CN101984271A - Multistage transmission - Google Patents
Multistage transmission Download PDFInfo
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- CN101984271A CN101984271A CN 201010549156 CN201010549156A CN101984271A CN 101984271 A CN101984271 A CN 101984271A CN 201010549156 CN201010549156 CN 201010549156 CN 201010549156 A CN201010549156 A CN 201010549156A CN 101984271 A CN101984271 A CN 101984271A
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Abstract
The invention discloses a multistage automatic transmission for a vehicle. The transmission comprises two or three power transmission mechanisms in the front, two planet rows and five or six gear shifting elements; the third rotary component of the second planet row is connected with an output; the first rotary components of the first and second planet rows are interconnected; the first and second gear shifting elements are connected in series between the second rotary component of the second planet row and the second and third rotary components of the first planet row in turn; the third gear shifting element is connected in series on the route of transmitting an input power to the third rotary component of the first planet row from the first power transmission mechanism; the fifth and sixth gear shifting elements are connected in series on the route of transmitting the input power to the first and second rotary components of the first planet row through the second power transmission mechanism or the second and third power transmission mechanisms in turn; and the fourth gear shifting element can selectively brake the third rotary component of the first planet row. The transmission is provided with five or eight forward gears, each gear is combined with three gear shifting elements, and the gears can be arranged on split shafts so that the length of the gears is shortened and the gears are suitable for driving the vehicle forwards.
Description
Technical field
The present invention relates to be used for the multiple-speed gear-box field of vehicle, be specifically related to comprise the multistage automatic transmission of a plurality of planetary gear set and gear-changing component.
Background technique
Automatic transmission is progressively developed to Pyatyi, six grades or more multistage several directions by early stage three, level Four speed change, complexity, volume weight also increase thereupon simultaneously, tradition level Four speed changer generally comprises two planetary gear set, five or more gear-changing component (clutch and break), and the conventional five-stage speed changer generally increases planetary gear set, one or more gear-changing component and constitutes on the basis of level Four speed changer.This traditional each gear of class speed changer is only in conjunction with two gear-changing components, other gear-changing component all is in the separation sliding mode, too much be in the gear-changing component that separates sliding mode and can have caused certain slip loss, this also is one of not high reason of traditional automatic transmission efficient.
Existing seven numerous or 8-speed transmissions, generally comprise more planetary gear set and gear-changing component, optimized design includes only three planetary gear set and six gear-changing components, perhaps four planetary gear set and five gear-changing components, as: " multispeed manual transmission " of Chinese patent publication number CN1531634, " planetary gear type multi-stage transmission for vehicle " of CN1934373 all comprised three (or being equivalent to three) planetary gear set and six gear-changing components, each gear of this class speed changer is only in conjunction with two gear-changing components, other four gear-changing components all are in the separation sliding mode, and the slip loss that is caused has greatly weakened by increasing the energy-saving benefit that number of steps of speeds obtained; " automatic transmission " of " multiple-speed gear-box " of Chinese patent publication number CN1650119, " multi-speed transmission " of CN101191535, CN101240833, CN101846160A, CN101846161A etc. comprised three (or being equivalent to three) planetary gear set and six gear-changing components equally, each gear of this class speed changer separates three gear-changing components, and the slip loss of gear-changing component is less.
In the 8-speed transmission that comprises four planetary gear set and five gear-changing components: " multi-speed transmission " of Chinese patent publication number CN101235879, CN101298881, " 8-speed automatic transmission " of CN101275644, CN101311580 " 8 gear gearbox " waits each gear to separate three gear-changing components; " multiple-speed gear-box " of Chinese patent publication number CN101103212, CN101218452, " multi-speed transmission " of CN101354072, CN101275631, CN101275633 " 8 gear gearbox " waits each gear only to separate two gear-changing components, and the slip loss of gear-changing component is reduced to minimum.
No matter be that three planetary gear set add six gear-changing components below, or four planetary gear set add seven or 8-speed transmission of five gear-changing components, their all planetary gear set, gear-changing component all are arranged on the same axis, the axial length of speed changer is longer, is not suitable for the vehicle of preposition forerunner, lateral arrangement speed changer.
" Powershift multistep transmission " of Chinese patent publication number CN101275630, " but multiple-speed gear-box of powershift " of CN101720395A, " eight speed automatic transmission of band planetary gear system and counter shaft gear device " of CN101334094, CN101392817, " 8-speed transmission " of CN101392819 etc. is the version that four planetary gear set of a class add the speed changer of five gear-changing components, be with planetary gear set, shifting element is arranged on two axis, transmit power by the external tooth wheels between centers, this class speed changer has reduced by a planetary gear set, shortened axial length, the vehicle that is fit to the lateral arrangement speed changer, but increased by three external gear wheel groups simultaneously, its volume weight does not reduce.
Summary of the invention
The invention provides the technical problem that a kind of multiple-speed gear-box will solve is: one, with three planetary gear set and five Pyatyi speed changers that gear-changing component is realized, each gear only separates two gear-changing components, increase the 8-speed transmission that a gear-changing component is realized, each gear separates three gear-changing components, the slip loss of gear-changing component is less, planetary gear set, gear-changing component can be arranged on two axis simultaneously, reduce by a planetary gear set, increase by two external tooth wheels, shorten the vehicle that axial length is applicable to the lateral arrangement speed changer; They are two years old, with four planetary gear set and five seven or 8-speed transmissions that gear-changing component is realized, each gear only separates two gear-changing components, the slip loss of gear-changing component is very little, planetary gear set, shifting element can be arranged on two axis simultaneously, reduce by two planetary gear set, increase by three external tooth wheels, shorten the vehicle that axial length is applicable to the lateral arrangement speed changer.
The general plotting of technical solution of the present invention is: a kind of multiple-speed gear-box comprises speed changer input block, speed changer output block, has the preposition drive part of fixed conveyor specific output and can change the main transformer speed part of velocity ratio; Described preposition drive part comprises two first, second power-transmitting units with fixed drive ratio at least, perhaps also comprises the 3rd power-transmitting unit with fixed drive ratio; Described main transformer speed part comprises first, second planetary gear set, described first, second planetary gear set respectively has three rotary components, the 3rd rotary component of described second planetary gear set is connected with the speed changer output block, and described first, second planetary gear set first rotary component separately interconnects; Two gear-changing components: first, second clutch shift element is serially connected in respectively between second, third rotary component of second rotary component of second planetary gear set and described first planetary gear set successively; Input power is imported from the speed changer input block; The three-clutch gear-changing component is arranged on from described first power-transmitting unit of speed changer input block input power process on the route of the 3rd rotary component transmission of the first star gear train;
One or two gear-changing component in addition: five, the 6th clutch gear-shift element be separately positioned on input power through described second power-transmitting unit or respectively through the second and the 3rd power-transmitting unit respectively successively on the route that first, second rotary component of described first planetary gear set transmits, specifically be two technological schemes:
Technological scheme one, described preposition drive part only comprises described first, second power-transmitting unit, both one of or two shifting elements: described the 5th, the 6th clutch shift element be separately positioned on input power through described second power-transmitting unit respectively successively on the route that first, second rotary component of the first star gear train transmits, also comprise the four clutches gear-changing component: the 3rd rotary component of selectively braking the first star gear train;
Technological scheme two, described preposition drive part comprises three: first, second, third power-transmitting unit, described the 5th, the 6th clutch shift element be separately positioned on input power respectively through described second, third power-transmitting unit respectively successively on the route that first, second rotary component of the first star gear train transmits.
Above-mentioned " X clutch shift element be arranged on input power through the Y power transmitting mechanism on the route that the Z rotary component of first planetary gear set transmits " its concrete feature is: described X clutch shift element both can be serially connected between the output block and described Z rotary component of described Y power transmitting mechanism, the input block of speed changer is connected with the input block of described Y power transmitting mechanism, also can be serially connected between the input block of the input block of speed changer and described Y power transmitting mechanism, the output block of described Y power transmitting mechanism is connected with described Z rotary component; Its effect is that described X clutch shift element is serially connected on the route of described transmission of power, the selectively transmission of ' connection/cut-out ' power.
The common trait of technological scheme one and technological scheme two is that annexation is identical between the output block of described first, second power-transmitting unit, first, second planetary gear set, first, second, third, the 5th clutch shift element, speed changer, and the effect of the 6th clutch shift element all is the power input of second rotary component of ' connection/cut-out ' first planetary gear set; Technological scheme one and technological scheme two differences are that the latter is than the former how described the 3rd power transmission mechanism, described the 6th clutch shift element is arranged in technological scheme one imports described second power-transmitting unit of power process on the route of second rotary component transmission of the first star gear train, and is arranged on described the 3rd power-transmitting unit of input power process in technological scheme two on the route of second rotary component transmission of the first star gear train.
In technological scheme one, described first power-transmitting unit can be made of the transmission shaft that connects the speed changer input block, and described second power-transmitting unit can be made of a planetary gear set with three rotary components: parts, two rotary components wherein that one of them rotary component connects the speed changer input connect case of transmission, three rotary components wherein as output block; Speed changer comprises three planetary gear set and five or six gear-changing components like this, and speed changer has reverse gear of five forward gearss or two reverse gear of eight forward gearss, and has between good gear ratio and shelves than distributing.
In technological scheme two, in four rotary components of two mutually compound planetary gear set: input block, two rotary components wherein that one of them rotary component connects speed changer connect case of transmission, its two other rotary component and a transmission shaft that is connected with the input block of speed changer respectively as each output blocks of described three power-transmitting units; Speed changer comprises four planetary gear set and five gear-changing components like this, always has nine gear ratio, suitably disposes the gear ratio of each planetary gear set, and speed changer has seven or eight forward gearss, a reverse gear.
Beneficial effect of the present invention is: first aspect, each gear of speed changer are all in conjunction with three gear-changing components, and two or three gear-changing components in addition are in the separation sliding mode, and the slip loss of gear-changing component is less; Second aspect, because each power-transmitting unit of preposition drive part all has fixing velocity ratio, therefore available common external tooth wheels replace constituting the planetary gear set of each power-transmitting unit, transmission shaft, speed changer only contains two planetary gear set like this: first, second planetary gear set, two or three external tooth wheels, and on can axis with the driving gear that partly or entirely is arranged into described external tooth wheels in the middle of the 3rd to the 5th clutch shift element, described first, second planetary gear set and described first, the second clutch gear-changing component is arranged on the axis of driven gear of described external tooth wheels, can significantly shorten the axial length of speed changer; The third aspect is compared with the existing speed changer of arranging by diaxon equally, and the present invention has reduced by a planetary gear set.Two technological schemes of the present invention all are on the basis of general plotting of the present invention: have annexation between preposition power-transmitting unit, first, second planetary gear set and the gear-changing component of fixed drive ratio, inequality with prior art, and produce above-mentioned beneficial effect thus.
Though the embodiment according to such scheme has a lot, only switch a pair of gear-changing component between adjacent gear and have gear ratio preferably and shelves between more few than the embodiment who distributes, enumerated practical embodiment in the specific embodiment of the invention.In addition, " first, second ... " described in the present invention only is the using names that attaches, be not expression physically or other Rankine-Hugoniot relationss in logic.
Description of drawings
Fig. 1, Fig. 2, Fig. 3, Figure 17 are general plotting of the present invention and several version, and wherein Fig. 1～3 reflections is the general plotting of technological scheme one, and what Figure 17 reflected is a kind of form of technological scheme two general plottings;
Fig. 4～15th, each embodiment one～12 of technological scheme one;
Figure 18～26th, each embodiment 13～22 of technological scheme two.
Embodiment
Fig. 1～3rd, the general plotting of technological scheme one, Fig. 4～15th, each embodiment one～12 of technological scheme one; Wherein said three-clutch gear-changing component 33 be arranged on input power through described first power-transmitting unit 100 on the route that the 3rd rotary component 13 of described first planetary gear set 10 transmits, selectively described first power-transmitting unit 100 of ' connections/cut-outs ' process is to the power of the 3rd rotary component 13 transmission of described first planetary gear set 10, described four clutches gear-changing component 34 selectively makes the 3rd rotary component 13 brakings of described first planetary gear set 10, and embodiment is:
Perhaps as Fig. 1: between the output block 102 that three-clutch gear-changing component 33 is serially connected in first power-transmitting unit 100 and the 3rd rotary component 13 of first planetary gear set 10 and the input block 101 of first power-transmitting unit 100 is connected with the input block 1 of speed changer and four clutches gear-changing component 34 is serially connected between the 3rd rotary component 13 and case of transmission 5 of first planetary gear set 10
Perhaps as Fig. 2: between the input block 101 that three-clutch gear-changing component 33 is serially connected in first power-transmitting unit 100 and the input block 1 of speed changer and the output block 102 of first power-transmitting unit 100 is connected with the 3rd rotary component 13 of first planetary gear set 10 and four clutches gear-changing component 34 is serially connected between the 3rd rotary component 13 and case of transmission 5 of first planetary gear set 10
Perhaps between the input block 1 of the input block 101 that is serially connected in first power-transmitting unit 100 as Fig. 3,5,8,10: the three-clutch gear-changing components 33 and speed changer and the output block 102 of first power-transmitting unit 100 is connected with the 3rd rotary component 13 of first planetary gear set 10 and the input block 101 and case of transmission 5 of four clutches gear-changing component 34 serial connections first power-transmitting unit 100 between.
Described the 5th clutch shift element 35 be arranged on input power through described second power-transmitting unit 200 on the route that first rotary component 11 of described first planetary gear set 10 transmits, selectively described second power-transmitting unit 200 of ' connections/cut-outs ' process is to the power of first rotary component, 11 transmission of described first planetary gear set 10, embodiment is:
Perhaps as Fig. 1～3,4,6,9,11～15: between the output block 202 that the 5th clutch shift element 35 is serially connected in second power-transmitting unit 200 and first rotary component 11 of first planetary gear set 10 and the input block 201 of second power-transmitting unit 200 be connected with the input block 1 of speed changer
Perhaps as Fig. 5,10: in the scheme of the 6th clutch shift element 36 as described in not comprising, between the input block 201 that the 5th clutch shift element 35 is serially connected in second power-transmitting unit 200 and the input block 1 of speed changer and the output block 202 of second power-transmitting unit 200 be connected with first rotary component 11 of first planetary gear set 10.
Described the 6th clutch shift element 36 be arranged on input power through described second power-transmitting unit 200 on the route that second rotary component 12 of described first planetary gear set 10 transmits, selectively described second power-transmitting unit 200 of ' connections/cut-outs ' process is to the power of second rotary component, 12 transmission of described first planetary gear set 10, embodiment is:
Perhaps as Fig. 1～3,7,12～15: between the output block 202 that the 6th clutch shift element 36 is serially connected in second power-transmitting unit 200 and second rotary component 12 of first planetary gear set 10 and the input block 201 of second power-transmitting unit 200 be connected with the input block 1 of speed changer
Perhaps as Fig. 8: in the scheme of the 5th clutch shift element 35 as described in not comprising, between the input block 201 that the 6th clutch shift element 36 is serially connected in second power-transmitting unit 200 and the input block 1 of speed changer and the output block 202 of second power-transmitting unit 200 be connected with second rotary component 12 of first planetary gear set 10.
Figure 17 is the general plotting of technological scheme two, Figure 16,18～26th, each embodiment 13～22 of technological scheme two; Wherein said the 3rd, the 5th, the 6th clutch shift element 33,35,36 be separately positioned on input power respectively through described first, second, third power-transmitting unit 100,200,300 respectively successively to the first star gear train 10 the 3rd, on the route that transmits of first, second rotary component 13,11,12, embodiment is:
Perhaps as Figure 18,20,21,23,25, the 26: the described the 3rd, the 5th, the 6th clutch shift element 33,35,36 are serially connected in described first respectively successively, second, the 3rd power-transmitting unit 100,200,300 separately output blocks 102,202, the 3rd of the 302 and first star gear train 10, first, second rotary component 13,11, between 12, and described first, second, the 3rd power-transmitting unit 100,200,300 separately input blocks 101,201,301 are connected with the input block 1 of speed changer
Perhaps as Figure 16,17,19,22, the 24: the described the 3rd, the 5th, the 6th clutch shift element 33,35,36 are serially connected in the input block 1 and described first of speed changer respectively successively, second, the 3rd power-transmitting unit 100,200,300 separately input blocks 101,201, between 301, and described first, second, the 3rd power-transmitting unit 100,200,300 separately output blocks 102,202,302 respectively successively with the 3rd of the first star gear train 10, first, second rotary component 13,11,12 are connected.
No matter technological scheme one still is each embodiment of technological scheme two, and described first, second clutch shift element 31,32 is serially connected in respectively between second, third rotary component 12,13 of second rotary component 22 of second planetary gear set 20 and described first planetary gear set 10 successively.The difference of two technological schemes is the annexation between described second, third power-transmitting unit 200,300 and described the 6th clutch shift element 36.In actual applications can also be as one or more two ends overrunning clutch in parallel of traditional speed changer in the middle of described the 4th, the 5th, the 6th clutch shift element 34,35,36, the frequent switching of gear-changing component during with the minimizing low vehicle speeds.Below specify each embodiment respectively.
Embodiment one: as Fig. 4, implement by technological scheme one; The transmission shaft that is connected with the input block 1 of speed changer constitutes described first power-transmitting unit 100; Described second power-transmitting unit 200 is made of a double-pinion type planetary gear set 120, output block 202, its planet carrier that input block 201, the gear ring that its sun gear constitutes second power-transmitting unit 200 constitutes second power-transmitting unit 200 are connected with case of transmission 5, and the gear ring of planetary gear set 120 and the input of speed changer 1 have fixing velocity ratio; Described first planetary gear set 10 is single pinion type planetary gear set 10_1, and its gear ring constitutes that first rotary component 11, sun gear constitute second rotary component 12, planet carrier constitutes the 3rd rotary component 13; Described second planetary gear set 20 is double-pinion type planetary gear set 20_1, and its planet carrier constitutes that first rotary component 21, sun gear constitute second rotary component 22, gear ring constitutes the 3rd rotary component 23; The shifting element of present embodiment comprises: first to the 5th clutch gear-shift element 31～35 does not comprise the 6th clutch gear-shift element 36; The gear ratio K value of the gear ring of each planetary gear set and sun gear just can obtain to have five forward gearss and reverse gear that ratio distributes between good gear ratio and shelves in the reasonable scope, below is gear table and corresponding number of teeth ratio:
K
10＝2.636，K
20＝2.333，K
120＝2.250
" ● " expression clutch shift combination of elements in the gear table, gear " R " is a reverse gear.
Embodiment two: as Fig. 5, be embodiment one branch diaxon setting type; The gear train that described first, second power-transmitting unit 100,200 each a pair of naturally intermeshing actives, driven gear constitute, described first, second power-transmitting unit 100,200 separately driving gear 105,205 or the coupling shaft of gear constitute first, second power-transmitting unit 100,200 input block 101,201 separately respectively, described first, second power-transmitting unit 100,200 separately driven gear 106,206 or the coupling shaft of gear constitute first, second power-transmitting unit 100,200 output block 102,202 separately respectively; Described first, second planetary gear set 10,20 and described first, second clutch gear-changing component 31,32 is identical with embodiment one, and be arranged in described driven gear 106, on 206 the axis, the described the 3rd, the 4th, the 5th clutch shift element 33,34,35 are arranged in described driving gear 105, on 205 the axis, the described the 3rd, the 5th clutch shift element 33,35 are serially connected in described driving gear 105 respectively, 205 and the input block 1 of speed changer between, described four clutches gear-changing component 34 is serially connected between described driving gear 105 and the case of transmission 5; Present embodiment is compared with embodiment one: increased by two external gear wheel groups, reduced by a planetary gear set, the element split axle is arranged, axial length significantly shortens, and is applicable to the vehicle of preposition forerunner, lateral arrangement speed changer.First, second planetary gear set 10,20 gear ratio K value is separately got the value identical with embodiment one: K
10=2.636, K
20=2.333, the gear ratio driven, driving gear of described first, second power-transmitting unit 100,200 is got respectively: Z
106/ Z
105=1.000, Z
206/ Z
205=2.250 can obtain the gear table identical with embodiment one.
Embodiment three: as Fig. 6, implement by technological scheme one; Described first, second power-transmitting unit 100,200 is identical with embodiment one; Described first planetary gear set 10 is double-pinion type planetary gear set 10_2, and its planet carrier constitutes that first rotary component 11, sun gear constitute second rotary component 12, gear ring constitutes the 3rd rotary component 13; Described second planetary gear set 20 is double-pinion type planetary gear set 20_2, and its planet carrier constitutes that first rotary component 21, sun gear constitute second rotary component 22, gear ring constitutes the 3rd rotary component 23; Each clutch shift element is also identical with embodiment one; Below get the gear table of suitable gear ratio for each planetary gear set:
K
10＝3.600，K
20＝2.333，K
120＝2.250
With reference to embodiment two, present embodiment can be changed to the setting type of branch diaxon equally.
Embodiment four: as Fig. 7, implement by technological scheme one; Described first power-transmitting unit 100 is made of a transmission shaft, described second power-transmitting unit 200 is made of a double-pinion type planetary gear set 121, its planet carrier constitutes the input block 201 of second power-transmitting unit 200, gear ring constitutes the output block 202 of second power-transmitting unit 200, its sun gear is connected with case of transmission 5, the transmission shaft that constitutes first power-transmitting unit 100 is actually input block 1 that connects speed changer and the transmission shaft that passes the planet carrier of planetary gear set 121, with the input block 201 of second power-transmitting unit 200 are same parts; Described first planetary gear set 10 is single pinion type planetary gear set 10_3, and its sun gear constitutes that first rotary component 11, planet carrier constitute second rotary component 12, gear ring constitutes the 3rd rotary component 13; Described second planetary gear set 20 is single pinion type planetary gear set 20_3, and its sun gear constitutes that first rotary component 21, planet carrier constitute second rotary component 22, gear ring constitutes the 3rd rotary component 23; Comprise first to fourth clutch shift element 33～34 and the 6th clutch shift element 36, and do not comprise the 5th clutch shift element that this point is different with embodiment one～three; Below get the gear table of suitable gear ratio for each planetary gear set:
K
10＝1.756，K
20＝4.000，K
120＝1.900
Embodiment five: as Fig. 8, be embodiment four branch diaxon setting type; The mode of similar embodiment two arranges that different is that the 6th clutch shift element 36 has replaced the 5th clutch shift element; First, second planetary gear set 10,20 gear ratio K value is separately got the value identical with embodiment four: K
10=1.756, K
20=4.000, the gear ratio driven, driving gear of described first, second power-transmitting unit 100,200 is got respectively: Z
106/ Z
105=1.000, Z
206/ Z
205=1.900 can obtain the gear table identical with embodiment four.
Embodiment six: as Fig. 9, implement by technological scheme one; Described first, second power-transmitting unit 100,200 is identical with embodiment one; Described first planetary gear set 10 is single pinion type planetary gear set 10_4, and its gear ring constitutes that first rotary component 11, planet carrier constitute second rotary component 12, sun gear constitutes the 3rd rotary component 13; Described second planetary gear set 20 is single pinion type planetary gear set 20_4, and its sun gear constitutes that first rotary component 21, planet carrier constitute second rotary component 22, gear ring constitutes the 3rd rotary component 23; Each clutch shift element is also identical with embodiment one; Below get the gear table of suitable gear ratio for each planetary gear set:
K
10＝2.636，K
20＝1.919，K
120＝2.290
First, second planetary gear set 10,20 all is single pinion type planetary gear set described in the present embodiment, and the value of their gear ratio K value is moderate, so present embodiment is preferable embodiment, makes easily and miniaturization.
The gear-changing component marriage relation of each gear and embodiment one～three are different in the present embodiment, need to prove gear among the present invention with the marriage relation of gear-changing component be and each rotary component of planetary gear set between speed ratio arrange even relevant with the gear ratio K value of planetary gear set, so different concrete enforcement has different gears and gear-changing component marriage relation.
Embodiment seven: as Figure 10, be embodiment six branch diaxon setting type; The mode of similar embodiment two is arranged; First, second planetary gear set 10,20 gear ratio K value is separately got the value identical with embodiment six: K
10=2.636, K
20=1.919, the gear ratio driven, driving gear of described first, second power-transmitting unit 100,200 is got respectively: Z
106/ Z
105=1.000, Z
206/ Z
205=2.290 can obtain the gear table identical with embodiment six.Present embodiment and embodiment six be equally preferable, make and the embodiment of miniaturization easily.
Embodiment eight: as Figure 11, implement by technological scheme one; Described first, second power-transmitting unit 100,200 is identical with embodiment one; Described first planetary gear set 10 is single pinion type planetary gear set 10_5, and its gear ring constitutes that first rotary component 11, planet carrier constitute second rotary component 12, sun gear constitutes the 3rd rotary component 13; Described second planetary gear set 20 is double-pinion type planetary gear set 20_5, and its sun gear constitutes that first rotary component 21, gear ring constitute second rotary component 22, planet carrier constitutes the 3rd rotary component 23; Each clutch shift element is also identical with embodiment one; Below get the gear table of suitable gear ratio for each planetary gear set:
K
10＝2.636，K
20＝3.000，K
120＝2.333
With reference to embodiment two, present embodiment can be changed to the setting type of branch diaxon equally.
Embodiment nine: as Figure 12, implement by technological scheme one; Described first, second power-transmitting unit 100,200 is identical with embodiment one; Described first planetary gear set 10 is double-pinion type planetary gear set 10_6, and its sun gear constitutes that first rotary component 11, planet carrier constitute second rotary component 12, gear ring constitutes the 3rd rotary component 13; Described second planetary gear set 20 is single pinion type planetary gear set 20_6, and its gear ring constitutes that first rotary component 21, sun gear constitute second rotary component 22, planet carrier constitutes the 3rd rotary component 23; Comprise six gear-changing components: first to the 6th clutch shift element 33～36; The gear ratio K value of each planetary gear set just can obtain to have eight forward gearss and two reverse gear that ratio distributes between good gear ratio and shelves in the reasonable scope, below is gear table and corresponding number of teeth ratio:
K
10＝2.212，K
20＝1.971，K
120＝2.176
Embodiment ten: as Figure 13, be embodiment nine branch diaxon setting type; Described first, second power-transmitting unit 100,200 is similar to embodiment two; Described first, second planetary gear set 10,20 and described first, second, the 5th, the 6th clutch shift element 31,32,35,36 is identical with embodiment nine, and be arranged on the axis of described driven gear 106,206, described the 3rd, four clutches gear-changing component 33,34 is arranged on the axis of described driving gear 105,205, described three-clutch gear-changing component 33 is serially connected between the input block 1 of described driving gear 105 and speed changer, and described four clutches gear-changing component 34 is serially connected between described driving gear 105 and the case of transmission 5; First, second planetary gear set 10,20 gear ratio K value is separately got the value identical with embodiment nine: K
10=2.212, K
20=1.971, the gear ratio driven, driving gear of described first, second power-transmitting unit 100,200 is got respectively: Z
106/ Z
105=1.000, Z
206/ Z
205=2.176 can obtain the gear table identical with embodiment nine.
Also can more shifting element be arranged on the driving shaft, further shorten axial distance with reference to embodiment's 13 modes.
Embodiment 11: as Figure 14, implement by technological scheme one; Described first, second power-transmitting unit 100,200 is identical with embodiment one; Described first planetary gear set 10 is double-pinion type planetary gear set 10_7, and its sun gear constitutes that first rotary component 11, planet carrier constitute second rotary component 12, gear ring constitutes the 3rd rotary component 13; Described second planetary gear set 20 is double-pinion type planetary gear set 20_7, and its planet carrier constitutes that first rotary component 21, sun gear constitute second rotary component 22, gear ring constitutes the 3rd rotary component 23; Gear-changing component is all identical with embodiment nine with gear quantity in the present embodiment; Below get the gear table of suitable gear ratio for each planetary gear set:
K
10＝2.212，K
20＝3.000，K
120＝2.059
With reference to embodiment ten, embodiment 13, present embodiment can be changed to the setting type of branch diaxon equally.
Embodiment 12: as Figure 15, implement by technological scheme one; Described first, second power-transmitting unit 100,200 is identical with embodiment one; Described first planetary gear set 10 is double-pinion type planetary gear set 10_8, and its planet carrier constitutes that first rotary component 11, gear ring constitute second rotary component 12, sun gear constitutes the 3rd rotary component 13; Described second planetary gear set 20 is single pinion type planetary gear set 20_8, and its sun gear constitutes that first rotary component 21, planet carrier constitute second rotary component 22, gear ring constitutes the 3rd rotary component 23; Gear-changing component is all identical with embodiment nine with gear quantity in the present embodiment; Below get the gear table of suitable gear ratio for each planetary gear set:
K
10＝2.333，K
20＝2.308，K
120＝2.067
With reference to embodiment ten, embodiment 13, present embodiment can be changed to the setting type of branch diaxon equally.
Embodiment 13: as Figure 16, be embodiment 12 branch diaxon setting type; Different with embodiment ten is that present embodiment has increased by an external gear wheel group 300, the 3rd power-transmitting unit 300 in its corresponding technological scheme two, its driven gear 306 connects second rotary component 12 of second planetary gear set 10, is connected in series described the 6th clutch shift element 36 between the input block 1 of its driving gear 305 and speed changer; The driven gear 106,206 of first, second power-transmitting unit 100,200 connects the 3rd, first rotary component 13,11 of first planetary gear set 10 respectively successively, is connected in series described the 3rd, the 5th clutch shift element 33,35 respectively between the input block 1 of driving gear 105,205 and speed changer; First, second planetary gear set 10,20 and first, second clutch shift element 31,32 are identical with embodiment 12, and be arranged on the axis of described driven gear 106,206,306, the 3rd, the 5th, the 6th clutch shift element 33,35,36 is arranged on the axis of described driving gear 105,205,305; Four clutches gear-changing component 34 both can be arranged on the axis of described driven tooth according to Figure 16, also can be arranged on the axis of described driving tooth as embodiment two.Present embodiment also can be regarded as increases four clutches gear-changing component 34 mode of executions on the basis of technological scheme two, though it is slightly more complicated than embodiment ten, but more shifting element is arranged on the driving shaft, more help shortening axial length, and can obtain ratio distribution between extraordinary gear ratio and shelves:
K
10＝2.333，K
20＝2.308，Z
106/Z
105＝1.000，Z
206/Z
205＝2.000，Z
306/Z
305＝2.214
Embodiment 14: as Figure 18, implement by technological scheme two; Described first, the 3rd power-transmitting unit 100,300 constitute by a double-pinion type planetary gear set 131 and a single pinion type planetary gear set 132 are mutually compound, the sun gear of described double-pinion type planetary gear set 131 constitutes first, the 3rd power-transmitting unit 100,300 common input blocks 101,301, the gear ring of described double-pinion type planetary gear set 131 is connected with the planet carrier of described single pinion type planetary gear set 132, and constitute the output block 102 of first power-transmitting unit 100, the sun gear of described single pinion type planetary gear set 132 constitutes the output block 302 of the 3rd power-transmitting unit 300, and the gear ring of the planet carrier of described double-pinion type planetary gear set 131 and described single pinion type planetary gear set 132 is connected with case of transmission 5; Described second power-transmitting unit 200 is transmission shafts that are connected with speed changer input block 1; Described first planetary gear set 10 is double-pinion type planetary gear set 10_9, and its sun gear constitutes that first rotary component 11, planet carrier constitute second rotary component 12, gear ring constitutes the 3rd rotary component 13; Described second planetary gear set 20 is double-pinion type planetary gear set 20_9, and its sun gear constitutes that first rotary component 21, planet carrier constitute second rotary component 22, gear ring constitutes the 3rd rotary component 23; Comprise five gear-changing components: the 5th, the 6th clutch shift element 31,32,33,35,36 first, second, third; They connect according to technological scheme two; Present embodiment comprises four planetary gear set and five gear-changing components; The gear ratio K value of each planetary gear set can obtain eight forward gearss and a reverse gear in the reasonable scope, below is gear table and corresponding number of teeth ratio:
K
10＝2.429，K
20＝2.143，K
131＝2.429，K
132＝3.200
The embodiment of all technological schemes two, each gear only two gear-changing components separates, and the slip loss of gear-changing component is very little.
Embodiment 15: as Figure 19, be embodiment 14 branch diaxon setting type; Described first, the second and the 3rd power-transmitting unit 100,200,300 each a pair of naturally intermeshing active, the gear train that driven gear constitutes, described first, the second and the 3rd power-transmitting unit 100,200,300 separately driving gears 105,205,305 or the coupling shaft of gear constitute first respectively, the second and the 3rd power-transmitting unit 100,200,300 separately input blocks 101,201,301, described first, the second and the 3rd power-transmitting unit 100,200,300 separately driven gears 106,206,306 or the coupling shaft of gear constitute first respectively, the second and the 3rd power-transmitting unit 100,200,300 separately output blocks 102,202,302; Described first, second planetary gear set 10,20 and described first, second clutch shift element 31,32 are identical with embodiment 14, and be arranged on the axis of described driven gear, described the 3rd, the 5th, the 6th clutch shift element 33,35,36 is arranged on the axis of described driving gear, and is serially connected in successively respectively between described first, second and the 3rd power-transmitting unit 100,200,300 driving gear 105,205,305 and the input block 1 of speed changer separately; Present embodiment is compared with embodiment 14 and has been reduced by two planetary gear set, increased by three external tooth wheels, three gear-changing components are arranged on another axis, has shortened the axial length of speed changer, is applicable to the vehicle of preposition forerunner, lateral arrangement speed changer.Below get the gear table of suitable gear ratio for each gear train:
K
10＝2.429，K
20＝2.143，Z
106/Z
105＝2.429，Z
206/Z
205＝1.000，Z
306/Z
305＝0.588
Embodiment 16: very similar to embodiment 14 as Figure 20, the planet carrier of described second planetary gear set 20 that different is is that first rotary component 21, sun gear are second rotary component 22.Below get the gear table of suitable gear ratio for each gear train:
K
10＝2.429，K
20＝1.870，K
131＝2.429，K
132＝3.200
With reference to embodiment 15, present embodiment can be changed to the setting type of branch diaxon equally.
Embodiment's 14,15,16 specializations are that they all have three overdirve gears.
Embodiment 17: as Figure 21, implement by technological scheme two; Described first power-transmitting unit 100 is transmission shafts that are connected with speed changer input block 1; Described second, the 3rd power-transmitting unit 200,300 constitute by a double-pinion type planetary gear set 231 and a single pinion type planetary gear set 232 are mutually compound, the sun gear of described double-pinion type planetary gear set 231 constitutes second, the 3rd power-transmitting unit 200,300 common input blocks 201,301, the gear ring of described double-pinion type planetary gear set 231 is connected with the sun gear of described single pinion type planetary gear set 232, and constitute the output block 202 of second power-transmitting unit 200, the gear ring of described single pinion type planetary gear set 232 constitutes the output block 302 of the 3rd power-transmitting unit 300, and the planet carrier of described double-pinion type planetary gear set 231 is connected with the planet carrier of described single pinion type planetary gear set 232, and be connected with case of transmission 5; Described first planetary gear set 10 is double-pinion type planetary gear set 10_11, and its sun gear constitutes that first rotary component 11, planet carrier constitute second rotary component 12, gear ring constitutes the 3rd rotary component 13; Described second planetary gear set 20 is single pinion type planetary gear set 20_11, and its gear ring constitutes that first rotary component 21, sun gear constitute second rotary component 22, planet carrier constitutes the 3rd rotary component 23; Comprise five gear-changing components: the 5th, the 6th clutch shift element 31,32,33,35,36 first, second, third; They connect according to technological scheme two; Present embodiment comprises four planetary gear set and five gear-changing components; The gear ratio K value of each planetary gear set can obtain eight forward gearss and a reverse gear in the reasonable scope, below is gear table and corresponding number of teeth ratio:
K
10＝1.692，K
20＝2.846，K
231＝2.600，K
232＝1.756
Embodiment 18: as Figure 22, be embodiment 17 branch diaxon setting type; Described first, second power-transmitting unit 100,200 each a pair of naturally intermeshing active, the gear train that driven gear constitutes, described the 3rd power-transmitting unit 300 is the driving gears 305 that are meshed successively, idle pulley 340, driven gear 306 constitutes gear train, described first, the second and the 3rd power-transmitting unit 100,200,300 separately driving gears 105,205,305 or the coupling shaft of gear constitute first respectively, the second and the 3rd power-transmitting unit 100,200,300 separately input blocks 101,201,301, described first, the second and the 3rd power-transmitting unit 100,200,300 separately driven gears 106,206,306 or the coupling shaft of gear constitute first respectively, the second and the 3rd power-transmitting unit 100,200,300 separately output blocks 102,202,302; Described first, second planetary gear set 10,20 and described first, second clutch shift element 31,32 are identical with embodiment 17, and be arranged on the axis of described driven gear, described the 3rd, the 5th, the 6th clutch shift element 33,35,36 is arranged on the axis of described driving gear, and is serially connected in respectively between described first, second and the 3rd power-transmitting unit 100,200,300 driving gear 105,205,305 and the input block 1 of speed changer separately; Present embodiment has reduced by two planetary gear set, increased by three external tooth wheels, three gear-changing components has been moved on on another axis, and the axial length of speed changer shortens, and is applicable to the vehicle of preposition forerunner, lateral arrangement speed changer.Present embodiment and embodiment's 15 difference is the driving and driven gear the 305, the 306th of described the 3rd power-transmitting unit 300, idle pulley 340 transferring power by the centre, therefore the driven gear 306 of the 3rd power-transmitting unit 300 is opposite with the sense of rotation of the driven gear 106,206 of other two power transmission mechanisms.Below get the gear table of suitable gear ratio for each gear train:
K
10＝1.692，K
20＝2.846，Z
106/Z
105＝1.000，Z
206/Z
205＝2.600，Z
306/Z
305＝4.600
Embodiment 19: as Figure 23, implement by technological scheme two; Described first power-transmitting unit 100 is transmission shafts that are connected with speed changer input block 1; The described second and the 3rd power-transmitting unit 200,300 are single pinion type planetary gear set by two: pre-planetary gear group 233 and back planetary gear set 234 mutually compound formations, the sun gear of described pre-planetary gear group 233 constitutes second, the 3rd power-transmitting unit 200,300 common input blocks 201,301, the gear ring of described back planetary gear set 234 constitutes the output block 202 of second power-transmitting unit 200, the planet carrier of described pre-planetary gear group 233 is connected with the planet carrier of described back planetary gear set 234, and constituting the output block 302 of the 3rd power-transmitting unit 300, the gear ring of described pre-planetary gear group 233 is connected with the sun gear of described back planetary gear set 234, and be connected with case of transmission 5; Described first planetary gear set 10 is single pinion type planetary gear set 10_12, and its gear ring constitutes that first rotary component 11, planet carrier constitute second rotary component 12, sun gear constitutes the 3rd rotary component 13; Described second planetary gear set 20 is single pinion type planetary gear set 20_12, and its sun gear constitutes that first rotary component 21, planet carrier constitute second rotary component 22, gear ring constitutes the 3rd rotary component 23; Comprise five gear-changing components: the 5th, the 6th clutch shift element 31,32,33,35,36 first, second, third; They connect according to technological scheme two; Present embodiment is compared with embodiment six: first, second planetary gear set 10,20, the first, second, third, the 5th clutch shift element 31,32,33,35 and their connection arrangement are all identical, are that the version that reduces four clutches gear-changing component 34, increase the 6th clutch shift element 36 and replace second power-transmitting unit is gone up on embodiment six bases;
Present embodiment comprises four planetary gear set and five gear-changing components; The gear ratio K value of each planetary gear set can obtain forward gears and reverse gear of seven practicalities in the reasonable scope, below is gear table and corresponding number of teeth ratio:
K
10＝2.286，K
20＝1.667，K
233＝1.971，K
234＝2.259
Shelves before present embodiment in fact also has eight, but one of them gear needs to switch two pairs of gear-changing components with adjacent shelves, and general the application only used seven gears that only switch a pair of gear-changing component between wherein adjacent shelves; All planetary gear set all are single pinion type planetary gear set in the present embodiment, and the value of their gear ratio K value is more moderate, and are also more suitable than distributing between shelves, so present embodiment is preferable embodiment, make easily and miniaturization.
Embodiment 20: as Figure 24, be embodiment 19 branch diaxon setting type; Layout and Placement that described first, second, third power-transmitting unit 100,200,300, the 3rd, the 5th, the 6th clutch shift element 33,35,36 and embodiment 15 are similar; Described first, second planetary gear set 10,20 and described first, second clutch shift element 31,32 are identical with embodiment 19, and are arranged on the axis of described driven gear; With embodiment 19 forward gears and a reverse gear of seven practicalities being arranged equally, below is gear table and corresponding number of teeth ratio:
K
10＝2.286，K
20＝1.667，Z
106/Z
105＝1.000，Z
206/Z
205＝2.083，Z
306/Z
305＝2.971
Present embodiment has only two single pinion type planetary gear set, with embodiment 19 be equally preferable, make and the embodiment of miniaturization easily.
Embodiment 21: as Figure 25, implement by technological scheme two; Very similar to embodiment 19, different is that described second planetary gear set 20 is double-pinion type planetary gear set 20_13, and its sun gear constitutes that first rotary component 21, gear ring constitute second rotary component 22, planet carrier constitutes the 3rd rotary component 23; Below be gear table and corresponding number of teeth ratio:
K
10＝2.286，K
20＝2.600，K
233＝1.971，K
234＝2.259
With reference to embodiment 20, present embodiment can be changed to the setting type of branch diaxon equally.
Embodiment 22: as Figure 26, implement by technological scheme two; Described first power-transmitting unit 100 is transmission shafts that are connected with speed changer input block 1; Described second, the 3rd power-transmitting unit 200,300 are single pinion type planetary gear set by two: pre-planetary gear group 235 and back planetary gear set 236 mutually compound formations, the sun gear of described back planetary gear set 236 constitutes second, the 3rd power-transmitting unit 200,300 common input blocks 201,301, the gear ring of described pre-planetary gear group 235 is connected with the planet carrier of described back planetary gear set 236, and constitute the output block 202 of second power-transmitting unit 200, the planet carrier of described pre-planetary gear group 235 is connected with the gear ring of described back planetary gear set 236, and constituting the output block 302 of the 3rd power-transmitting unit 300, the sun gear of described pre-planetary gear group 235 is connected with case of transmission (5); Described first planetary gear set 10 is double-pinion type planetary gear set 10_14, and its planet carrier constitutes that first rotary component 11, gear ring constitute second rotary component 12, sun gear constitutes the 3rd rotary component 13; Described second planetary gear set 20 is single pinion type planetary gear set 20_14, and its sun gear constitutes that first rotary component 21, planet carrier constitute second rotary component 22, gear ring constitutes the 3rd rotary component 23; Comprise five gear-changing components: the 5th, the 6th clutch shift element 31,32,33,35,36 first, second, third; They connect according to technological scheme two; Present embodiment comprises four planetary gear set and five gear-changing components; With embodiment 19 forward gears and a reverse gear of seven practicalities being arranged equally, below is gear table and corresponding number of teeth ratio:
K
10＝2.286，K
20＝1.667，K
235＝2.097，K
236＝3.200
With reference to embodiment 20, present embodiment can be changed to the setting type of branch diaxon equally.
Claims (25)
1. multiple-speed gear-box comprises speed changer input block (1), speed changer output block (2), preposition first and second power-transmitting units (100,200), first and second planetary gear set (10,20), first to fourth clutch shift element (31,32,33,34), also comprises the the 5th (35) or the 6th (36) clutch shift element or comprise the the 5th (35) and the 6th (36) clutch shift element simultaneously; It is characterized in that: described first, second power-transmitting unit (100,200) has input block (101,201) and output block separately (102,202) separately; Described first planetary gear set (10) has first, second and the 3rd rotary component (11,12,13), and described second planetary gear set (20) has first, second and the 3rd rotary component (21,22,23);
The 3rd rotary component (23) of described second planetary gear set (20) is connected with described speed changer output block (2), described first, second planetary gear set (10,20) first rotary component (11 separately, 21) interconnect, described first clutch gear-changing component (31) is serially connected between second rotary component (22) of second rotary component (12) of described first planetary gear set (10) and described second planetary gear set (20), and described second clutch gear-changing component (32) is serially connected between second rotary component (22) of the 3rd rotary component (13) of described first planetary gear set (10) and described second planetary gear set (20); Input power is imported from speed changer input block (1);
Described three-clutch gear-changing component (33) be arranged on input power through described first power-transmitting unit (100) on the route that the 3rd rotary component (13) of described first planetary gear set (10) transmits, selectively ' connections/cut-outs ' through the power of described first power-transmitting unit (100) to the 3rd rotary component (13) transmission of described first planetary gear set (10), described four clutches gear-changing component (34) selectively makes the 3rd rotary component (13) of described first planetary gear set (10) brake;
Described the 5th clutch shift element (35) be arranged on input power through described second power-transmitting unit (200) on the route that first rotary component (11) of described first planetary gear set (10) transmits, selectively ' connections/cut-outs ' described second power-transmitting unit of process (200) is to the power of first rotary component (11) transmission of described first planetary gear set (10);
Described the 6th clutch shift element (36) be arranged on input power through described second power-transmitting unit (200) on the route that second rotary component (12) of described first planetary gear set (10) transmits, selectively ' connections/cut-outs ' described second power-transmitting unit of process (200) is to the power of second rotary component (12) transmission of described first planetary gear set (10).
2. multiple-speed gear-box according to claim 1 is characterized in that: described first power-transmitting unit (100) is made of a transmission shaft, and its front and back ends constitutes input, the output block (101,102) of first power-transmitting unit (100) respectively; Described second power-transmitting unit (200) is made of a double-pinion type planetary gear set (120), and its sun gear constitutes the input block (201) of second power-transmitting unit (200), output block (202), its planet carrier that gear ring constitutes second power-transmitting unit (200) is connected with case of transmission (5).
3. multiple-speed gear-box according to claim 1, it is characterized in that: described first, second power-transmitting unit (100,200) each a pair of naturally intermeshing active, the gear train that driven gear constitutes, described first, second power-transmitting unit (100,200) driving gear (105 separately, 205) or the coupling shaft of gear constitute first respectively, second power-transmitting unit (100,200) input block (101 separately, 201), described first, second power-transmitting unit (100,200) driven gear (106 separately, 206) or the coupling shaft of gear constitute first respectively, second power-transmitting unit (100,200) output block (102 separately, 202).
4. multiple-speed gear-box according to claim 1 is characterized in that: described first power-transmitting unit (100) is made of a transmission shaft, and its front and back ends constitutes input, the output block (101,102) of first power-transmitting unit (100) respectively; Described second power-transmitting unit (200) is made of a double-pinion type planetary gear set (121), and its planet carrier constitutes the input block (201) of second power-transmitting unit (200), output block (202), its sun gear that gear ring constitutes second power-transmitting unit (200) is connected with case of transmission (5).
5. according to claim 1,2 or 3 described multiple-speed gear-boxes, it is characterized in that: described first planetary gear set (10) is single pinion type planetary gear set (10_1), and its gear ring constitutes that first rotary component (11), sun gear constitute second rotary component (12), planet carrier constitutes the 3rd rotary component (13); Described second planetary gear set (20) is double-pinion type planetary gear set (20_1), and its planet carrier constitutes that first rotary component (21), sun gear constitute second rotary component (22), gear ring constitutes the 3rd rotary component (23).
6. according to claim 1,2 or 3 described multiple-speed gear-boxes, it is characterized in that: described first planetary gear set (10) is double-pinion type planetary gear set (10_2), and its planet carrier constitutes that first rotary component (11), sun gear constitute second rotary component (12), gear ring constitutes the 3rd rotary component (13); Described second planetary gear set (20) is double-pinion type planetary gear set (20_2), and its planet carrier constitutes that first rotary component (21), sun gear constitute second rotary component (22), gear ring constitutes the 3rd rotary component (23).
7. according to claim 1,2 or 4 described multiple-speed gear-boxes, it is characterized in that: described first planetary gear set (10) is single pinion type planetary gear set (10_3), and its sun gear constitutes that first rotary component (11), planet carrier constitute second rotary component (12), gear ring constitutes the 3rd rotary component (13); Described second planetary gear set (20) is single pinion type planetary gear set (20_3), and its sun gear constitutes that first rotary component (21), planet carrier constitute second rotary component (22), gear ring constitutes the 3rd rotary component (23).
8. according to claim 1,2 or 3 described multiple-speed gear-boxes, it is characterized in that: described first planetary gear set (10) is single pinion type planetary gear set (10_4), and its gear ring constitutes that first rotary component (11), planet carrier constitute second rotary component (12), sun gear constitutes the 3rd rotary component (13); Described second planetary gear set (20) is single pinion type planetary gear set (20_4), and its sun gear constitutes that first rotary component (21), planet carrier constitute second rotary component (22), gear ring constitutes the 3rd rotary component (23).
9. according to claim 1,2 or 3 described multiple-speed gear-boxes, it is characterized in that: described first planetary gear set (10) is single pinion type planetary gear set (10_5), and its gear ring constitutes that first rotary component (11), planet carrier constitute second rotary component (12), sun gear constitutes the 3rd rotary component (13); Described second planetary gear set (20) is double-pinion type planetary gear set (20_5), and its sun gear constitutes that first rotary component (21), gear ring constitute second rotary component (22), planet carrier constitutes the 3rd rotary component (23).
10. according to claim 1,2 or 3 described multiple-speed gear-boxes, it is characterized in that: described first planetary gear set (10) is double-pinion type planetary gear set (10_6), and its sun gear constitutes that first rotary component (11), planet carrier constitute second rotary component (12), gear ring constitutes the 3rd rotary component (13); Described second planetary gear set (20) is single pinion type planetary gear set (20_6), and its gear ring constitutes that first rotary component (21), sun gear constitute second rotary component (22), planet carrier constitutes the 3rd rotary component (23).
11. according to claim 1,2 or 3 described multiple-speed gear-boxes, it is characterized in that: described first planetary gear set (10) is double-pinion type planetary gear set (10_7), and its sun gear constitutes that first rotary component (11), planet carrier constitute second rotary component (12), gear ring constitutes the 3rd rotary component (13); Described second planetary gear set (20) is double-pinion type planetary gear set (20_7), and its planet carrier constitutes that first rotary component (21), sun gear constitute second rotary component (22), gear ring constitutes the 3rd rotary component (23).
12. according to claim 1,2 or 3 described multiple-speed gear-boxes, it is characterized in that: described first planetary gear set (10) is double-pinion type planetary gear set (10_8), and its planet carrier constitutes that first rotary component (11), gear ring constitute second rotary component (12), sun gear constitutes the 3rd rotary component (13); Described second planetary gear set (20) is single pinion type planetary gear set (20_8), and its sun gear constitutes that first rotary component (21), planet carrier constitute second rotary component (22), gear ring constitutes the 3rd rotary component (23).
13. a multiple-speed gear-box comprises that speed changer input block (1), speed changer output block (2), preposition first, second and the 3rd power-transmitting unit (100,200,300), first and second planetary gear set (10,20), five clutch shift elements are respectively the first, second, third, the 5th and the 6th clutch shift element (31,32,33,35,36); It is characterized in that: described first, second, third power-transmitting unit (100,200,300) has input block (101,201,301) and output block separately (102,202,302) separately; Described first planetary gear set (10) has first, second and the 3rd rotary component (11,12,13), and described second planetary gear set (20) has first, second and the 3rd rotary component (21,22,23);
The 3rd rotary component (23) of described second planetary gear set (20) is connected with described speed changer output block (2), described first, second planetary gear set (10,20) first rotary component (11 separately, 21) interconnect, described first clutch gear-changing component (31) is serially connected between second rotary component (22) of second rotary component (12) of described first planetary gear set (10) and described second planetary gear set (20), and described second clutch gear-changing component (32) is serially connected between second rotary component (22) of the 3rd rotary component (13) of described first planetary gear set (10) and described second planetary gear set (20); Input power is imported from speed changer input block (1);
Described three-clutch gear-changing component (33) be arranged on input power through described first power-transmitting unit (100) on the route that the 3rd rotary component (13) of described first planetary gear set (10) transmits, selectively ' connections/cut-outs ' described first power-transmitting unit of process (100) is to the power of the 3rd rotary component (13) transmission of described first planetary gear set (10);
Described the 5th clutch shift element (35) be arranged on input power through described second power-transmitting unit (200) on the route that first rotary component (11) of described first planetary gear set (10) transmits, selectively ' connections/cut-outs ' described second power-transmitting unit of process (200) is to the power of first rotary component (11) transmission of described first planetary gear set (10);
Described the 6th clutch shift element (36) be arranged on input power through described the 3rd power-transmitting unit (300) on the route that second rotary component (12) of described first planetary gear set (10) transmits, selectively ' connections/cut-outs ' described the 3rd power-transmitting unit of process (300) is to the power of second rotary component (12) transmission of described first planetary gear set (10).
14. multiple-speed gear-box according to claim 13, it is characterized in that: the described first and the 3rd power-transmitting unit (100,300) by a double-pinion type planetary gear set (131) and the mutually compound formation of a single pinion type planetary gear set (132), the sun gear of described double-pinion type planetary gear set (131) constitutes first, the 3rd power-transmitting unit (100,300) common input block (101,301), the gear ring of described double-pinion type planetary gear set (131) is connected with the planet carrier of described single pinion type planetary gear set (132), and constitute the output block (102) of first power-transmitting unit (100), the sun gear of described single pinion type planetary gear set (132) constitutes the output block (302) of the 3rd power-transmitting unit (300), and the gear ring of the planet carrier of described double-pinion type planetary gear set (131) and described single pinion type planetary gear set (132) is connected with case of transmission (5); Described second power-transmitting unit (200) is made of a transmission shaft, and its front and back ends constitutes input, the output block (201,202) of second power-transmitting unit (200) respectively.
15. multiple-speed gear-box according to claim 13 is characterized in that: described first power-transmitting unit (100) is made of a transmission shaft, and its front and back ends constitutes input, the output block (101,102) of first power-transmitting unit (100) respectively; The described second and the 3rd power-transmitting unit (200,300) by a double-pinion type planetary gear set (231) and the mutually compound formation of a single pinion type planetary gear set (232), the sun gear of described double-pinion type planetary gear set (231) constitutes second, the 3rd power-transmitting unit (200,300) common input block (201,301), the gear ring of described double-pinion type planetary gear set (231) is connected with the sun gear of described single pinion type planetary gear set (232), and constitute the output block (202) of second power-transmitting unit (200), the gear ring of described single pinion type planetary gear set (232) constitutes the output block (302) of the 3rd power-transmitting unit (300), and the planet carrier of described double-pinion type planetary gear set (231) is connected with the planet carrier of described single pinion type planetary gear set (232), and be connected with case of transmission (5).
16. multiple-speed gear-box according to claim 13 is characterized in that: described first power-transmitting unit (100) is made of a transmission shaft, and its front and back ends constitutes input, the output block (101,102) of first power-transmitting unit (100) respectively; The described second and the 3rd power-transmitting unit (200,300) be single pinion type planetary gear set by two: pre-planetary gear group (233) and the mutually compound formation of back planetary gear set (234), the sun gear of described pre-planetary gear group (233) constitutes second, the 3rd power-transmitting unit (200,300) common input block (201,301), the gear ring of described back planetary gear set (234) constitutes the output block (202) of second power-transmitting unit (200), the planet carrier of described pre-planetary gear group (233) is connected with the planet carrier of described back planetary gear set (234), and constituting the output block (302) of the 3rd power-transmitting unit (300), the gear ring of described pre-planetary gear group (233) is connected with the sun gear of described back planetary gear set (234), and be connected with case of transmission (5).
17. multiple-speed gear-box according to claim 13 is characterized in that: described first power-transmitting unit (100) is made of a transmission shaft, and its front and back ends constitutes input, the output block (101,102) of first power-transmitting unit (100) respectively; The described second and the 3rd power-transmitting unit (200,300) be single pinion type planetary gear set by two: pre-planetary gear group (235) and the mutually compound formation of back planetary gear set (236), the sun gear of described back planetary gear set (236) constitutes second, the 3rd power-transmitting unit (200,300) common input block (201,301), the gear ring of described pre-planetary gear group (235) is connected with the planet carrier of described back planetary gear set (236), and constitute the output block (202) of second power-transmitting unit (200), the planet carrier of described pre-planetary gear group (235) is connected with the gear ring of described back planetary gear set (236), and constituting the output block (302) of the 3rd power-transmitting unit (300), the sun gear of described pre-planetary gear group (235) is connected with case of transmission (5).
18. multiple-speed gear-box according to claim 13, it is characterized in that: described first, the second and the 3rd power-transmitting unit (100,200,300) each a pair of naturally intermeshing active, the gear train that driven gear constitutes, described first, the second and the 3rd power-transmitting unit (100,200,300) driving gear (105 separately, 205,305) or the coupling shaft of gear constitute first respectively, the second and the 3rd power-transmitting unit (100,200,300) input block (101 separately, 201,301), described first, the second and the 3rd power-transmitting unit (100,200,300) driven gear (106 separately, 206,306) or the coupling shaft of gear constitute first respectively, the second and the 3rd power-transmitting unit (100,200,300) output block (102 separately, 202,302).
19. multiple-speed gear-box according to claim 13, it is characterized in that: described first, second power-transmitting unit (100,200) each a pair of naturally intermeshing active, the gear train that driven gear constitutes, described the 3rd power-transmitting unit (300) is the driving gear (305) that is meshed successively, idle pulley (340), driven gear (306) constitutes gear train, described first, the second and the 3rd power-transmitting unit (100,200,300) driving gear (105 separately, 205,305) or the coupling shaft of gear constitute first respectively, the second and the 3rd power-transmitting unit (100,200,300) input block (101 separately, 201,301), described first, the second and the 3rd power-transmitting unit (100,200,300) driven gear (106 separately, 206,306) or the coupling shaft of gear constitute first respectively, the second and the 3rd power-transmitting unit (100,200,300) output block (102 separately, 202,302).
20. according to claim 13,14 or 18 described multiple-speed gear-boxes, it is characterized in that: described first planetary gear set (10) is double-pinion type planetary gear set (10_9), and its sun gear constitutes that first rotary component (11), planet carrier constitute second rotary component (12), gear ring constitutes the 3rd rotary component (13); Described second planetary gear set (20) is double-pinion type planetary gear set (20_9), and its sun gear constitutes that first rotary component (21), planet carrier constitute second rotary component (22), gear ring constitutes the 3rd rotary component (23).
21. according to claim 13,14 or 18 described multiple-speed gear-boxes, it is characterized in that: described first planetary gear set (10) is double-pinion type planetary gear set (10_10), and its sun gear constitutes that first rotary component (11), planet carrier constitute second rotary component (12), gear ring constitutes the 3rd rotary component (13); Described second planetary gear set (20) is double-pinion type planetary gear set (20_10), and its planet carrier constitutes that first rotary component (21), sun gear constitute second rotary component (22), gear ring constitutes the 3rd rotary component (23).
22. according to claim 13,15 or 19 described multiple-speed gear-boxes, it is characterized in that: described first planetary gear set (10) is double-pinion type planetary gear set (10_11), and its sun gear constitutes that first rotary component (11), planet carrier constitute second rotary component (12), gear ring constitutes the 3rd rotary component (13); Described second planetary gear set (20) is single pinion type planetary gear set (20_11), and its gear ring constitutes that first rotary component (21), sun gear constitute second rotary component (22), planet carrier constitutes the 3rd rotary component (23).
23. according to claim 13,16 or 18 described multiple-speed gear-boxes, it is characterized in that: described first planetary gear set (10) is single pinion type planetary gear set (10_12), and its gear ring constitutes that first rotary component (11), planet carrier constitute second rotary component (12), sun gear constitutes the 3rd rotary component (13); Described second planetary gear set (20) is single pinion type planetary gear set (20_12), and its sun gear constitutes that first rotary component (21), planet carrier constitute second rotary component (22), gear ring constitutes the 3rd rotary component (23).
24. according to claim 13,16 or 18 described multiple-speed gear-boxes, it is characterized in that: described first planetary gear set (10) is single pinion type planetary gear set (10_13), and its gear ring constitutes that first rotary component (11), planet carrier constitute second rotary component (12), sun gear constitutes the 3rd rotary component (13); Described second planetary gear set (20) is double-pinion type planetary gear set (20_13), and its sun gear constitutes that first rotary component (21), gear ring constitute second rotary component (22), planet carrier constitutes the 3rd rotary component (23).
25. according to claim 13,17 or 18 described multiple-speed gear-boxes, it is characterized in that: described first planetary gear set (10) is double-pinion type planetary gear set (10_14), and its planet carrier constitutes that first rotary component (11), gear ring constitute second rotary component (12), sun gear constitutes the 3rd rotary component (13); Described second planetary gear set (20) is single pinion type planetary gear set (20_14), and its sun gear constitutes that first rotary component (21), planet carrier constitute second rotary component (22), gear ring constitutes the 3rd rotary component (23).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010105491567A CN101984271B (en) | 2010-11-18 | 2010-11-18 | Multistage transmission |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010105491567A CN101984271B (en) | 2010-11-18 | 2010-11-18 | Multistage transmission |
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| Publication Number | Publication Date |
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| CN101984271A true CN101984271A (en) | 2011-03-09 |
| CN101984271B CN101984271B (en) | 2012-08-01 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2010105491567A Expired - Fee Related CN101984271B (en) | 2010-11-18 | 2010-11-18 | Multistage transmission |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105114556A (en) * | 2015-09-10 | 2015-12-02 | 韦兆利 | Planet gear multi-group transmission self-force-increasing device |
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| US5460579A (en) * | 1993-02-27 | 1995-10-24 | Volkswagen Ag | Automatic transmission having three planetary gear sets |
| US6860831B2 (en) * | 2001-03-30 | 2005-03-01 | Zf Friedrichshafen Ag | Multi-stage transmission |
| US7252617B2 (en) * | 2004-07-28 | 2007-08-07 | Hyundai Motor Company | Six-speed powertrain of an automatic transmission |
| US7341537B2 (en) * | 2005-05-25 | 2008-03-11 | General Motors Corporation | Multi-speed transmission |
| US7803082B2 (en) * | 2005-03-23 | 2010-09-28 | Zf Friedrichshafen Ag | Multi-step transmission |
| US7833124B2 (en) * | 2007-08-16 | 2010-11-16 | Hyundai Motor Company | Power train of an automatic transmission for a vehicle |
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2010
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Patent Citations (6)
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|---|---|---|---|---|
| US5460579A (en) * | 1993-02-27 | 1995-10-24 | Volkswagen Ag | Automatic transmission having three planetary gear sets |
| US6860831B2 (en) * | 2001-03-30 | 2005-03-01 | Zf Friedrichshafen Ag | Multi-stage transmission |
| US7252617B2 (en) * | 2004-07-28 | 2007-08-07 | Hyundai Motor Company | Six-speed powertrain of an automatic transmission |
| US7803082B2 (en) * | 2005-03-23 | 2010-09-28 | Zf Friedrichshafen Ag | Multi-step transmission |
| US7341537B2 (en) * | 2005-05-25 | 2008-03-11 | General Motors Corporation | Multi-speed transmission |
| US7833124B2 (en) * | 2007-08-16 | 2010-11-16 | Hyundai Motor Company | Power train of an automatic transmission for a vehicle |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105114556A (en) * | 2015-09-10 | 2015-12-02 | 韦兆利 | Planet gear multi-group transmission self-force-increasing device |
| CN105114556B (en) * | 2015-09-10 | 2017-09-22 | 江苏锡沂高新区科技发展有限公司 | The multigroup transmission self energizing effort device of planetary gear |
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| CN101984271B (en) | 2012-08-01 |
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