CN102808906A - Automatic transmission and motor vehicle - Google Patents

Automatic transmission and motor vehicle Download PDF

Info

Publication number
CN102808906A
CN102808906A CN2012102978024A CN201210297802A CN102808906A CN 102808906 A CN102808906 A CN 102808906A CN 2012102978024 A CN2012102978024 A CN 2012102978024A CN 201210297802 A CN201210297802 A CN 201210297802A CN 102808906 A CN102808906 A CN 102808906A
Authority
CN
China
Prior art keywords
main
pair
planetary gears
sun gear
gear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN2012102978024A
Other languages
Chinese (zh)
Other versions
CN102808906B (en
Inventor
王超
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Great Wall Motor Co Ltd
Original Assignee
Great Wall Motor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Great Wall Motor Co Ltd filed Critical Great Wall Motor Co Ltd
Priority to CN201210297802.4A priority Critical patent/CN102808906B/en
Publication of CN102808906A publication Critical patent/CN102808906A/en
Application granted granted Critical
Publication of CN102808906B publication Critical patent/CN102808906B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2066—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using one freewheel mechanism
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2069—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using two freewheel mechanism

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention discloses an automatic transmission and a motor vehicle, which relates to the technical field of transmission, and is invented for better improving the dynamic performance of the vehicle. The automatic transmission includes a gear box internally provided with an input shaft and an output shaft, wherein a first planetary gear mechanism is arranged on the input shaft and connected with a first variable speed actuating mechanism; the first variable speed actuating mechanism includes a plurality of first variable speed actuating components; and a second planetary gear mechanism is arranged on the output shaft and connected with a second variable speed actuating mechanism, and the second variable speed actuating mechanism includes a plurality of second variable speed actuating components. By selectively enabling the first variable speed actuating components and the second variable speed actuating components to simultaneously act, the first planetary gear mechanism and the second planetary gear mechanism are combined to form at least six transmission ratios of forward motive power. The automatic transmission is mainly applicable to the motor vehicle.

Description

A kind of automatic transmission and motor vehicle
Technical field
The present invention relates to the speed changer technical field, relate in particular to a kind of automatic transmission and motor vehicle.
Background technique
Nowadays; Vehicle with automatic transmission has advantages such as high-comfort, simple operation, fuel economy are good with it and receives popular parent and look at; Therefore domestic a lot of automobile vendors have the vehicle of automatic transmission in continuous independent development hardy; Wherein, in the majority with three speed automatic transmissions or four speed automatic transmissions.
For example with regard to four speed automatic transmissions; Usually in order to reduce the volume of automatic transmission; Mechanical driving part in the automatic transmission generally adopts the combined type planetary gears of compact structure; The combined type planetary gears is made up of a plurality of simple planetary gear set again; And can form four kinds of power transmission ratios, just can make four kinds of different power of four speed automatic transmissions output like this, thus can provide four kinds of different power of vehicle to satisfy vehicle required driving dynamics under different road conditions (like ramp, rough road, hill path, expressway etc.).
But because after four speed automatic transmissions and the engine whole vehicle coupling; Four kinds of power of final output can not make full use of the dynamic property of motor; And along with increasingly sophisticatedization of present traffic; Four kinds of power that four speed automatic transmissions are provided can not satisfy vehicle demand to driving dynamics under different road conditions, therefore make the vehicle that possesses four speed automatic transmissions aspect power performance, also have deficiency.
Summary of the invention
Embodiments of the invention provide a kind of automatic transmission and motor vehicle, can improve the power performance of vehicle preferably.
For achieving the above object, embodiments of the invention adopt following technological scheme:
A kind of automatic transmission includes gearbox, is provided with in the said gearbox:
Input shaft, said input shaft is provided with fluid torque converter;
Output shaft, said output shaft and said input shaft are parallel to each other;
First planetary gears, said first planetary gears is formed by the two-row planetary gear group, and said first planetary gears is located on the said input shaft;
The first speed change actuator, the said first speed change actuator comprises a plurality of first speed change executive components, the said first speed change executive component connects said first planetary gears; Through making said first speed change executive component action selectively, make said first planetary gears form the velocity ratio of four kinds of onward impulses;
Second planetary gears, said second planetary gears is located on the said output shaft, and said second planetary gears connects said first planetary gears,
The second speed change actuator, the said second speed change actuator comprises a plurality of second speed change executive components, the said second speed change executive component connects said second planetary gears;
Through the said first speed change executive component and the said second fast executive component are moved simultaneously, make said first planetary gears and said second planetary gears be combined to form the velocity ratio of at least six kinds of onward impulses.
Wherein, Said first planetary gears comprises the first main sun gear and the first secondary sun gear; The said first main sun gear is engaged with first primary planet wheel; Said first primary planet wheel is engaged with the first secondary planet wheel jointly with the said first secondary sun gear, and the said first secondary planet wheel is engaged with first main (pair) gear ring, and said first main planetary gear and the said first secondary planet wheel are connected with first jointly and lead (pair) planet carrier;
Said a plurality of first speed change executive component comprises first to three-clutch, first and second break and first overrunning clutch; Said first connects the said first secondary sun gear, said second accordingly to three-clutch leads (pair) sun gear and said first main (pair) planet carrier; Said first, second break connects the said first secondary sun gear, said first main (pair) planet carrier accordingly; Said first overrunning clutch connects said first main (pair) planet carrier.
Further; Said second planetary gears is formed by the single planetary gear set that with sun gear, planet carrier, gear ring is three rotation key elements, and the first rotation key element in said three rotation key elements connects said first main (pair) gear ring, the second rotation key element is fixed on the said output shaft;
Said a plurality of second speed change executive component comprises four clutches, the 3rd break, and said four clutches all is connected the 3rd rotation key element in said three rotation key elements with said the 3rd break.
Preferably; Said second planetary gears is formed by the two-row planetary gear group; Comprise second main (pair) sun gear, be engaged with second primary planet wheel and the second secondary planet wheel respectively on said second main (pair) sun gear, said second primary planet wheel and the said second secondary planet wheel are connected with the second primary planet frame and the second secondary planet carrier accordingly; And said second primary planet wheel and the said second secondary planet wheel are engaged with the second main gear ring and second auxiliary tooth ring accordingly; The said second main gear ring connects said first main (pair) gear ring, and said second auxiliary tooth ring connects the said second primary planet frame, and the said second primary planet frame is fixed on the said output shaft;
Said a plurality of second speed change executive component comprises four clutches, the 3rd break and second overrunning clutch; The input end of said four clutches connects the said second main gear ring, output terminal connects said second main (pair) sun gear; Said the 3rd break connects said second main (pair) sun gear; One end of said second overrunning clutch connects the said second secondary planet carrier.
Further, said input shaft and said output shaft are along coaxial arrangement.
The embodiment of the invention also provides a kind of motor vehicle, comprises the described automatic transmission of above-mentioned each item.
In the automatic transmission and motor vehicle that the embodiment of the invention provides; Comprise second planetary gears that is located on the said output shaft in the said gearbox; Said second planetary gears connects said first planetary gears; The power of said like this first planetary gears output can be input on said second planetary gears; Again by said second planetary gears with transmission of power to output shaft; Wherein, said second planetary gears also connects a plurality of said second speed change executive components, like this through making the said second fast executive component action selectively; Make said second planetary gears can form the velocity ratio of at least two kinds of power; And because first planetary gears can be through making the velocity ratio of four kinds of onward impulses of said first speed change executive component action formation selectively, therefore the power transmission ratio that forms respectively of first planetary gears and said second planetary gears can independent assortment, and through the said first speed change executive component and the said second fast executive component are moved simultaneously; Make said first planetary gears and said second planetary gears be combined to form the velocity ratio of at least six kinds of onward impulses; And then can make vehicle possess at least six gears that advance, just can provide at least six kinds of different power of vehicle to satisfy vehicle required driving dynamics under different road conditions (like ramp, rough road, hill path, expressway etc.) like this, thus the power performance of vehicle improved preferably.
Description of drawings
In order to be illustrated more clearly in the embodiment of the invention or technological scheme of the prior art; To do to introduce simply to the accompanying drawing of required use in embodiment or the description of the Prior Art below; Obviously, the accompanying drawing in describing below only is some embodiments of the present invention, for those of ordinary skills; Under the prerequisite of not paying creative work, can also obtain other accompanying drawing according to these accompanying drawings.
Fig. 1 is the schematic representation of automatic transmission in the embodiment of the invention;
Fig. 2 is the schematic representation of automatic transmission preferably in the embodiment of the invention;
Fig. 3 is the view when each retaining work of the first speed change executive component and the second speed change executive component in the automatic transmission shown in Figure 2.
Reference character:
The 1-gearbox, 2-fluid torque converter, 3-input shaft, 8-output shaft;
4-first planetary gears, the 40a-first main sun gear, the 40b-first secondary sun gear, 41a-first primary planet wheel, the 41b-first secondary planet wheel, 42-first main (pair) planet carrier, 43-first main (pair) gear ring;
The 5-first speed change actuator, 50-first clutch (C1), 51-second clutch (C2), 52-three-clutch (C3), 53-first break (B1), 54-second break (B2), 55-first overrunning clutch (F1);
6-second planetary gears, 60-second main (pair) sun gear, 61a-second primary planet wheel; The 61b-second secondary planet wheel, the 62a-second primary planet frame, the 62b-second secondary planet carrier; The 63a-second main gear ring, 63b-second auxiliary tooth ring, 60 '-sun gear; 61 '-planet wheel, 62 '-planet carrier, 63 '-gear ring;
The 7-second speed change actuator, 70,70 '-four clutches (C4), 71,71 ' the-the 3rd breaks (B3), 72-second overrunning clutch (F2).
Embodiment
To combine the accompanying drawing in the embodiment of the invention below, the technological scheme in the embodiment of the invention is carried out clear, intactly description, obviously, described embodiment only is the present invention's part embodiment, rather than whole embodiments.Based on the embodiment among the present invention, the every other embodiment that those of ordinary skills are obtained under the prerequisite of not making creative work belongs to the scope that the present invention protects.
As shown in Figure 1, be a specific embodiment of automatic transmission of the present invention.Said automatic transmission includes gearbox 1, is provided with in the said gearbox 1:
Input shaft 3, said input shaft 3 is provided with fluid torque converter 2;
Output shaft 8, said output shaft 8 is parallel to each other with said input shaft 3;
First planetary gears 4, said first planetary gears 4 is formed by the two-row planetary gear group, and said first planetary gears 4 is located on the said input shaft 3;
The first speed change actuator 5, the said first speed change actuator 5 comprises a plurality of first speed change executive components, the said first speed change executive component connects said first planetary gears 4; Through making said first speed change executive component action selectively, make said first planetary gears 4 form the velocity ratio of four kinds of onward impulses;
Second planetary gears 6, said second planetary gears 6 is located on the said output shaft 8, and said first planetary gears 4 of said second planetary gears, 6 connections,
The second speed change actuator 7, the said second speed change actuator 7 comprises a plurality of second speed change executive components, the said second speed change executive component connects said second planetary gears 6;
Through the said first speed change executive component and the said second fast executive component are moved simultaneously, make said first planetary gears 4 and said second planetary gears 6 be combined to form the velocity ratio of at least six kinds of onward impulses.
In the automatic transmission that the embodiment of the invention provides; Comprise second planetary gears 6 that is located on the said output shaft 8 in the said gearbox 1; Said second planetary gears 6 connects said first planetary gears 4; The power of said like this first planetary gears 4 outputs can be input on said second planetary gears 6; Again by said second planetary gears 6 with transmission of power to output shaft 8; Wherein, said second planetary gears 6 also connects a plurality of said second speed change executive components, like this through making the said second fast executive component action selectively; Make said second planetary gears 6 can form the velocity ratio of at least two kinds of power; And because first planetary gears 4 can be through making the velocity ratio of four kinds of onward impulses of said first speed change executive component action formation selectively, therefore the power transmission ratio that forms respectively of first planetary gears 4 and said second planetary gears 6 can independent assortment, and through the said first speed change executive component and the said second fast executive component are moved simultaneously; Make said first planetary gears 4 and said second planetary gears 6 be combined to form the velocity ratio of at least six kinds of onward impulses; And then can make vehicle possess at least six gears that advance, just can provide at least six kinds of different power of vehicle to satisfy vehicle required driving dynamics under different road conditions (like ramp, rough road, hill path, expressway etc.) like this, thus the power performance of vehicle improved preferably.
Usually; Kind with double or double above combined type planetary gears comprises a variety of; And every kind of combined type planetary gears all can form a plurality of suitable velocity ratios, but along with the continuous accumulation of experience, nowadays this combined type planetary gears basically all adopts the mechanism of some typification; And the structure of these typification is all compact, for example La Weina planetary gears, simpson planetary gear mechanism or tandem planetary gears.
Like this according to above-mentioned content; Said first planetary gears 4 in the embodiment of the invention can adopt the La Weina planetary gears; Wherein, Comprise the first main sun gear 40a and the first secondary sun gear 40b, the said first main sun gear 40a is engaged with first primary planet wheel 41a, and said first primary planet wheel 41a and the said first secondary sun gear 40b are engaged with the first secondary planet wheel 41b jointly; The said first secondary planet wheel 41b is engaged with first main (pair) gear ring 43, and said first main planetary gear and the said first secondary planet wheel 41b are connected with first main (pair) planet carrier 42 jointly;
Said a plurality of first speed change executive component comprises first to three-clutch 52, first and second break and first overrunning clutch 55; Said first connects the said first secondary sun gear 40b, said second accordingly to three-clutch 52 leads (pair) sun gear 60 and said first main (pair) planet carrier 42; Said first, second break 54 connects the said first secondary sun gear 40b, said first main (pair) planet carrier 42 accordingly; Said first overrunning clutch 55 connects said first main (pair) planet carrier 42.
Below be each first speed change executive component effect in first planetary gears 4:
First clutch 50 is with the secondary sun gear 40b of the transmission of power to the first of input shaft 3;
Second clutch 51 is with the main sun gear 40a of the transmission of power to the first of input shaft 3;
Three-clutch 52 is with main (pair) planet carrier 42 of the transmission of power to the first of input shaft 3;
First break 53, the fixing first secondary sun gear 40b is motionless, and the first secondary planet wheel 41b can rotate around the outer rim of the first secondary sun gear 40b;
Second break 54, fixing first main (pair) planet carrier 42 is motionless, and first primary planet wheel 41a or the first secondary planet wheel 41b be only as transition wheel, and can be around the rotational of self;
First overrunning clutch 55 can be motionless along a sense of rotation fixing first main (pair) planet carrier 42, and another opposite sense of rotation can freely be rotated.
In conjunction with Fig. 1; Second planetary gears 6 described in the embodiment of the invention can by with sun gear 60 ', planet carrier 62 ', the single planetary gear set of three rotations of gear ring 63 ' be key elements form, the first rotation key elements in said three rotation key elements connect said first main (pair) gear ring 43, second and rotate key element and be fixed on the said output shaft 8;
Said a plurality of second speed change executive component comprise four clutches 70 ', the 3rd break 71 ', said four clutches 70 ' with said three the rotation key elements of said the 3rd break 71 ' all be connected in the 3rd rotation key elements.
Illustrate according to Fig. 1, when the first rotation key element be gear ring 63 ', the second rotation key element planet carrier 62 ', the 3rd rotation key element is 60 ' time of sun gear, from the power of first planetary gears, 4 inputs gear ring rotated; When four clutches 70 ' action, the 3rd break 71 ' be failure to actuate, sun gear 60 ' with gear ring 63 ' rotation synchronously; And then make planet wheel 61 ' with planet carrier 62 ' rotate synchronously; And drive output shaft 8 rotations, thus outputing power, this moment, power transmission compared i=1; When four clutches 70 ' be failure to actuate, the 3rd break 71 ' action, sun gear 60 ' fixed, planet carrier 62 ' with gear ring 63 ' rotation, and drive output shaft 8 and rotate, thereby outputing power, this moment, power transmission was than i＞1.Know from above-mentioned; Second planetary gears 6 that the embodiment of the invention provides is during for single planetary gear set; Can form two kinds of power transmission ratios,, finally can form the velocity ratio of at least six kinds of power in conjunction with four kinds of onward impulse velocity ratios that first planetary gear mechanism is provided.
But above-mentioned single planetary gear set is not limited to the embodiment of the invention through the mode of the second speed change actuator 7 multiple velocity ratio that forms; For example can also increase by the second speed change executive component and adjust in the single planetary gear set element that is connected with input shaft 3 or first main (pair) gear ring 43 (sun gear 60 ', planet carrier 62 ' or gear ring 63 '), so also can reach the object of the invention.
Need to prove; When second planetary gears 6 adopts single planetary gear set,, can make said second planetary gears 6 form two kinds of power transmission ratios through making the said second fast executive component (four clutches 70 ', the 3rd break 71 ') action selectively; Four kinds of onward impulse velocity ratios that combine first planetary gears 4 to be provided again; Finally can be combined into eight kinds of different power transmission ratios, but in some cases, these eight kinds of different power transmission are than can not all satisfying the required power character of automatic transmission; Therefore generally also to therefrom screen more suitably power transmission ratio; Can find out that thus power transmission is relatively narrower than the scope of selecting, and make vehicle can not possess more gear (for example eight gears that advance), therefore; In order further to enlarge the range of choice of velocity ratio, the embodiment of the invention can adopt following scheme:
Said second planetary gears 6 can be formed by the two-row planetary gear group; This is because can know through content noted earlier; The combined type planetary gears basically all adopts the mechanism of some typification; For example La Weina planetary gears, simpson planetary gear mechanism or tandem planetary gears, so second planetary gears 6 that is formed by the two-row planetary gear group in the embodiment of the invention is preferably simpson planetary gear mechanism.
Particularly; Said second planetary gears 6 comprises second main (pair) sun gear 60; Be engaged with second primary planet wheel 61a and the second secondary planet wheel 61b respectively on said second main (pair) sun gear 60; Said second primary planet wheel 61a and the said second secondary planet wheel 61b are connected with the second primary planet frame 62a and the second secondary planet carrier 62b accordingly; And said second primary planet wheel 61a and the said second secondary planet wheel 61b are engaged with the second main gear ring 63a and the second auxiliary tooth ring 63b accordingly; The said second main gear ring 63a connects said first main (pair) gear ring 43, and the said second auxiliary tooth ring 63b connects the said second primary planet frame 62a, and the said second primary planet frame 62a is fixed on the said output shaft 8;
Said a plurality of second speed change executive component can comprise four clutches 70, the 3rd break 71 and second overrunning clutch 72; The input end of said four clutches 70 connects the said second main gear ring 63a, output terminal connects said second main (pair) sun gear 60; Said the 3rd break 71 connects said second main (pair) sun gear 60; One end of said second overrunning clutch 72 connects the said second secondary planet carrier 62b.
Below be each second speed change executive component effect in second planetary gears 7:
Four clutches 70 is with main (pair) sun gear 60 of first main (pair) gear ring 43 transmission of power to the second;
The 3rd break 71, fixing second main (pair) sun gear 60 is motionless, and second primary planet wheel 61a or the second secondary planet wheel 61b can rotate around the outer rim of second main (pair) sun gear 60;
Second overrunning clutch 72 can be motionless along the fixing second secondary planet carrier 62b of a sense of rotation, and another opposite sense of rotation can freely be rotated.
For clearer expression foregoing, the working principle of second planetary gears 6 in the embodiment of the invention is described in conjunction with accompanying drawing 2:
When four clutches 70 actions, the 3rd break 71 and braking member are failure to actuate; Second main (pair) sun gear 60 can be regarded as with the second main gear ring 63a and is structure as a whole, and therefore when the second main gear ring 63a rotated with first main (pair) gear ring 43 synchronously, second main (pair) sun gear 60 also rotated with the second main gear ring 63a synchronously; And then make the second primary planet frame 62a rotate synchronously with the second auxiliary tooth ring 63b; And drive output shaft 8 rotations, thus outputing power, this moment, power transmission compared i=1;
When 71 actions of the 3rd break, four clutches 70 and second overrunning clutch 72 are failure to actuate; This moment second, main (pair) sun gear 60 was fixed; When the second main gear ring 63a rotates with first main (pair) gear ring 43 synchronously, make the second primary planet frame 62a rotate, and drive output shaft 8 rotations with the second auxiliary tooth ring 63b; Thereby output power, this moment, power transmission was than i＞1;
When 72 actions of second overrunning clutch, four clutches 70 and the 3rd break 71 are failure to actuate; This moment, the second secondary planet carrier 62b was fixed; Second main (pair) sun gear 60 is in free state, and the planetary gear set that is formed by the second main gear ring 63a, the second primary planet frame 62a, second main (pair) sun gear 60 like this is in the degrees of freedom state, and definite velocity ratio can't be provided; But because the second secondary planet carrier 62b is fixed; Therefore the planetary gear set that is formed by the second auxiliary tooth ring 63b, the second secondary planet carrier 62b, second main (pair) sun gear 60 has definite velocity ratio, and when the second main gear ring 63a rotated with first main (pair) gear ring 43 synchronously, the second auxiliary tooth ring 63b rotated with the second primary planet frame 62a; And drive output shaft 8 rotations, thereby output power.
Can find out that like this second planetary gears 6 can provide three kinds of different power transmission ratios; Through four kinds of onward impulse velocity ratios that combine first planetary gears 4 to be provided; Finally can be combined into 12 kinds of different power transmission ratios, enlarge the range of choice of power transmission ratio like this, and can therefrom select at least eight kinds of different power transmission ratios; Therefore not only can make vehicle possess the gear that advances more than at least eight, and can bring into play the dynamic property of motor better.
Likewise; Above-mentioned Simpson's gear mechanism also is not limited to the embodiment of the invention through this mode of the second speed change actuator 7 multiple velocity ratio that forms; For example can also adjust the element of the Simpson's gear mechanism that is connected with the second speed change executive component (four clutches 70, the 3rd break 71 or second overrunning clutch 72); Perhaps increase by the second speed change executive component; Perhaps adjust the element that is connected with input shaft 3 or first main (pair) gear ring 43 in Simpson's gear mechanism again, can reach the object of the invention like this.
Also it is emphasized that; When making vehicle possess advancing during gear more than eight; For the embodiment of the invention, then preferred eight gears that advance, and closely be connected between eight velocity ratios of eight gear correspondences of advancing; Can improve the power of vehicle in shift process so on the one hand and be connected smoothness, also can improve the travelling comfort of gearshift simultaneously; On the other hand; Because the range of choice of velocity ratio compares broad; Therefore can select rational eight velocity ratios, and then vehicle is gone at more rational gear, can reduce the rotating speed of motor output like this; And then reduced the fuel consumption of vehicle and the waste discharge amount of minimizing waste gas, thereby improved vehicle fuel economy and emission performance in motion.
Further; Said input shaft 3 can be along coaxial arrangement with said output shaft 8; Make La Weina gear mechanism and Simpson's gear mechanism to be arranged side by side like this, and because the structure of La Weina gear mechanism and Simpson's gear mechanism is all compact, occupation space is less in gearbox 1; Therefore can be so that the structure of whole automatic transmission to be compact, volume is less.
The embodiment of the invention also provides a kind of motor vehicle, comprises the described automatic transmission of above-mentioned each item, can make vehicle possess eight gears that advance; Because therefore the gear range of a retaining～eight retainings can be brought into play the dynamic property of motor preferably, thereby make vehicle in motion than broad; Show power character preferably; And the velocity ratio that respectively advances between the gear closely is connected, and shifting comfort is higher, can increase the enjoyment of driver in driving procedure; Can also improve vehicle fuel economy and emission performance in motion in addition.
In conjunction with Fig. 2, Fig. 3 and foregoing, it is following that the embodiment of the invention has the work transfer route of each gear in the automatic transmission of eight gears that advance:
One retaining (D1):
Second clutch 51, first break 53,72 actions of second overrunning clutch; This moment, the first main sun gear 40a combined with input shaft 3; The first secondary sun gear 40b and the second secondary planet carrier 62b all are fixed; Power is delivered to input shaft 3 by fluid torque converter 2; Input shaft 3 is delivered to first main (pair) gear ring 43, the first main (pair) gear rings 43 by the first main sun gear 40a, first primary planet wheel 41a, the first secondary planet wheel 41b successively with power and again power is delivered to the second auxiliary tooth ring 63b by the second main gear ring 63a, second primary planet wheel 61a, second main (pair) sun gear 60, second secondary planet wheel 61b successively, because the second auxiliary tooth ring 63b and the second primary planet frame 62a interconnect; Therefore the second primary planet frame 62a rotates with the second auxiliary tooth ring 63b synchronously, and transmission of power is to output shaft 8 the most at last.
Two retainings (D2):
The second, four clutches (51,70), 55 actions of first overrunning clutch; This moment, the first main sun gear 40a combined with input shaft 3; First main (pair) planet carrier 42 all is fixed; Second main (pair) sun gear 60 combines with first main (pair) gear ring 43, and power is delivered to input shaft 3 by fluid torque converter 2, and input shaft 3 is delivered to first main (pair) gear ring 43 by the first main sun gear 40a, first primary planet wheel 41a, the first secondary planet wheel 41b successively with power; First main (pair) gear ring 43 is delivered to the second main gear ring 63a, second main (pair) sun gear 60 with power more simultaneously; The such second main gear ring 63a, second main (pair) sun gear 60 rotate synchronously, and drive the second primary planet frame 62a and rotate synchronously, and transmission of power is to output shaft 8 the most at last.
Three retainings (D3):
Second and third clutch (51,52), 72 actions of second overrunning clutch; This moment, the first main sun gear 40a and first main (pair) planet carrier 42 all combined with input shaft 3; The second secondary planet carrier 62b is fixed; Power is delivered to input shaft 3 by fluid torque converter 2; Input shaft 3 is delivered to the first main sun gear 40a and first main (pair) planet carrier 42, such first main sun gear 40a and first main (pair) planet carrier 42 simultaneously with power and rotates synchronously, and with main (pair) gear ring 43 of transmission of power to the first; First main (pair) gear ring 43 is delivered to the second auxiliary tooth ring 63b with power by the second main gear ring 63a, second primary planet wheel 61a, second main (pair) sun gear 60, second secondary planet wheel 61b again; Because the second auxiliary tooth ring 63b and the second primary planet frame 62a interconnect, therefore the second primary planet frame 62a rotates with the second auxiliary tooth ring 63b synchronously, and transmission of power is to output shaft 8 the most at last.
Four retainings (D4):
Second clutch 51, first and third break action (53,71); This moment first, main sun gear 40a input shaft 3 combined; The first secondary sun gear 40b and second main (pair) sun gear 60 all are fixed; Power is delivered to input shaft 3 by fluid torque converter 2, and input shaft 3 is delivered to first main (pair) gear ring 43 by the first main sun gear 40a, first primary planet wheel 41a, the first secondary planet wheel 41b successively with power, because second main (pair) sun gear 60 is fixed; Therefore the second main gear ring 63a drives the second primary planet frame 62a and rotates synchronously, and the most at last transmission of power to output shaft 8.
Five retainings (D5):
Three-clutch 52, first break 53,72 actions of second overrunning clutch; This moment first, main (pair) planet carrier 42 combined with input shaft 3; The first secondary sun gear 40b and the second secondary planet carrier 62b all are fixed; Power is delivered to input shaft 3 by fluid torque converter 2; Input shaft 3 is delivered to first main (pair) gear ring 43, the first main (pair) gear rings 43 with power by first main (pair) planet carrier 42 and again power is delivered to the second auxiliary tooth ring 63b by the second main gear ring 63a, second primary planet wheel 61a, second main (pair) sun gear 60, second secondary planet wheel 61b successively, because the second auxiliary tooth ring 63b and the second primary planet frame 62a interconnect; Therefore the second primary planet frame 62a rotates with the second auxiliary tooth ring 63b synchronously, and transmission of power is to output shaft 8 the most at last.
Six retainings (D6):
The second, four clutches (51,70), 53 actions of first break; This moment, the first main sun gear 40a combined with input shaft 3; The first secondary sun gear 40b is fixed; Second main (pair) sun gear 60 combines with first main (pair) gear ring 43, and power is delivered to input shaft 3 by fluid torque converter 2, and input shaft 3 is delivered to first main (pair) gear ring 43 by the first main sun gear 40a, first primary planet wheel 41a, the first secondary planet wheel 41b successively with power; First main (pair) gear ring 43 is delivered to the second main gear ring 63a, second main (pair) sun gear 60 with power more simultaneously; The such second main gear ring 63a, second main (pair) sun gear 60 rotate synchronously, and drive the second primary planet frame 62a and rotate synchronously, and transmission of power is to output shaft 8 the most at last.
Seven retainings (D7):
Second and third, four clutches (51,52,70) action; This moment, the first main sun gear 40a and first main (pair) planet carrier 42 all combined with input shaft 3; Second main (pair) sun gear 60 combines with first main (pair) gear ring 43, and power is delivered to input shaft 3 by fluid torque converter 2, and input shaft 3 is delivered to the first main sun gear 40a and first main (pair) planet carrier 42 simultaneously with power; The such first main sun gear 40a and first main (pair) planet carrier 42 rotate synchronously; And main (pair) gear ring 43, the first main (pair) gear rings 43 of transmission of power to the first are delivered to the second main gear ring 63a, second main (pair) sun gear 60, such second main gear ring 63a, second main (pair) sun gear 60 with power more simultaneously rotate synchronously; And drive the second primary planet frame 62a and rotate synchronously, transmission of power is to output shaft 8 the most at last.
Eight retainings (D8):
Third and fourth clutch (52,70), 53 actions of first break; This moment, the first main sun gear 40a and first main (pair) planet carrier 42 all combined with input shaft 3; The first secondary sun gear 40b is fixed; Second main (pair) sun gear 60 combines with first main (pair) gear ring 43, and power is delivered to input shaft 3 by fluid torque converter 2, and input shaft 3 is delivered to first main (pair) gear ring 43 with power by first main (pair) planet carrier 42; First main (pair) gear ring 43 is delivered to the second main gear ring 63a, second main (pair) sun gear 60 with power more simultaneously; The such second main gear ring 63a, second main (pair) sun gear 60 rotate synchronously, and drive the second primary planet frame 62a and rotate synchronously, and transmission of power is to output shaft 8 the most at last.
(R) keeps off:
First, fourth clutch (50,70), 54 actions of second break; This moment, the first secondary sun gear 40b combined with input shaft 3; First main (pair) planet carrier 42 is fixed; Second main (pair) sun gear 60 combines with first main (pair) gear ring 43, and power is delivered to input shaft 3 by fluid torque converter 2, and input shaft 3 is delivered to first main (pair) planet carrier 42 by the first secondary sun gear 40b, the first secondary planet wheel 41b successively with power; First main (pair) planet carrier 42 is delivered to the second main gear ring 63a, second main (pair) sun gear 60 with power more simultaneously; The such second main gear ring 63a, second main (pair) sun gear 60 rotate synchronously, and drive the second primary planet frame 62a and rotate synchronously, and transmission of power is to output shaft 8 the most at last.
Empty (N) keeps off/parks (P) retaining:
Each first speed change executive component all is failure to actuate with each second speed change executive component, and fluid torque converter 2 drives input shafts 3 rotations, but transferring power not.
The above; Be merely embodiment of the present invention, but protection scope of the present invention is not limited thereto, any technician who is familiar with the present technique field is in the technical scope that the present invention discloses; Can expect easily changing or replacement, all should be encompassed within protection scope of the present invention.Therefore, protection scope of the present invention should be as the criterion with the protection domain of said claim.

Claims (6)

1. an automatic transmission includes gearbox, is provided with in the said gearbox:
Input shaft, said input shaft is provided with fluid torque converter;
Output shaft, said output shaft and said input shaft are parallel to each other;
First planetary gears, said first planetary gears is formed by the two-row planetary gear group, and said first planetary gears is located on the said input shaft;
The first speed change actuator, the said first speed change actuator comprises a plurality of first speed change executive components, the said first speed change executive component connects said first planetary gears; Through making said first speed change executive component action selectively, make said first planetary gears form the velocity ratio of four kinds of onward impulses;
It is characterized in that, also be provided with in the said gearbox:
Second planetary gears, said second planetary gears is located on the said output shaft, and said second planetary gears connects said first planetary gears,
The second speed change actuator, the said second speed change actuator comprises a plurality of second speed change executive components, the said second speed change executive component connects said second planetary gears;
Through the said first speed change executive component and the said second fast executive component are moved simultaneously, make said first planetary gears and said second planetary gears be combined to form the velocity ratio of at least six kinds of onward impulses.
2. automatic transmission according to claim 1 is characterized in that,
Said first planetary gears comprises the first main sun gear and the first secondary sun gear; The said first main sun gear is engaged with first primary planet wheel; Said first primary planet wheel and the said first secondary sun gear are engaged with the first secondary planet wheel jointly; The said first secondary planet wheel is engaged with first main (pair) gear ring, and said first main planetary gear and the said first secondary planet wheel are connected with first main (pair) planet carrier jointly;
Said a plurality of first speed change executive component comprises first to three-clutch, first and second break and first overrunning clutch;
Said first connects the said first secondary sun gear, said second accordingly to three-clutch leads (pair) sun gear and said first main (pair) planet carrier; Said first, second break connects the said first secondary sun gear, said first main (pair) planet carrier accordingly; Said first overrunning clutch connects said first main (pair) planet carrier.
3. automatic transmission according to claim 2; It is characterized in that; Said second planetary gears is formed by the single planetary gear set that with sun gear, planet carrier, gear ring is three rotation key elements, and the first rotation key element in said three rotation key elements connects said first main (pair) gear ring, the second rotation key element is fixed on the said output shaft;
Said a plurality of second speed change executive component comprises four clutches, the 3rd break, and said four clutches all is connected the 3rd rotation key element in said three rotation key elements with said the 3rd break.
4. automatic transmission according to claim 2 is characterized in that,
Said second planetary gears is formed by the two-row planetary gear group; Comprise second main (pair) sun gear; Be engaged with second primary planet wheel and the second secondary planet wheel respectively on said second main (pair) sun gear; Said second primary planet wheel and the said second secondary planet wheel are connected with the second primary planet frame and the second secondary planet carrier accordingly, and said second primary planet is taken turns and the said second secondary planet wheel is engaged with the second main gear ring and second auxiliary tooth ring accordingly, and the said second main gear ring connects said first main (pair) gear ring; Said second auxiliary tooth ring connects the said second primary planet frame, and the said second primary planet frame is fixed on the said output shaft;
Said a plurality of second speed change executive component comprises four clutches, the 3rd break and second overrunning clutch;
The input end of said four clutches connects the said second main gear ring, output terminal connects said second main (pair) sun gear; Said the 3rd break connects said second main (pair) sun gear; One end of said second overrunning clutch connects the said second secondary planet carrier.
5. according to each described automatic transmission of claim 1-4, it is characterized in that said input shaft and said output shaft are along coaxial arrangement.
6. motor vehicle is characterized in that, comprise each described automatic transmission of claim 1-5.
CN201210297802.4A 2012-08-17 2012-08-17 A kind of automatic transmission and motor vehicles Active CN102808906B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201210297802.4A CN102808906B (en) 2012-08-17 2012-08-17 A kind of automatic transmission and motor vehicles

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201210297802.4A CN102808906B (en) 2012-08-17 2012-08-17 A kind of automatic transmission and motor vehicles

Publications (2)

Publication Number Publication Date
CN102808906A true CN102808906A (en) 2012-12-05
CN102808906B CN102808906B (en) 2016-06-08

Family

ID=47232715

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201210297802.4A Active CN102808906B (en) 2012-08-17 2012-08-17 A kind of automatic transmission and motor vehicles

Country Status (1)

Country Link
CN (1) CN102808906B (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102927222A (en) * 2012-10-29 2013-02-13 长城汽车股份有限公司 Automatic transmission
CN103057395A (en) * 2013-01-31 2013-04-24 长城汽车股份有限公司 Hybrid power transmission
CN108223706A (en) * 2016-12-21 2018-06-29 重庆硬核派传动科技有限公司 A kind of two speed compare epicyclic transmission

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3924491A (en) * 1973-05-30 1975-12-09 Volkswagenwerk Ag Hydrodynamic-mechanical transmission for automobiles
JP2009162322A (en) * 2008-01-08 2009-07-23 Honda Motor Co Ltd Transmission
CN102107658A (en) * 2009-12-24 2011-06-29 北京汽车研究总院有限公司 Hybrid power system and hybrid vehicle
CN202165536U (en) * 2011-06-30 2012-03-14 长城汽车股份有限公司 Automatic transmission with six forward gears and reverse gear
CN202188084U (en) * 2011-06-30 2012-04-11 长城汽车股份有限公司 6AT transmission

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3924491A (en) * 1973-05-30 1975-12-09 Volkswagenwerk Ag Hydrodynamic-mechanical transmission for automobiles
JP2009162322A (en) * 2008-01-08 2009-07-23 Honda Motor Co Ltd Transmission
CN102107658A (en) * 2009-12-24 2011-06-29 北京汽车研究总院有限公司 Hybrid power system and hybrid vehicle
CN202165536U (en) * 2011-06-30 2012-03-14 长城汽车股份有限公司 Automatic transmission with six forward gears and reverse gear
CN202188084U (en) * 2011-06-30 2012-04-11 长城汽车股份有限公司 6AT transmission

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102927222A (en) * 2012-10-29 2013-02-13 长城汽车股份有限公司 Automatic transmission
CN102927222B (en) * 2012-10-29 2016-01-06 长城汽车股份有限公司 Automatic transmission
CN103057395A (en) * 2013-01-31 2013-04-24 长城汽车股份有限公司 Hybrid power transmission
CN108223706A (en) * 2016-12-21 2018-06-29 重庆硬核派传动科技有限公司 A kind of two speed compare epicyclic transmission

Also Published As

Publication number Publication date
CN102808906B (en) 2016-06-08

Similar Documents

Publication Publication Date Title
CN100478583C (en) Eight-speed transmissions with four planetary gear sets
CN101275634B (en) 8-speed transmission
CN104343904A (en) Multi-speed transmission
US10000115B2 (en) Method of operating a transmission
CN101275633B (en) 8-speed transmission
US9291244B2 (en) Nine speed automatic transmission
CN102192285B (en) Multi-speed transmission with compound and simple planetary gear sets and with layshafts
CN102878259B (en) A kind of many gears automatic transmission and power assembly
JP2013199959A (en) Automatic transmission for vehicle
CN105134893A (en) Multi-speed transmission with lay shaft
CN101275628B (en) 8-speed transmission with two fixed interconnections
CN101275637B (en) 8-speed transmission
CN104595436A (en) Seven-gear planetary transmission for automatic transmission case
CN101311580B (en) 8-gear transmission
CN101275629B (en) 8-speed transmission with two fixed interconnections
CN101290055A (en) Eight-speed transmission
CN102192286B (en) Multi-speed planetary transmission with three brakes and four clutches
CN101275635B (en) 8-speed transmission
JP5693510B2 (en) Automatic transmission for vehicles
JP2013204708A (en) Automatic transmission for vehicle
CN102808906A (en) Automatic transmission and motor vehicle
CN101446332B (en) Planetary gearbox with multi-gear power gear shifting
CN101275638A (en) 8-speed transmission
KR101872795B1 (en) Transmission apparatus for vehicles
CN102808918B (en) A kind of parallel axes type automatic transmission, power assembly and vehicle

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C14 Grant of patent or utility model
GR01 Patent grant