 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 consist of by the pressure type actuator or the electromagnetic actuator that utilize hydraulic pressure etc. the driver part that each push part 75,175 is driven.

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, due to when two clutches 70,170 at least one party slide, the temperature of lubricant oil rises, therefore, the temperature of the lubricant oil that detects according to the temperature transducer that has by control gear 13, when the temperature of lubricant oil during higher than set point of temperature, or when the climbing of the temperature of lubricant oil is larger than specified value, the clutch coupled condition 13b of feeler mechanism detects each clutch 70,170 semi-connection state.And, in this case, because the temperature transducer that can utilize the temperature that detects lubricant oil detects each clutch 70,170 semi-connection state, therefore, can realize the cost cutting of cutting down based on number of spare parts.

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

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

Claims (5)

1. automatic transmission has:

Input shaft by prime mover rotary actuation;

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 inputted 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,

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

The secondary sidewall that sidewall that described the first side wall and described the second sidewall are had by a described gear ratio control unit respectively and secondary gear ratio control unit have consists of,

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

A described sidewall and a described gear sidewall and described secondary sidewall and described secondary gear sidewall consist of 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 made of following part: the gear perisporium that the three key element gear in described three key element gears has; The secondary gear perisporium that the 3rd secondary key element gear in described three secondary key element gears has; The periphery wall that shares that a described gear ratio control unit and described secondary gear ratio control unit have.

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 with the rotation of the second key element gears in described three key element gears of overrunning clutch prevention to a direction,

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

Described periphery wall is to limit for described once rotation restriction overrunning clutch and described secondary rotating the outside body component that shares with overrunning clutch.

4. automatic transmission as described in any one of claim 1～3 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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