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    • 专利摘要:
    [Document Name] Abstract It is an object of the present invention to provide a planetary gear type gearbox forallowing a multi-stage gear train to keep a simple structure by inhibiting passage torqueWithout increasing the size of gears to be disposed in a rear stage or adding an extracomponent such as a speedup gear. An input-side transmission (10) is a transmissionsection for transmitting power from an input shaft (ll) to an interrnediate shaft (21). Theinput-side transmission (10) includes L, M and I-I clutches (12a-12c), two sets of M and Hplanetary gear trains (13, 14) axially adjoining to each other. The M planetary gear train(13) includes a sun gear (Ba), a carrier (1312), a ring gear (13c) and planet gears (13e).The H pianetary gear train (14) includes a sun gear (14a), a carrier (Mb), a ring gear (14c)and two sets of planetary gears (14e1) and planetary gears (14e2). In the activation of Mand H clutches (12b, 12c), power is inputted into the carrier (13b) from the input shaft (11) and is then outputted from the ring gear (13c).
    公开号:SE1050004A1
    申请号:SE1050004
    申请日:2008-08-27
    公开日:2010-02-25
    发明作者:Masaki Shiohara
    申请人:Komatsu Mfg Co Ltd；
    IPC主号:
    专利说明:

    [1] [0001] The present invention relates to a planetary gear type gearbox, for instance, to beinstalled in a dump truck.
    [2] [0002] A transmission, including a plurality of planetary gear trains, has been recentlyinstalled in the construction vehicles such the dump trucks. In the gearbox, engine torqueis inputted into an input shaft and a plurality of speed stages are shifted back and forthdepending on objects of driving a vehicle.
    [3] [0003] For example, patent document 1 discloses a gearbox in Which not only clutchesand brakes but also a torque converter and two sets of planetary gear trains are combined.According to the gearbox, a Wide range of speed reduction can be realized by setting theinter-stage ratios to be roughly the same. Note the inter-stage ratio is a ratio betweenspeed change ratios of speed-change stages.
    [4] [0004] The aforernentioned conventional gearbox has the following dravvback.
    [5] [0005] In short, the gearbox, disclosed in the aforementioned patent document, has adrawback that a reduction ratio of a speed unit always exceeds For example, asillustrated in FIG2 of the aforementioned patent document, the reduction ratio is set to be:l.00 in .engagement of a clutch 28 (L clutch); 1.35 in engagement of a brake 24 (M c1utch);and 1.84 in engagernent of a brake 26 (H clutch).
    [6] [0006] With the configuration, large torque is transmitted to the rear stage of the gearbox.In response to this, a variety of counterrneasures are required. For example, torque isrequired to be inhibited by installing a speedup gear in the front-stage side of the gearsdisposed in the rear stage. Alternativeiy, the gears to be disposed in the rear stage arerequired to be formed in a large size in consideration of their durability.
    [7] [0007] It is an object of the present invention to provide a planetary gear type gearbox forallowing a multi-stage gear train to keep a simple structure by inhibiting output-side torquewithout addition of an extra component such as a speedup gear or size increase of the gears to be disposed in the rear stage.
    [8] [0008] A planetary gear type gearbox according to a first aspect of the present inventionincludes a front-stage transmission section and a rear-stage transmission section. Thefront-stage transmission section includes an input shaft that power is inputted thereto.The rear-stage transmission section includes an iriterrnediate shaft coupled to thefiont-stage transmission section and an output shaft for outputting power. The front-stagetransmission section includes a first planetary gear train, a second planetary gear train, afirst ciutch, a second clutch and a third clutch. The first pianetary gear train is composedof a first sun gear, a plurality of first planet gears, a first carrier and a first ring gear. Thefirst planet gears mesh With the first sun gear. The first carrier is coupled to the inputshaft, and rotatably supports the first planet gears. The first ring gear is connected to theinterrnediate shaft, and rneshes with the first planet gears. The second planetary gear trainis cornposed of a second sun gear, a plurality of inner peripheral side second planet gears, aplurality of outer peripheral side second planet gears, a second carrier and a second ringgear. The second sun gear is integrally and rotatably coupled to the first sun gear. Theinner peripheral side second planet gears mesh With the second sun gear. The outerperipheral side second pianet gears rnesh with the inner peripheral side second planet gears.The second carrier is connected to the input shaft, and rotatably supports the innerperipheral side second planet gears and the outer peripheral side second planet gears. Thesecond ring gear rneshes with the outer peripheral side second planet gears. The firstclutch is confignred to couple/uncouple the input shaft and the interrnediate shaft. Thesecond clutch is configured to allow/prevent rotation of the second sun gear. The thirdclutch is configured to allow/prevent rotation of the second ring gear.
    [9] [0009] The planetary gear type gearbox is installed in the construction vehicles and thelike (e.g., dump trucks), for instance. The pianetary gear type gearbox includes the firstand second planetary gear trains and the first to third clntches for shifting threespeed-change stages back and forth The second planetary gear train is so-called a doublepianetary type planetary gear train. Additionally, according to the planetary gear typegearbox, power transrnissions of the first and second planetary gear trains have aconfiguration that power is inputted into the first carrier and is outputted from the first ringgear in a speed-change stage in Which a reduction ratio is gradually reduced.
    [10] [0010] According to the configuration, the reduction ratios in the three stages can be all set to be equai to or less than 1.000 by configuring power to be inputted into the carrier and 2 to be outputted from the ring gear in the first planetary gear train. [001 l] As a result, it is possible to cornpactly forrn the gears and the like on the rear-stageside Without increasing their sizes just like the conventional gearboxes that the reductionratios in three speed-change stages are all equal to or greater than 1.000. Furthermore,With the adoption of the aforementioned structure, it is possible to appropriately set thereduction ratios of three speed-change stages so that the inter-stage ratios among threespeed-change stages can be roughly the same. As a result, it is possible to compactlyfonn a multi-stage gearbox for providing nine forward stages and three reverse stages, forinstance, hy disposing the planetary gear type gearbox of the present invention in the inputstage and disposing the conventional three~train gearbox in the output stage.
    [12] [0012] A planetary gear type gearbox according to a second aspect of the presentinvention is the planetary gear type gearbox of the first aspect. In the planetary gear typegearbox, an output side of the second planetary gear train is connected to the interrnediateshaft through the first planetaiy gear train.
    [13] [0013] According to the present invention, the size of the gearbox can be further reduced.
    [14] [0014] A planetary gear type gearbox according to a third aspect of the present inventionis the planetary gear type gearbox of the first aspect. In the planetary gear type gearbox,the rear-stage transmission section is a transmission for providing three forward stages andone reverse stage. The forward stages are cornposed of a low-speed stage, ameddle-speed stage and a high-speed stage. The rear-stage transniission section includesa third planetary gear train, a fourth planetary gear train, a fiitth planetary gear train, alow-speed clntch, a middle-speed clutch, a high-speed clutch and a reverse clutch. Thethird planetary gear train is cornposed of a third sun gear, a plurality of third planet gears, a third Carrier and a third ring gear. The third planet gears rnesh With the third sun gear.
    [15] [0015] According to the present invention, the low-speed clutch and the third planetarygear train are disposed in the closest position to the output side (i.e., the final stage) asoutput-side components of the gearbox, compared to the reverse clutch and the fifthplanetary gear train that correspond to the reverse speed-change stage.
    [16] [0016] When the reverse speed-change stage is norrnaliy disposed in the final stage side,power is inputted through a plurality of planetary gear trains. Therefore, a reduction ratiois increased and traction force thereby tends to be excessively increased.
    [17] [0017] According to the present invention, however, such a configuration can be avoidedthat a reduction ratio of the reverse first-speed stage is greater than that of the forwardfirst-speed stage. As a result, it is possible to produce a gearbox for providing nineforward stages and three reverse stages, while such as case is avoided that a less-usablegearbox is produced due to the reverse first-speed stage having low speed and quite largetraction force.
    [18] [0018] A planetary gear type gearbox according to a fourth aspect of the presentinvention is the planetary gear type gearbox of the third aspect. In the planetary gear typegearbox, the third sun gear, the fourth sun gear and the fifth sun gear are all coupled to theintermediate shaft.
    [19] [0019] A planetary gear type gearbox according to a fifth aspect of the present inventionis the planetary gear type gearbox of the third aspect. In the planetary gear type gearbox,the fifth planet gear are composed of a plurality of inner peripheral side fifth planet gearsand a plurality of outer peripheral side planet gears. The inner peripheral side fifih planetgears mesh with the fifth sunpgear, whereas the outer peripheral side fifth planet gears meshwith the fifth ring gear.
    [20] [0020] A planetary gear type gearbox according to a sixth aspect of the present inventionis the planetary gear type gearbox of the third aspect. In the planetary gear type gearbox,the third ring gear, the fourth carrier and the fifth carrier are integrally and rotatably 4 coupled to each other.
    [21] [0021] A pianetary gear type gearbox according to a Seventh aspect of the presentinvention is the pianetary gear type gearbox of the first aspect. In the planetary gear typegearbox, the rear-stage transmission section is a transmission for providing three forwardstages and one reverse stage. The forward stages are cornposed of a low-speed stage, ameddle-speed stage and a high-speed stage. The rear-stage transmission section includesa third planetary gear train, a fourth planetary gear train, a fifth planetary gear train, alow-speed clutch, a middle-speed clutch, a high-speed clutch, and a reverse clutch. Thethird planetary gear train is cornposed of a third sun gear, a plurality of third planet gears, a third Carrier, and a third ring gear. The third planet gears mesh with the third sun gear.
    [22] [0022] According to the present invention, the reverse clutch and the fifth planetary geartrain, which correspond to the reverse speed-change stage, are disposed in the closestposition to the rear-stage side as output-side components of the gearbox. [0023} With the structure, it is possible to produce a gearbox for providing nine forwardstages and three reverse stages while quite large traction force is achieved in the reversefirst-speed stage by increasing a reduction ratio of the reverse first-speed stage.
    [24] [0024] A planetary gear type gearbox according to an eighth aspect of the presentínvention is the planetary gear type gearbox of the Seventh aspect. In the planetary gear type gearbox, the third sun gear and the fourth sun gear are coupled to the intermediate 5 shaft.
    [25] [0025] A planetary gear type gearbox according to a ninth aspect of the present inventionis the planetary gear type. gear box of the Seventh aspect. In the pianetaiy gear typegearbox, the third ring gear, the fourth carrier, and the ñfth sun gear are integraiiy androtatatbiy coupied to each other.
    [28] [0028] A configuration of a transmission (planetary gear type gearbox) 1, composed of afront-stage transmission section 10 and a rear-stage transmission section 20, Will behereinafter explained With reference to FIGS.1 to 4.
    [29] [0029] As illustrated in FIGS.l and 2, the transmission 1 according to the presentembodiment includes a torque converter 2, the front-stage transmission section 10 disposedon the rear-stage side of the torque converter 2, and the rear-stage transmission section 20.In the transmission 1, revolution of the torque converter 2 is transmitted to an input shaft11. Revolution speed of the input shaft 11 is shifted by the front-stage transmissionsection 10, and the shifted revolution is transmitted to an interrnediate shaft 21. Moreover,revolution speed of the interrnediate shaft 21 is shafted by the rear-stage transmissionsection 20, and the shified revolution is transmitted to an output shaft 26.
    [30] [0030] Specifically, the transmission 1 includes the front-stage transmission section 10and the rear-stage transmission section 20. The front-stage transmission section 10 isdisposed between the input shaft 11 and the intennediate shaft 21, Whereas the rear-stage transmission section 20 is disposed between the interrnediate shaft 21 and the output shaft 8 26. The transmission 1 makes up speed-change stages including nine forward stages (Flto F9) and three reverse stages (Rl to RB) by the combination of the front-stagetransmission section 10 (three stages) and the rear-stage transmission section 20 (threeforward stages and one reverse stage) (see FIG.4).[Front-Stage Transmission Section 10][0031] The front-stage transmission section 10 is mainly composed of the input shaft ll,a L clutch (first ciutch) 12a, a M clutch (second clutch) 12b, a H clutch (third clutch) l2c, aM pianetary gear train (first planetary gear train) 13 and a H planetary gear train (secondplanetary gear train) 14. in this case, the M pianetary gear train 13 and the I-I planetarygear train 14 are coaxially disposed to each other. The input shaft 11 is disposed in themost upstream position of a power transmission path in the transmission 1. Power of thetorque converter 2 is transmitted to the input shaft 11. The L clutch 12a is disposed in theciosest position to the output side in the front-stage transmission section 10. On the otherhand, the M clutch l2b is disposed in the closest position to the input side of the front-stagetransmission section 10. The H clutch l2c is disposed between the L clutch 12a and theM clutch 121).[M-Pianetary Gear Train 13]
    [32] [0032] The M-planetary gear train 13 is a single planetary type planetary gear train. TheM planetary gear train 13 is disposed on the output side in the front-stage transmissionsection 10. The M-planetary gear train 13 is mainly composed of a sun gear 13a, a carrier13b, a ring gear 13o and a piuraiity of planet gears l3e.
    [33] [0033] The sun gear 13a is disposed on the outer peripheral side of the input shaft ll.The sun gear 13a is also disposed in the most radiai inward position of the M planetarygear train 13.
    [34] [0034] The Carrier 13b rotatably supports the planet gears l3e roughly equally spacedapart from each other in the circurnferential direction. The respective planet gears l3eInesh with the sun gear 13a. In the present embodiment, the Carrier 13b is fixed to theinput shaft ll. in the M planetary gear train 13, revolution of the input shaft ll isconfigured to be inputted into the oarrier 13b.
    [35] [0035] The ring gear l3c is disposed for meshing with the planet gears l3e whose axesare supported by the carrier 13b. in the present ernbodiment, the ring gear 13o is fixed with respect to the intermediate shaft 21. Revolution of the M planetary gear train 13 is 9 thus outputted from the ring gear l3c.[H Planetary Gear Train 14]
    [36] [0036] The H planetary gear train 14 is a double planetary type planetary gear train.The H planetary gear train 14 is disposed in a closer position to the input side in thefront-stage transmission section 10 than the M planetary gear train 13 is. The H planetarygear train 14 is mainly composed of a sun gear 14a, a carrier 14b, a ring gear 14c, aplurality of inner peripheral side planet gears 14e1, and a plurality of outer peripheral sideplanet gears 14e2. In other Words, the H planetary gear train 14 includes two groups ofplanet gears.
    [37] [0037] The sun gear 14a is disposed on the outer peripheral side of the input shaft 11.The sun gear 14a is also disposed in the most radial inward position of the H planetary geartrain 14. Additionally, the sun gear 14a of the H planetary gear train 14 is configured tointegrally rotate With the sun gear 13a of the M planetary gear train 13.
    [38] [0038] The carrier 14b rotatably supports the inner peripheral side planet gears 14e1roughly equally spaced apart frorn each other in the circurnferential direction and the outerperipheral side planet gears i4e2 roughly equaliy spaced apart from each other in thecircuniferential direction. The inner peripheral side planet gears 14e1 of the inner andouter peripheral side planet gears 14e1, 14e2 herein rnesh with the sun gear 14a. In thepresent embodiment, the carrier 14b adjoins the carrier 13b included in the M planetarygear train 13 in the axiai direction of the input shaft 11. The carrier 14b is also integratedwith the carrier 13b. Therefore, revolution of the input shaft 11 can be inputted into thecarrier 14b in the I-I planetary gear train 14, too.
    [39] [0039] The ring gear 14c is disposed for ineshing With the outer peripheral side planetgears 14e1 of the planet gears 14e1, 14e2 whose axes are supported by the Carrier 14b.[0040] As described above, the inner peripheral side planet gears 14e1 rnesh with the sungear 14a whereas the outer peripheral side planet gears 14e2 mesh with the ring gear 14c.Additionally, the inner peripheral side planet gears 14e1 and the outer peripheral sideplanet gears 14e2 mesh with each other. In other words, each of the inner peripheral sideplanet gears 14e1 meshes With the sun gear 14a and one of the outer peripheral side planetgears l4e2. On the other hand, each of the outer peripheral planet gears 14e2 meshesWith the ring gear 140 and one of the inner peripheral side planet gears 14e1.
    [41] [0041] As described above, the H planetary gear train 14 is a double pianetary type planetary gear train composed of two groups of the planet gears 14e1, 14e2. With theconfiguration, the output rotational direction can be reversed.[0042] [Clutch and Power Transmission Path] The L ciutch 12a is configured to directly connect the input shaft 11 and theintermediate shaft 21. As illustrated in FIG.3(a), power is thereby directly transmitted tothe intermediate shaft 21 from the input shaft 11 via the L elutch 12a in the activation (i.e.,clutch connection) of the L clutch 12a. in this case, the reduction ratio is set to be 1.000.[0043] The M elutch 12b selectiveiy joins the sun gear 13a of the M pianetary gear train13 and a casing (fixation part) of the front-stage transmission section 10. As iliustrated inFIG.3(b), after inputted into the carrier 13b of the M planetary gear train 13 connected tothe input shaft 11, power is transmitted to the intermediate shaft 21 from the ring gear 130through the planet gears 13e whose axes are supported by the carrier 13b in the activation(i.e., elutch connection) of the M elutch 12b. In other words, power is inputted into thecarrier 13b and is then outputted from the ring gear 13c. With the configuration, thereduction ratio will be 0.742 in the activation of the M elutch 12b. The reduction ratio0.742 is less than that in the activation of the L elutch 12a (L-M inter-stage ratio is 1.348).[0044] The H ciutch 120 selectively joins the ring gear 14c of the H planetary gear train14 and the casing (fixation part) of the front-stage transmission section 10. As illustratedin FIG.3(c), after inputted into the carrier 13b of the M planetary gear train 13 connected tothe input shaft 11, power is partially transmitted to the intennediate shaft 21 from the ringgear 130 of the M pianetary gear train 13 without any changes in the activation (clutchconnection) of the H elutch 12c. On the other hand, rest of the power inputted into thecarrier 13b is transrnitted to the sun gear 14a of the H planetary gear train 14 via the carrier14b of the H planetary gear train 14 integrated with the carrier 13b of the M planetary geartrain 13. Then, the power is transmitted to the sun gear 13a of the M pianetary gear train13. Subsequently, the power is transrnitted to the intennediate shailft 21 from the ring gear13c of the M planetary gear train 13.
    [45] [0045] In the activation of the H clutch 12c as described above, after inputted into thecarrier 13b of the M planetary gear train 13, power is outputted from the ring gear 13c viathe carrier 14b and the sun gear 14a of the H planetary gear train 14 and the sun gear 13a ofthe M planetary gear train 13 sequentialiy. Accordingly, the reduction ratio is set to be 0.556, which is less than that in the activation of the M elutch (M-H inter~stage ratio is 11 1.335).[Rear-stage Transmission Section 20]
    [46] [0046] The rear-stage transmission section 20 includes the intermediate shaft 21, afirst-speed clutch (low-speed clutch) 22a, a second-speed clutch (middle-speed chitch) 22b,a third-speed clutch (high-speed clutch) 22c, a reverse clutch 22d, a first-speed planetarygear train (third pianetary gear train ) 23, a second-speed planetary gear train (fourthpianetary gear train ) 24, a reverse pianetary gear train (fifth planetary gear train ) 25 andthe output shafi 26.
    [47] [0047] The intermediate shaft 21 is interposed between the input shaft 11 and the outputshaft 26. The intermediate shaft 21 transmits power, outputted from the front-stagetransmission section 10, to the rear-stage transmission section 20. The first~speed ciutch22a is disposed in the closest position to the output side in the rear-stage transmissionsection 20. The second~speed clutch 22b is disposed between the third-speed eiutch 220and the reverse clutch 22d. The third-speed clntch 22c is disposed in the ciosest positionto the input side in the rear-stage transmission section 20. The reverse clutch 22d isdisposed between the first-speed clutch 22a and the second-speed ciutch 22b. The outputshaft 26 is disposed in the most downstream position of the power transmission path in thetransmission 1. The output shaft 26 outputs power, transrnitted thereto fiorn the inputshaft 11 via the intennediate shaft 21, to the downstrearn.
    [48] [0048] The first-speed planetary gear train (third pianetary gear train) 23 is a singlepianetary type pianetary gear train. The first-speed planetary gear train 23 is disposed inthe closest position to the output side in the rear-stage transmission section 20. Thefirst-speed planetary gear train 23 is mainiy composed of a sun gear 23a, a carrier 23b, aring gear 230 and a plurality of planet gears 23e.
    [49] [0049] The sun gear 23a is disposed on the outer peripherai side of the intermediate shaft21. The sun gear 23a is also disposed in the most radial inward position of the first-speedplanetary gear train 23.
    [50] [0050] The carrier 23b rotatably supports the planet gears 23e roughly equaiiy spacedapart from each other in the circurnferentiai direction. The respective planet gears 23emesh with the sun gear 23a. In the present embodiment, the Carrier 23b is fixed to the output shaft 26. With the structure, power of the rear-stage transmission section 20 is 12 outputted to the output shaft 26 from the Carrier 2313.
    [51] [0051] The ring gear 23c rneshes With the planet gears 23e whose axes are supported bythe Carrier 23b.
    [52] [0052] The second-speed planetary gear train (fourth planetary gear train) 24 is a singleplanetary type planetary gear train. The second-speed planetary gear train 24 is disposedin the Closest position to the input side of the rear-stage transmission section 20. Thesecond~speed planetary gear train 24 is mainly Cornposed of a sun gear 24a, a Carrier 24b, aring gear 24C and a plurality of planet gears 24e.
    [53] [0053] The sun gear 24a is disposed on the outer peripheral side of the intermediate shaft21. The sun gear 24a is also disposed in the most radial inward position of thesecond-speed planetary gear train 24.
    [54] [0054] The Carrier 24b rotatably supports the pianet gears 24e roughly equally spacedapart from each other in the circumferential direction. The respective planet gears 24emesh the sun gear 24a. In the present embodirnent, the Carrier 24b adjoins a Carrier 25bof the reverse planetary gear train 25 in the axial direction. The Carrier 24b is alsointegrated With the Carrier 25b.
    [55] [0055] The ring gear 24c meshes with the planet gears 24e whose axes are supported bythe Carrier 24b.
    [56] [0056] The reverse planetary gear train (fifth planetary gear train) 25 is a doubleplanetary type planetary gear train. The reverse planetary gear train 25 is interposedbetween the first-speed planetary gear train 23 and the second-speed planetary gear train 24in the rear-stage transmission section 20. The reverse gear train 25 is mainly composed ofa sun gear 25a, the Carrier 25b, a ring gear 250, a plurality of inner peripheral side planetgears 25el and a plurality of outer peripheral side planet gears 25e2.
    [57] [0057] The sun gear 25 a is disposed on the outer peripheral side of the intermediate shaft21. The sun gear 25a is also disposed in the most radial inward position of the reverseplanetary gear train 25.
    [58] [0058] The Carrier 25b rotatably supports the inner peripheral side planet gears 25elroughly equally spaced apart from each other in the Circumferential direction and the outer peripheral side planet gears 25e2 roughly equally spaced apart from each other in the 13 circuniferential direction. The respective inner peripheral side planet gears 25e1 meshWith the sun gear 25a. In the present ernbodirnent, the carrier 25b is integrated with andaxially adjoins the Carrier 24b of the second-speed planetary gear train _24 as describedabove. Furthermore, the carrier 25b is also integraily and rotatably coupled to the ringgear 23 of the first-speed planetaiy gear train 23.
    [59] [0059] The ring gear 25c meshes with the outer peripheral side planet gears 25e2 whoseaxes are supported by the carrier 25b.
    [60] [0060] As described above, the inner peripheral side planet gears 25e1 mesh with the sungear 25a whereas the outer peripheral side planet gears 25e2 mesh with the ring gear 25c.Furthermore, the inner peripheral side planet gears 25e1 and the outer peripheral sideplanet gears 25e2 mesh with each other. In other words, each of the inner peripheral sideplanet gears 25el rneshes With the sun gear 25a and one of the outer peripheral side pianetgears 25e2. On the other hand, each of the outer peripheral side planet gears 25e2 rnesheswith the ring gear 25c and one of the inner peripheral side planet gears 25e1. [0061} As described above, the reverse planetary gear train 25 is a double planetary typeplanetary gear train cornposed of two groups of the planet gears 25e1, 25e2. With thestructure, power for reversely moving the vehicle can be transmitted by reversing theoutput rotational direction.
    [62] [0062] The first-speed clutch 22a selectively joins the ring gear 23c of the first-speedplanetary gear train 23 and a casing (fixation part) of the rear-stage transmission section 20.In the activation (clutch connection) of the first-speed clutch 22a, power is transmitted tothe car-fier 23b from the sun gear 23a of the first-speed planetary gear train 23 connected tothe intennediate shaft 21 via 'die planet gears 23e. The power, transmitted to the earrier23b, is then transmitted to the output shaft 26. Note in the activation of the first-speedclutch 22a, forward first to third speed change stages (Fl to F3) can be achieved by thecombination of the aforernentioned activations of the L, M and H ciutches 12a, l2b and120. FIG.4 illustrates example speed change 'ratios of the case. Specifically, the speedchange ratios of Fl, F2 and P3 can be set to 5.091, 3.780 and 2.830, respectiveïy. Asshown in FIGÅ, the inter-stage ratio F1/F2 is herein 1.348 whereas the inter-stage ratioF2/F3 is 1.335.
    [63] [0063] The second-speed clutch 22b selectively joins the ring gear 240 of the 14 second-speed planetary gear train 24 to the casing (fixation part) of the rear~stagetransmission section 20. In the activation (i.e., clutch connection) of the second-speedciutch 221), the power inputted into the interrnediate shatt 21 is partially transmitted fromthe sun gear 24a of the second-speed planetary gear train 24 to the carrier 25b integratedwith the carrier 2413 via the planet gears 24e. Then the partiaily transmitted power istransmitted to the carrier 2313 of the first-speed pianetary gear train 23 via the ring gear 23cand the planet gears 23e. Finally, the partiaily transmitted power is transmitted to theoutput shaft 26. Simuitaneously, the rest of power is transmitted from the sun gear 23a ofthe first-speed planetary gear train 23 to the carrier 231) via the planet gears 23e. Thustransmitted power is then transmitted to the output shaft 26.
    [64] [0064] I the activation of the second-speed clutch 22b, forward fourth to sixth speedchange stages (F4 to P6) can be achieved by the combination of the aforementionedactivations of the L, M and H clutches 12a, 12b and 120. FIG.4 shows example speed'change ratios of the case. Specificaliy, the speed change ratios of P4, F5 and F6 can beset to be 2.163, 1.606 and 1.203, respectively. As shown in FIG.4, the inter-stage ratios - F3/F4, F4/F5 and F5/F6 are herein 1.308, 1.348 and 1.335, respectively.
    [66] [0066] In the activation of the third-speed clutch 22c, forward Seventh to ninth speed change stages (P7 to P9) can be achieved by the combination of the aforementioned L, M i and H oiutches 12a, 12b and 12c. F1G.4 shows example speed change ratios of the case.
    [67] [0067] The reverse clutch 22d selectively joins the ring gear 25c of the reverse planetary gear train 25 and the casing (fixation part) of the rear-stage transmission section 20. Inthe activation (i.e., clutch connection) of the reverse clutch 22d, power inputted into theinterrnediate shaft 21 is transmitted from the sun gear 25a of the reverse planetary geartrain 25 to the carrier 25b via the planet gears 25e. The power is then transmitted to thecarrier 23b of the first-speed planetary gear train 23 via the ring gear 230 and the planetgears 23e. Thus transrnitted power is then transmitted to the output shaft 26. ln theactivation of the reverse clutch 22d, reverse first to third speed change stages (Rl to R3) can be achieved by the combination of the aforementioned activations of the L, M and H clutches 12a, l2b and 12c. FIG.4 shows example speed change ratios of the case.
    [68] [0068] [Characteristics of Transmission 1 and Front-stage transmission section 10 ofPresent Embodiment] (1) In the front-stage transmission section 10 of the present embodiment, both of thecarrier 13b of the M planetary gear train 13 and the carrier l4b of the H planetary gear train14 are connected to the input shaft 11. Additionally, the ring gear 130 of the M planetarygear train 13 is connected to the interrnediate shaft 21.
    [69] [0069] With the structure, it is possible to achieve a configuration that power is inputtedinto the carrier 13b from the input shaft 11 and the inputted power is outputted from thering gear 130 in the activation of the M and H clutches l2b, 12c. Therefore, the reductionratios can be all set to be equal to or less than 1.000 with the combination of theaforementioned two planetary gear trains in the activations of the L, M and H clutches 12a,l2b and 12c. Consequently, the large amount of torque is not transmitted to theintennediate shaft 21 on the output side, and the structure of the transmission 1 can beSimplified.
    [70] [0070] Furthermore, the inter-stage ratios arnong H, M and L can be roughly the sameusing the Structures of the M and 1-1 planetary gear trains 13, 14 and the relation betweeninput power and output power, as described above. Accordingiy, the speed change stages,cornposed of nine forward stages and three reverse stages, can be easily provided by the combination of the M and H planetary gear trains 13, 14 and the rear~stage transmission 16 section 20 that is disposed on the rear-stage side and includes three forward stages and onereverse stage.[0071] (2) In the transmission 1 of the present embodiment, the rear-stage transmissionsection 20 is disposed on the output side of the aforementioned front-stage transmissionsection 10, as illustrated in FIGSJ and 2. The rear-stage transmission section 20 includesa clutch mechanism having the first-speed, second-speed, third-speed and reverse clutches22a, 22b, 220 and 22d, and the first-speed, the second-speed and reverse planetary geartrains 23, 24 and 25.
    [72] [0072] With the structure, the inter-stage ratios among three speed change stages (L, Mand H) can be set to be roughly the same in the front~stage transmission section 10.Consequently, it is possible to easily form the multi-stage (i.e., nine forward stages andthree reverse stages) transmission 1 with equal inter-stage ratios in a compact size only bycombining the front-stage transmission section 10 with the rear-stage transmissions section20 that provides three forward stages and one reverse stage.
    [73] [0073] (3) In the transmission 1 of the present embodiment, the reverse clutch 22d and thereverse planetary gear train 25 are disposed closer to the input side than the first-speedclutch 22a and the first-speed planetary gear train 23 are. It is possible to prevent thereduction ratios of the speed change stages from having unduly large values in the reversetravel of the vehicle, compared to a transmission having a structure that the reverse clutchand the like are disposed in the closest position to the output side. Consequently, thetravel speed and the travel torque can he appropriately set When the vehicle reverselytravels.
    [74] [0074] [Other Ernbodiments] As described above, an embodiment of the present invention has been explained.However, the present invention is not limited to the aforementioned ernbodirnent. Avariety of changes are possible without departing from the scope of the present invention.[0075] (A) In the aforernentioned ernbodiment, a configuration has been exemplified that thethird speed clutch 220, a collection of the second-speed clutch 22b and the second-speed planetary gear train 24, a collection of the reverse clutch 22d and the reverse planetary gear 17 train 25, and a collection of the first-speed clutch 22a and the first-speed planetary geartrain 23 are disposed in this sequential order from the front-stage side as componentsforming the rear-stage transmission section 20 disposed on the rear side of the front-stagetransmission section 10. However, the present invention is not limited to theconfiguration.
    [76] [0076] In short, a transmission section, having other configuration, may he combinedWith the front-stage transmission section 10 as the rear-stage transmission section. i[0077] For example, a transmission of the present invention may be a transmission 100illustrated in FIGS. The transmission 100 is configured to transmit power from anintermediate shaft 31 to an output shaft 36. The transmission 100 includes a rear-stagetransmission section 30. The rear-stage transmission section 30 has a configuration that athird-speed clutch 320, a collection of a second-speed clutch 32h and a second-speedplanetary gear train 34, a collection of a first~speed clutch 32a and a first-speed planetarygear train 33, and a collection of a reverse clutch 32d and a reverse planetary gear train 35are sequentially disposed in this order from the front-stage side.
    [78] [0078] In the transmission 100 illustrated in FIGS, the first-speed planetary gear train 33is selectively joined to the first clutch 32a. The first-speed planetary gear train 33includes a sun gear 33a, a carrier 33b, a plurality of planet gears 33e rotatably supported bythe carrier 33b, and a ring gear 33e.
    [79] [0079] On the other hand, the second~speed planetary gear train 34 is selectively joined tothe second clutch 32b. The second-speed planetary gear train 34 includes a sun gear 34a,a carrier 34b, a plurality of planet gears 34e rotatably supported by the carrier 34b, and aring gear 34c.
    [80] [0080] Further, the reverse planetary gear train 35 is selectively joined to the reverseclutch 32d. The reverse planetary gear train 35 includes a sun gear 35a, a carrier 35b, aplurality of planet gears 35e rotatably supported by the carrier 35b, and a ring gear 35c.[0081] Furthermore, the ring gear 33e, the carrier 34b and the sun gear 35a are coupled tothe intermediate shaft 31 through the third-speed clutch 32c. On the other hand, the sungears 33a, 34a are integrally and rotatably coupled to each other. The carriers 3313, 35bare coupled to the output shaft 36.
    [82] [0082] Further, the first-speed clutch 32a couples/uncouples the ring gear 33e from a casing (fixation part). The second-speed clutch 32h couples/uncouples the ring gear 34c 18 from the casing (fixation part)- The third-speed ciutch 32c couples the intermediate shaft31 to the carrier 34b. The reverse clutch 32d couples the ring gear 35c to the case(fixation part).
    [83] [0083] In this case, the reverse planetary gear train 35 and the like are positioned in theclosest position to the rear-stage side. It is thereby possible to sufficiently ensure tractionforce by substantially increasing the reduction ratio of the reverse first-speed stage. As aresult, the present example embodiment can be applied to a type of vehicle that requirestraction force in the reverse traveling.
    [84] [0084] (B) In the aforementioned embodiment, the setting has been exernplified that the H, Mand L reduction ratios of the front-stage transmission section 10 are set to be 0.556, 0.742and 1.000, respectively. However, the present invention is not limited to this.
    [85] [0085] For example, the reduction ratios can be set to be greater/less than the abovevalues as long as the inter-stage ratios H/M and M/L can be roughly the same based on thereduction ratios.
    [86] [0086] (C) In the aforementioned embodiment, a configuration has been exemplified that therear-stage transmission section 20 provides three forward stages and one reverse stage.However, the present invention is not limited to this.
    [87] [0087] For example, a further multi-stage transmission section, providing four forwardstages and one reverse stage, may be combined with the front-stage transmission section asthe rear-stage transmission section. In this case, it is possible to obtain a furthermulti-stage gearbox that provides 12 forward stages and three reverse stages as a whole.[0088] (D) In the aforementioned embodirnent, the transmission l of the present inventionhas been explained with an eirarnple case that it is installed in a dump truck. However,application of the present invention is not limited to this.
    [89] [0089] For exarnple, the transmission 1 may be installed in a construction vehicle such asa wheel loader. Altematively, it may be installed in any other working vehicles.INDUSTRIAL APPLICABILITY
    [90] [0090] According to the planetary gear type gearbox of the present invention, amulti-stage gear train with a simple structure can be produced by inhibiting torque to be 19 transrnitted to a rear-stage transmission section without increasing the size of gears to bedisposed in the rear stage or adding an extra component such as a speedup gear.Therefore, the present invention can be Widely applied to the general vehicles configured totravel while the travel speed or the traction force are changed by shifiing a plurality of speed change stages back and forth.
    权利要求:
    Claims (10)
    [1] 1. A planetary gear type gearbox, comprising: a front-stage transmission section including an input shaft that power is inputtedthereto; and a rear-stage transmission section including an intermediate shaft coupled to thefront-stage transmission section and an output shaft for outputting power, wherein the fiont-stage transmission section includes: a first planetary gear train composed of: a first sun gear; a plurality offirst planet gears meshing with the first sun gear; a first Carrier connected to theinput shait, the first carrier rotatabiy supporting the first planet gears; and a firstring gear connected to the illtennediate shaft, the first ring gear meshing With the i first planet gears; a second planetary gear train composed of: a second sun gear integrallyand rotatably coupled to the first sun gear; a plurality of inner peripheral sidesecond planet gears meshing With the second sun gear; a plurality of outerperipheral side second píanet gears rneshing With the inner peripheral sidesecond planet gears; a second carrier connected to the input shaft, the secondcarrier rotatably supporting the inner peripheral side second planet gears and theouter peripheral side second planet gears; and a second ring gear meshing with theouter peripherai side second planet gears; a first clutch configured to couple/uncouple the input' shaft and theintermediate shaft; a second clutch configured to allow/prevent rotation of the second sun - gear; and a third ciutch configured to allow/prevent rotation of the second ring gear.[Clairn 2]
    [2] 2. The planetary gear type gearbox according to claim 1, Wherein an output side ofthe second planetary gear train is connected to the intermediate shaft through the firstplanetary gear train.
    [3] 3. [Claim 3] 21
    [4] 4. The planetary gear type gearbox according to claim 1, Wherein a speedup ratio ofthe second planetary gear train is greater than that of the first planetary gear train.[Claim 4]
    [5] 5. The planetary gear type gearbox according to ciaim 1, wherein the rear-stage transmission section is a transmission for providing threeforvvard stages and one reverse stage, the forward stages being composed of a low-speedstage, a rneddle-speed stage and a high-speed stage, and the rear-stage transmission section includes: a third planetary gear train composed of: a third sun gear; a plurality ofthird pianet gears meshing with the third sun gear; a third carrier coupied to theoutput shaft, the third carrier rotatably supporting the third planet gears; and athird ring gear meshing with the third planet gears; a fourth planetary gear train cornposed of: a fourth sun gear; a piurality offourth planet gears meshing With the fourth sun gear; a fourth carrier rotatablysupporting the fourth planet gears; and a fourth ring gear meshing with the fourthplanet gears; a fifth pianetary gear train cornposed of: a fifth sun gear; a plurality offifth planet gears meshing With the fifth sun gear; a fifth carrier rotatablysupporting the fifth planet gears; and a ñfth ring gear meshing with the iifth planet gear-s; a low-speed clutch configured to allow/prevent rotation of the third ringgear; a middle-speed clutch configured to allow/prevent rotation of the fourth.ring gear; a high-speed clutch configured to couple/uncouple the intermediate shaftand the fourth Carrier and couple/uncouple the intermediate shaft and the tifthCarrier; anda reverse clutch confignred to allow/prevent rotation of the fifth ring gear.[Claim 5]The planetary gear type gearbox according to ciaim 4, wherein the third sun gear,the fourth sun gear and the fifth sun gear are all coupíed to the intermediate shaft.[Cíaim 6] 22
    [6] 6. The planetary gear type gearbox according to clairn 4, wherein the fifth planetgears are composed of a plurality of inner peripheral side fifth planet gears and a piuralityof outer peripheral side planet gears, the inner peripheral side fifth planet gears rneshingvvith the fifth sun gear, and the outer peripheral side fifth planet gears meshing with thefifth ring gear.
    [7] 7. [Claim 7]
    [8] 8. The planetary gear type gearbox according to claim 4, Wherein the third ring gear,the fourth carrier and the fifth carrier are integrally and rotatably coupied to each other."[Claim 8]
    [9] 9. The planetary gear type gearbox according to claim 1, wherein the rear-stage transmission section is a transmission for providing threeforward stages and one reverse stage, the forward stages being composed of a low-speedstage, a rneddle-speed stage and a high-speed stage, and the rear-stage transmission section includes: a third pianetary gear train composed of: a third sun gear; a pluraiity ofthird planet gears meshing With the third sun gear; a third carrier coupled to theoutput shaft, the third carrier rotatably supporting the third planet gears; and athird ring gear rneshing with the third planet gears; a fourth planetary gear train composed of: a fourth sun gear; a plurality offourth planet gears meshing with the fourth sun gear; a fourth carrier rotatabiysupportingthe fourth planet gears; and a fourth ring gear rneshing with the fourthplanet gears; a fifth planetary gear train composed of: a fifth sun gear; a plurality of ' fifth planet gears meshing With the fifth sun gear; a fifth carrier coupled to theoutput shaft, the fifth carrier rotatably supporting the fifth planet gears; and a fifthring gear rneshing with the fifth planet gears; a low-speed clutch configured to allow/prevent rotation of the third ringgear; i a middle-speed clutch configured to allow/prevent rotation of the fourth ring gear; a high-speed clutch configured to couple/uncouple the interrnediate shaftand the fourth carrier; and I 23 a reverse clutch confignred to allow/prevent rotation of the fifth ring gear.[Claim 91The planetary gear type gearbox according to claim 8, wherein the third sun gear and the fourth sun gear are coupled to the intermediate shaft.
    [10] 10. [Claim 10]The planetary gear type gearbox according to claím 8, wherein the third ring gear, the fourth carrier and the fifih sun gear are integrally and rotatably coupled to each other. 24
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    同族专利:
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    CN103185113B|2014-05-07|
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US4004473A|1973-11-29|1977-01-25|Caterpillar Tractor Co.|Broad range fluid and mechanical power transmission for vehicles or the like|
    US4205563A|1975-12-10|1980-06-03|Caterpillar Tractor Co.|Variable speed transmission|
    JP2671463B2|1988-12-07|1997-10-29|トヨタ自動車株式会社|Gearbox for automatic transmission|
    JPH0560190A|1991-08-27|1993-03-09|Komatsu Ltd|Multistage speed change gear apparatus with auxiliary speed change gear|
    US5823910A|1995-11-23|1998-10-20|Hyundai Motor Company|Transmission including planetary gear sets|
    US7276011B2|2003-08-18|2007-10-02|Toyota Jidosha Kabushiki Kaisha|Automatic transmission|
    DE102004023956A1|2004-05-14|2005-12-01|Zf Friedrichshafen Ag|Multi-stage gear for e.g. passenger car, has two rotatable shafts that are connected to sun gears of planetary gear sets, respectively, where input shaft is connected to sun gear of one set|
    US7204780B2|2005-05-25|2007-04-17|General Motors Corporation|Multi speed transmission|
    DE102006031309B4|2006-07-06|2011-08-25|ZF Friedrichshafen AG, 88046|Multi-speed transmission|
    US7887457B2|2007-01-11|2011-02-15|GM Global Technology Operations LLC|Multi-speed transmission|
    US7775931B2|2007-03-16|2010-08-17|Gm Global Technology Operations, Inc.|Multi-speed transmission|
    US7811197B2|2007-03-30|2010-10-12|Gm Global Technology Operations, Inc.|8-speed transmission|
    JP5084751B2|2009-01-07|2012-11-28|株式会社野村総合研究所|Advertisement providing support device, advertisement providing support method, and advertisement providing system|US9339938B2|2010-10-08|2016-05-17|Milwaukee Electric Tool Corporation|Powered cutting tool|
    USD668922S1|2012-01-20|2012-10-16|Milwaukee Electric Tool Corporation|Powered cutting tool|
    KR101367411B1|2012-04-17|2014-02-27| 에이치엠|Transmission device|
    US8827862B2|2012-07-02|2014-09-09|Caterpillar Inc.|Configuration for compact five speed planetary transmission|
    CN103527728B|2013-10-22|2016-08-17|重庆隆旺机电有限责任公司|Double-planet system three-speed gearbox|
    KR101637272B1|2014-09-23|2016-07-07|현대자동차 주식회사|Planetary gear train of automatic transmission for vehicles|
    US9644724B2|2014-10-17|2017-05-09|Allison Transmission, Inc.|Split power infinitely variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges|
    US9644721B2|2014-10-17|2017-05-09|Allison Transmission, Inc.|Split power infinitely variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges and low variator load at vehicle launch|
    US9651127B2|2014-10-17|2017-05-16|Allison Transmission, Inc.|Split power infinitely variable transmission architecture incorporating aplanetary type ball variator with low part count|
    US9772017B2|2014-10-17|2017-09-26|Allison Transmission, Inc.|Split power infinitely variable transmission architecture incorporating a planetary type ball variator with low variator loading at vehicle launch|
    US9382988B2|2014-10-17|2016-07-05|Allison Transmission, Inc.|Split power infinitely variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges|
    US9512911B2|2014-10-17|2016-12-06|Allison Transmission, Inc.|Split power continuously variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges|
    KR101664046B1|2014-12-15|2016-10-10|현대자동차 주식회사|Planetary gear train of automatic transmission for vehicles|
    CA3011708A1|2016-01-19|2017-07-27|Twin Disc, Inc.|Heavy-duty industrial transmission|
    CN106062419B|2016-02-01|2017-05-17|株式会社小松制作所|Planetary gear type transmission|
    KR20180003158A|2016-06-30|2018-01-09|현대자동차주식회사|Planetary gear train of automatic transmission for vehicles|
    DE102016222226A1|2016-11-11|2018-05-17|Zf Friedrichshafen Ag|Multi-speed transmission|
    EA033682B1|2017-06-14|2019-11-15|State Scient Institution Joint Institute Of Mechanical Engineering Of The National Academy Of Scienc|Main box of planetary gearbox, planetary gearbox and method for manufacture thereof|
    KR20190048372A|2017-10-31|2019-05-09|현대자동차주식회사|Planetary gear train of automatic transmission for vehicles|
    KR20190066306A|2017-12-05|2019-06-13|현대자동차주식회사|Planetary gear train of automatic transmission for vehicles|
    法律状态:
    2017-03-28| NUG| Patent has lapsed|
    优先权:
    申请号 | 申请日 | 专利标题
    JP2007246655A|JP2010156351A|2007-09-25|2007-09-25|Planetary gear type gearbox|
    PCT/JP2008/065314|WO2009041209A1|2007-09-25|2008-08-27|Planetary gear type gearbox|
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