CN103470699A - Double-clutch-transmission drive mechanism - Google Patents
Double-clutch-transmission drive mechanism Download PDFInfo
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- CN103470699A CN103470699A CN2013103213518A CN201310321351A CN103470699A CN 103470699 A CN103470699 A CN 103470699A CN 2013103213518 A CN2013103213518 A CN 2013103213518A CN 201310321351 A CN201310321351 A CN 201310321351A CN 103470699 A CN103470699 A CN 103470699A
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- 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
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- 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
- F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
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Abstract
The invention discloses a double-clutch-transmission drive mechanism. The double-clutch-transmission drive mechanism comprises a first double-row planetary gear train and a second dual-set planetary gear train, wherein at least one of the two planetary gear trains adopts a CR-CR type gear speed change mechanism and comprises a front planetary gear set and a rear planetary gear set, in the front planetary gear set, a front gear ring is integrated with a rear planetary carrier into a whole through a synchronizer or a clutch, a front planetary carrier and a rear gear ring are integrated into a whole and connected with an output shaft to perform power output, the power is inputted through a front sun gear, or the power is inputted to a rear sun gear or a rear planetary carrier through the synchronizer or the clutch. According to the double-clutch-transmission drive mechanism, the CR-CR type gear speed change mechanism is combined with a Ravigneaux gear speed change mechanism and a Simpson gear speed change mechanism, two clutches and multiple synchronizers are also used in a matched manner, the gear shifting performance of double clutch transmissions is realized, the size of transmissions is reduced, and the gear-shifting smoothness is also improved.
Description
Technical field
The present invention relates to the automotive transmission technical field, specifically relate to a kind of double-clutch speed changer driving mechanism.
Background technique
The automotive transmission driving mechanism, by train pattern difference used, has two kinds of axis jointing type speed changer (parallel shaft transmission) and axis rotary speed gears (planetary transmission).Quantity by clutch can be divided into single clutch speed changer and double-clutch speed changer.The actuating unit of the double-clutch speed changer of application is parallel shaft transmission at present, power transmission is divided into two lines, the one, odd number shelves transfer route, the 2nd, even number shelves transfer route, article two, power transmission line connects first, second input shaft by first, second clutch respectively, by the driving gear on the driven shaft corresponding with two input shafts, output power again, double-clutch speed changer controls by the coordination of two clutches and each synchronizer is controlled, can realize in the situation that do not cut off the power transmission ratio, thereby shorten shift time.Yet the parallel-axis type double-clutch speed changer must adopt independent reverse gear shaft and reverse gear.When adopting an output shaft, the speed changer axial dimension is large; While adopting two output shafts, the speed changer radial dimension is large, takes up room large, is unfavorable for the topology layout design of automobile.The double-clutch speed changer forward gears of application adopts 7 grades at most at present, most widely used is six grades, total velocity ratio is little, when gear arranges, one grade of velocity ratio is also smaller, and the cosmetic vehicle that engine displacement is less is prone to when starting automobile phenomenon of shaking, and engine speed is higher during high speed, speed ratio changes greatly simultaneously, engine speed changes greatly during gear shift like this, make automobile power character, economical be not very desirable, smoothness is poor.
Summary of the invention
The technical problem to be solved in the present invention is, provides that a kind of structure is more compact by the double-clutch speed changer driving mechanism of brand new, and what reduce speed changer axially reaches radial dimension, and the gear that simultaneously advances can be more, to overcome the deficiencies in the prior art.
For solving the problems of the technologies described above, the technical solution used in the present invention is: a kind of double-clutch speed changer driving mechanism, comprise the first clutch and the first corresponding input shaft, the second clutch and the second corresponding input shaft, a plurality of synchronizers, output shaft, the sheathed setting of described first and second input shaft, also comprise first, second double planetary gear train, intermeshing the first gear and the second gear and the 3rd gear and the 4th gear; In described first, second double planetary gear train, have at least a double planetary gear train to adopt CR-CR formula gear shift, two planet rows before and after comprising, in front planet row, front ring gear is connected by synchronizer or clutch with rear planet carrier, front planet carrier is connected and is connected as power and exports with output shaft with rear gear ring, power is inputted by front sun gear, or is input on rear sun gear or rear planet carrier by synchronizer or clutch.
The front sun gear of the first double planetary gear train is connected with the second input shaft, and the planet carrier of front planet row is connected with the gear ring of rear planet row and the first gear; Rear sun gear is connected with the first external axle sleeve, and rear planet carrier is connected with axle sleeve in the middle of first.
The front sun gear of described the second double planetary gear train is connected with the second jack shaft and the 4th gear, the planet carrier of the front planet row of the second double planetary gear train is connected with the gear ring of rear planet row and the second gear, rear sun gear is connected with the second external axle sleeve, and rear planet carrier is connected with axle sleeve in the middle of second.
The first normal engagement synchronizer is located between the first double planetary gear train front ring gear and rear planet carrier, the second synchronizer is arranged between the rear planet carrier and the first external axle sleeve of the first double planetary gear train, the 3rd synchronizer is arranged between the first middle axle sleeve of the second input shaft and the first double planetary gear train, the second normal engagement synchronizer is located between the second double planetary gear train front ring gear and rear planet carrier, the 5th synchronizer is arranged between the rear planet carrier and the second external axle sleeve of the second double planetary gear train, the 6th synchronizer is arranged between the 7th synchronizer and the second external axle sleeve of the second double planetary gear train, the 7th synchronizer is arranged between the second middle axle sleeve of the 4th gear and the second double planetary gear train.
First, second clutch is arranged on the first double planetary gear train right side, output shaft be arranged on the second double planetary gear train and from first, second clutch at different axis, six grades of synchronizers are set between the rear sun gear of the second input shaft and the first row star wheel series.
First, second clutch is arranged on the first double planetary gear train right side, output shaft be arranged on the first double planetary gear train and with first, second clutch on same axis.
The described first double planetary gear train adopts CR-CR formula gear shift, and the second double planetary gear train adopts the La Weinashi gear shift.
The described first double planetary gear train adopts the Simpson gear shift, and the second double planetary gear train adopts CR-CR formula gear shift.
Described the first gear or the second gear and the engagement of main reducing gear driven gear, main reducing gear driven gear connected with differential.
Compared with prior art, the present invention has the following advantages: the present invention is on the basis of existing dual-clutch transmission, by adopting CR-CR formula gear shift and La Weinashi gear shift, the combination of Simpson gear shift, and coordinate two clutches, a plurality of synchronizers use, make it both can reach with few gear logarithm realize more the purpose of multiple gear ratios gear, can realize again the power shfit performance of dual-clutch transmission, and can reduce the axial and radial dimension of speed changer, make the size of speed changer controlled, the vehicle structure layout design is more flexible, can reduce production costs simultaneously.Transmission gear increases simultaneously, total velocity ratio is increased, when gear arranges, one grade of velocity ratio is also larger, the automobile phenomenon of shaking while making automobile that engine displacement is less be not easy starting to occur, and during high speed, engine speed is lower, because speed ratio changes littlely, the engine speed variation is less during gear shift like this, make the power character, economical all more satisfactory of automobile, the smoothness of gear shift simultaneously is improved.
The accompanying drawing explanation
The power-transmitting unit schematic diagram that Fig. 1 is double-clutch speed changer the first embodiment of the present invention;
The power-transmitting unit schematic diagram that Fig. 2 is second embodiment of the invention;
The power-transmitting unit schematic diagram that Fig. 3 is third embodiment of the invention;
The power-transmitting unit schematic diagram that Fig. 4 is fourth embodiment of the invention;
The power-transmitting unit schematic diagram that Fig. 5 is fifth embodiment of the invention;
The power-transmitting unit schematic diagram that Fig. 6 is sixth embodiment of the invention;
The power-transmitting unit schematic diagram that Fig. 7 is seventh embodiment of the invention;
The power-transmitting unit schematic diagram that Fig. 8 is eighth embodiment of the invention;
The structural representation that the output form that Fig. 9 is double-clutch speed changer of the present invention changes.
Embodiment
The double planetary gear train of the present invention first and the second double planetary gear train all can adopt CR-CR formula gear shift, Simpson gear shift or La Weinashi gear shift, but the first double planetary gear train and the second double planetary gear train have at least a double planetary gear train to adopt CR-CR formula gear shift.Can obtain multiple transmission scheme by combination.
Below, in conjunction with Figure of description and specific embodiment, technological scheme of the present invention is further described.
First, second double planetary gear train is all embodiments of CR-CR formula gear shift:
The first embodiment (eight grades)
Referring to Fig. 1, double clutch of the present invention comprises that two clutch components 1 (comprise the first clutch 2 and the second clutch 3, distinguish the first input shaft 4, the double planetary gear train 101 of the double planetary gear train 100, second of the second input shaft 5, the first, output shaft 130 and a plurality of synchronizer of corresponding two clutches.The first double planetary gear train and the second double planetary gear train are with upper and lower structural configuration, all CR-CR formula gear shifts, two planet rows before and after the first double planetary gear train comprises, front planet row is the first planet row X1, rear planet row is the second planet row X2, and the second double planetary gear train comprises the front planet row of third planet row X3(the second double planetary gear train) and the rear planet row of fourth planet row X4(the second double planetary gear train).
The front sun gear 114 of the first double planetary gear train is connected with the second input shaft 5, planet row before the first planet row X1() planet carrier 111 and planet row after the second planet row X2() gear ring 116 and the first gear 181 be connected.Rear sun gear 119 is connected with the first external axle sleeve 123.Rear planet carrier 120 is connected with axle sleeve 122 in the middle of first.
The front sun gear 134 of the second double planetary gear train is connected with the second jack shaft 143 and the 4th gear 184, planet row before third planet row X3() planet carrier 131 and planet row after fourth planet is arranged X4() gear ring 136 and the second gear 182 be connected.Rear sun gear 139 is connected with the second external axle sleeve 145.Rear planet carrier 140 is connected with axle sleeve 144 in the middle of second.
First input shaft 4 the other ends are connected with the 3rd gear 183, the three gears 183 and the 4th gear 184 engagements, the first gear 181 and the second gear 182 engagements, and the second gear 182 is connected with output shaft 8, and output shaft 8 and double clutch assembly 1 are in the same side.
The first normal engagement synchronizer 115 is located between the first double planetary gear train 100 front ring gears 112 and rear planet carrier 120, and the second synchronizer (two, fourth gear synchronizer 117) is arranged between the rear planet carrier 120 and the first external axle sleeve 123 of the first double planetary gear train 100.The 3rd synchronizer (six, eight grades of synchronizers 121) is arranged between the first middle axle sleeve 122 of the second input shaft 5 and the first double planetary gear train 100.
The second normal engagement synchronizer 135 is located between the second double planetary gear train 101 front ring gears 132 and rear planet carrier 140, and the 5th synchronizer (, third gear synchronizer 137) is arranged between the rear planet carrier 140 and the second external axle sleeve 145 of the second double planetary gear train 101.The 6th synchronizer (reversing-gear synchronizer 141) is arranged between the 7th synchronizer 142 and the second external axle sleeve 145 of the second double planetary gear train 101.The 7th synchronizer (five, seven grades of synchronizers 142) is arranged between the second middle axle sleeve 144 of the 4th gear 184 and the second double planetary gear train 101.
The double-clutch speed changer of the present embodiment can be realized eight fast forward gearss and a fast reverse gear.The first double planetary gear train 100 is realized two, four, six, eight gears controls.The second double planetary gear train 101 realizes that one, three, five, seven grade and reverse gear control.
Action at each gear synchronizer and clutch is as follows:
During neutral state, as shown in Figure 1, the first normal engagement synchronizer 115 links together the first double planetary gear train front ring gear 112 with rear planet carrier 120, the second normal engagement synchronizer 135 links together the second double planetary gear train front ring gear 132 with rear planet carrier 140.Two, fourth gear synchronizer 117 and, third gear synchronizer 137 mediate.Six, eight grades of synchronizers 121 and five, seven grades of synchronizers 142 and reversing-gear synchronizer 141 on right side in jointing state not.
One grade: one, third gear synchronizer 137 moves to left, rear planet carrier 140 in the second double planetary gear train 101 and the second normal engagement synchronizer 135 and the second double planetary gear train front ring gear 132 are connected and do not rotate, and the such second double planetary gear train 101 forms restriction relations.First clutch 2 engages simultaneously.Power passes to the first input shaft 4, the three gear 183, the four gears 184 through first clutch 2, then arrives output shaft through the second double planetary gear train 101.Now second clutch 3 is in separated state, the position of all the other synchronizers when neutral state.
Second gear: two, fourth gear synchronizer 117 moves to left, and rear planet carrier the 120, first normal engagement synchronizer 115 and front ring gear 112 connections in the first double planetary gear train 101 are not rotated, and the such first double planetary gear train 100 forms restriction relations.First clutch 2 separates, and second clutch 3 engages simultaneously, and power passes to the second input shaft 5 through first clutch 2, through the first double planetary gear train 100, the first gear 181, the second gears 182, then by output shaft 8 outputs.
Third gear: one, third gear synchronizer 137 moves to right, and the second external axle sleeve 145 is connected, thereby also connect motionless by the rear sun gear of the second double planetary gear train 139.Second clutch 3 separates, and first clutch 2 engages, and realizes the third gear transmission of power.
Fourth gear: two, fourth gear synchronizer 117 moves to right, and the first external axle sleeve 123 is connected, thereby also connect motionless by the rear sun gear of the first double planetary gear train 119.First clutch 2 separates, and second clutch 3 engages, and realizes the fourth gear transmission of power.Power passes to the second input shaft 5 through second clutch 2, through the first double planetary gear train 181, the first gear 161, the second gears 162, then by output shaft 8 outputs.
Five grades: five, seven grades of synchronizers 142 move to left, and the 4th gear 184 is connected with axle sleeve 144 in the middle of second.Second clutch 3 separates, and first clutch 2 engages, and realizes five grades of transmission of power.
Six grades: six, eight grades of synchronizers 121 move to left, and the second input shaft 5 is connected with axle sleeve 122 in the middle of first.First clutch 2 separates, and second clutch 3 engages, and realizes six grades of shelves transmission of power.Power passes to the second input shaft 5 through second clutch 2, through the first double planetary gear train 181, the first gear 161, the second gears 162, then by output shaft 8 outputs.
Seven grades: five, seven grades of synchronizers 142 move to left, the 4th gear 184 is connected with axle sleeve 144 in the middle of second, the second normal engagement synchronizer 135 moves to right, make the second double planetary gear train front ring gear 132 throw off and separate with rear planet carrier 140, while one, third gear synchronizer 137 move to right, by the second external axle sleeve 145, thereby also by the rear sun gear of the second double planetary gear train 139, connect motionless.Second clutch 3 separates, and first clutch 2 engages, and realizes seven grades of transmission of power.
Eight grades: six, eight grades of synchronizers 121 move to left, and the second input shaft 5 is connected with axle sleeve 122 in the middle of first.The first normal engagement synchronizer 115 moves to right, make the first double planetary gear train front ring gear 112 throw off and separate with rear planet carrier 120, while two, fourth gear synchronizer 117 move to right, and by the first external axle sleeve 123, thereby also by the rear sun gear of the second double planetary gear train 139, connect motionless.First clutch 2 separates, and second clutch 3 engages, and realizes eight grades of shelves transmission of power.
Reverse gear: reversing-gear synchronizer 141 moves to left, the second external axle sleeve 145 is connected with five, seven grades of synchronizers 142, and one, third gear synchronizer 137 moves to left, the rear planet carrier 140 in the second double planetary gear train 101 is connected and do not rotate.Second clutch 3 separates, and first clutch 2 engages, and realizes the reverse gear transmission of power.
Double-clutch speed changer in this invention can be realized multiple transforming gear pattern:
The order shift mode:
The order upgrade, take one grade be raised to second gear as example, before shifting commands sends, speed changer is in a gear working state.Prepare to implement before gearshift to need in advance two, fourth gear synchronizer 117 moves to left the front ring gear 112 in the first double planetary gear train 100 connected and do not rotate, now first clutch 2 and second clutch 3 are still respectively in engaging and separated state.When control system is sent shifting commands and is raised to second gear by one grade, all synchronizer hold modes are motionless, first clutch 2 progressively separates, second clutch 3 progressively engages simultaneously, until first clutch 2 separates fully, second clutch 3 engages fully, simultaneously and control one, third gear synchronizer 137 gets back to neutral position, make the second double planetary gear train front ring gear 132 unfettered, the irrelevant synchronizer of all the other and a grade and second gear also is failure to actuate.The order of other gears upgrades and order lowers category also knows by inference with same method.
The jump shift mode:
Odd gear is changed to the jump lifting shelves of even number gear, be raised to fourth gear or five grades and drop to second gear etc. as one grade, the even number gear is changed to the jump lifting shelves of odd gear, upgrade five grades or eight grades and drop to five etc. as two, its gear changing mode is the same with the controlling method that order upgrades, and can use the same method and know by inference.
The jump that odd gear is changed to odd gear upgrades, take one grade rise third gear as example, before shifting commands sends, speed changer is in a gear working state.Before prepare implementing gearshift, first clutch 2 separates, and one, third gear synchronizer 137 first gets back to neutral position, then move to right and connect motionless by the rear sun gear of the second double planetary gear train 139.First clutch 2 is rejoined, and completes one grade of control that rises third gear.In this process, second clutch 3 is always in separated state, and the irrelevant synchronizer of all the other and a grade and third gear also is failure to actuate.The jump that the jump lifting shelves that the jump that odd gear is changed to odd gear lowers category and the even number gear is changed to the even number gear and odd gear the are changed to odd gear controlling method that upgrades is the same, can use the same method and know by inference.
The setting of each gear velocity ratio can be passed through each planet row
value (
equal planet row the ratio of the gear ring number of teeth and the sun gear number of teeth), the velocity ratio of the first gear 181 and the second gear 182
and the 3rd gear 183 and the 4th gear 184 velocity ratios
set.For example establish the first double planetary gear train and comprise the first planet row X1 and the second planet row X2, the second double planetary gear train comprises that third planet is arranged X3 and fourth planet is arranged X4's
value is respectively
2.4,
3.1,
3.4,
2.6,
1,
1.19, obtain each gear velocity ratio shown in table 1, than level and the working condition of synchronizer.From numerical value, the velocity ratio of each gear, more appropriate rationally than level, and total gear ratio reaches 6.93, obtains good gear ratio characteristic.
the working condition of each gear velocity ratio of table 1 eight gear gearboxes, ratio level and synchronizer
Annotate: " zero " means that clutch engages or the synchronizer action
The second embodiment (seven grades)
Referring to Fig. 2, on the first embodiment's basis, two clutch components 1 are arranged on to the first double planetary gear train 100 right sides, output shaft 8 is arranged on the second double planetary gear train 101 from two clutch components 1 at different axis and not in the same side, cancel six, eight grades of synchronizers 121 and the first middle axle sleeve 122, and six grades of synchronizers 124 are set between the rear sun gear 119 of the second input shaft 5 and the first row star wheel series.The velocity ratio that needs appropriate change the first gear 181 and the second gear 182, the 3rd gear 183 and the 4th gear 184 is set according to the gear velocity ratio, and each planet row
value.The such first double planetary gear train 100 is realized two, four, six grades, and the second double planetary gear train 101 realizes one, three, five, seven and reverse gear.
The 3rd embodiment (six grades)
Referring to Fig. 3, on the second embodiment's basis, output shaft 8 is arranged on the first double planetary gear train 100 with two clutch components 1 at same axis at homonymy not, cancel the second normal engagement synchronizer 135 and reversing-gear synchronizer 141 and five, seven grades of synchronizers 142, and between the rear sun gear 139 of the second planetary gear train and the 4th gear 184, six grades of synchronizers 146 are set.Recover the first normal engagement synchronizer 115 in the first embodiment on the first double planetary gear train 100.In order to better meet the gear velocity ratio, needs are set, but the velocity ratio of appropriate change the first gear 181 and the second gear 182, the 3rd gear 183 and the 4th gear 184, and each planet row
value.The first double planetary gear train 100 realizes one, three, five and reverse gear, and the second double planetary gear train 101 is realized two, four, six grades.
From top embodiment, output shaft 8 can change with the position relationship of two clutch components 1, when being arranged on the second double planetary gear train 101, output shaft 8 can be placed on not homonymy and the same side with two clutch components 1, when homonymy not, output shaft 8 both can also can be at different axis at same axis from two clutch components 1, and when the same side, output shaft 8 can only be from two clutch components 1 at different axis.Can only be at homonymy not when output shaft 8 is arranged on the first double planetary gear train 100, but same output shaft 8 can also can be at different axis at same axis from two clutch components 1.Odd number shelves or even number shelves can be arranged on the first double planetary gear train 100 also can be at the second double planetary gear train 101.Obtain the first double planetary gear train by permutation and combination thus and the second double planetary gear train is all 18 kinds of transmission schemes of CR-CR formula gear shift, referring to table 2.
the double planetary gear train of table 2 first and the second double planetary gear train are all CR-CR formula gear shift transmission schemes
First, second double planetary gear train adopts the embodiment by CR-CR formula gear shift and the combination of La Weinashi gear shift:
The 4th embodiment (eight grades)
Referring to Fig. 4, on the first embodiment's basis, the second double planetary gear train is adopted to the La Weinashi gear shift.The second double planetary gear train 101 comprises third planet row X3 and fourth planet row X4, small sun gear 233 is connected with short planet wheel 232 engagements and with the second middle axle sleeve 243, short planet wheel 232 and long planet wheel 231 engagements, large sun gear with also with long planet wheel 231, mesh and be connected with the second external axle sleeve 242, short planet wheel 232 and long planet wheel 231 are installed on planet carrier 235, planet carrier 235 is connected with the second jack shaft 241, gear ring 234 is connected with the second gear and output shaft 8, one, third gear synchronizer 237 be arranged on planet carrier 235 and between, reversing-gear synchronizer 238 is arranged between the second normal engagement synchronizer 239 and the second external axle sleeve 242, the second normal engagement synchronizer 239 is arranged on five, in the middle of seven grades of synchronizers 240 and second between axle sleeve 243, five, seven grades of synchronizers 240 are arranged between the second jack shaft 241 and the 4th gear 184.
The setting of each gear velocity ratio can be passed through each planet row
value (
equal planet row the ratio of the gear ring number of teeth and the sun gear number of teeth), when the 3rd gear 183 and the 4th gear 184 transmissions of the transmission of the first gear 181 and the second gear 182 recently set.
This embodiment's shift mode is consistent with the first embodiment, and the first double planetary gear train is realized two, four, six, eight grades, and the first double planetary gear train realizes one, three, five, seven and reverse gear.
The 5th embodiment (seven grades)
Referring to Fig. 5, on the 4th embodiment's basis, two clutch components 1 are placed on to the opposite side of the first double planetary gear train 100, output shaft 8 and two clutch components 1 are respectively at homonymy not and not on same axis like this, cancel the second jack shaft 241, reversing-gear synchronizer 238, the second normal engagement synchronizer 239 and five, seven grades of synchronizers 240 in the second double planetary gear train 101, six grades of synchronizers 245 are set between the second external axle sleeve 242 and the 4th gear 284, and increase reversing-gear synchronizer 125 at the first double planetary gear train 100.Transmission each planet row when that needs appropriate change the first gear 181 and the second gear 182, the 3rd gear 183 and the 4th gear 184 is set according to the gear velocity ratio
value.The first double planetary gear train 100 realizes one, three, five, seven and reverse gear, and the second double planetary gear train 101 is realized two, four, six grades.
The 6th embodiment (six grades)
Referring to Fig. 6, on the 5th embodiment's basis, location swap by the first double planetary gear train and the second double planetary gear train, output shaft 8 be placed on the same axis of the first double planetary gear train on, and at homonymy not, cancel reversing-gear synchronizer 124 and five, seven grades of synchronizers 121, increase Five-gear synchronizer 124.Transmission each planet row when that needs appropriate change the first gear 181 and the second gear 182, the 3rd gear 183 and the 4th gear 184 is set according to the gear velocity ratio
value.The first double planetary gear train 100 is realized two, four, six grades, and the second double planetary gear train 101 realizes one, three, five and reverse gear.
From fourth, fifth, six embodiments, simultaneously in conjunction with first, second and third embodiment's situation, output shaft 8 can change with the position relationship of two clutch components 1, when being arranged on the second double planetary gear train, output shaft 8 can be placed on not homonymy and the same side with two clutch components 1, when homonymy not, output shaft 8 both can also can be at different axis at same axis from two clutch components 1, and when the same side, output shaft 8 can only be from two clutch components 1 at different axis.Can only be at homonymy not when output shaft 8 is arranged on the first double planetary gear train, but same output shaft 8 can also can be at different axis at same axis from two clutch components 1.Odd number shelves or even number shelves can be arranged on the first double planetary gear train also can be at the second double planetary gear train, simultaneously, CR-CR formula gear shift and La Weina gear shift both can be set to the odd number shelves also can be set to the even number shelves, and both can be placed on the first double planetary gear train and also can be placed on the second double planetary gear train.Obtain 36 kinds of transmission schemes by permutation and combination thus, referring to table 3.
table 3 is by CR-CR formula gear shift and La Weina gear shift combination transmission scheme
First, second double planetary gear train adopts the embodiment by CR-CR formula gear shift and the combination of Simpson gear shift:
The 7th embodiment (seven grades)
Referring to Fig. 7, on embodiment one basis, the first double planetary gear train is adopted to the Simpson gear shift.The first double planetary gear train 100 comprises the first planet row X1 and the second planet row X2, front ring gear 312 in the first double planetary gear train 100 is connected with the second input shaft 5, front sun gear 314 in the first double planetary gear train and rear sun gear 319 are connected with the first axle sleeve 321, and the first axle sleeve 321 empty sets are on the first input shaft 4.Front planet carrier 313, rear gear ring 315 and the first gear 181 link together, and six grades of synchronizers 317 are arranged between rear gear ring 315 and rear planet carrier 318, and two, fourth gear synchronizer 320 is located between rear planet carrier 318 and the first axle sleeve 321.Transmission each planet row when that needs appropriate change the first gear 181 and the second gear 182, the 3rd gear 183 and the 4th gear 184 is set according to the gear velocity ratio
value.The first double planetary gear train 100 is realized two, four, six gears controls.The second double planetary gear train 101 realizes that one, three, five, seven grade and reverse gear control.
The 8th embodiment (six grades)
On the 7th embodiment's basis, output shaft 8 be placed on the same axis of the first double planetary gear train on, and at homonymy not, cancel second in the middle of axle sleeve 144, reversing-gear synchronizer 141 and five or seven grades of synchronizers 142, increase Five-gear synchronizer 147.Transmission each planet row when that needs appropriate change the first gear 181 and the second gear 182, the 3rd gear 183 and the 4th gear 184 is set according to the gear velocity ratio
value.The first double planetary gear train 100 is realized two, four, six gears controls.The second double planetary gear train 101 realizes that one, three, five grade and reverse gear control.
From the 7th, eight embodiments, simultaneously in conjunction with first, second, third and fourth, five, six embodiments' situation, output shaft 8 can change with the position relationship of two clutch components 1, when being arranged on the second double planetary gear train, output shaft 8 can be placed on not homonymy and the same side with two clutch components 1, when homonymy not, output shaft 8 both can also can be at different axis at same axis from two clutch components 1, and when the same side, output shaft 8 can only be from two clutch components 1 at different axis.Can only be at homonymy not when output shaft 8 is arranged on the first double planetary gear train, but same output shaft 8 can also can be at different axis at same axis from two clutch components 1.Odd number shelves or even number shelves can be arranged on the first double planetary gear train also can be at the second double planetary gear train, simultaneously, CR-CR formula gear shift and Simpson gear shift both can be set to the odd number shelves also can be set to the even number shelves, and both can be placed on the first double planetary gear train and also can be placed on the second double planetary gear train, but in thering are seven gear speed-changing devices, only have CR-CR formula gear shift just can be set to the odd number shelves, both one, three, five, seven grade.Obtain 18 kinds of transmission schemes by permutation and combination thus, referring to table 4.
table 4 is by CR-CR formula gear shift and Simpson gear graduation combination transmission scheme
In all transmission modes, change and each planet row
the transmission of value, the first gear and the second gear is the 3rd gear and the 4th gear ratio when, adjust the action of gear gear shift executive component simultaneously, gear setting can suitably change, eight gear gearboxes are changed to a planet row and realize one, three, five, six, another planet row is realized two, four, seven, eight grades, seven speed transmissions is changed to a planet row and realizes one, three, five, six, and another planet row is realized two, four, seven grades, and reverse gear is generally established with one grade on same planet row.Take seven speed transmissions as example, referring to Fig. 2, establish the first double planetary gear train the first planet row X1 and the second planet row X2, the second double planetary gear train comprises that third planet is arranged X3 and fourth planet is arranged X4's
value is respectively
3.2,
2.1,
3.5,
3.5, establish the velocity ratio of the first gear 181 and the second gear 182
and the 3rd gear 183 and the 4th gear 184 velocity ratios
be respectively
0.8,
1.25, obtain each different gear velocity ratios, than level and the working condition of synchronizer, referring to table 5, the such first double planetary gear train 100 is realized two, four, seven grades, the second double planetary gear train 101 realizes one, three, five, six.From numerical value, the velocity ratio of each gear, more appropriate rationally than level, and total gear ratio reaches 7.03, obtains gear ratio characteristic preferably.
the working condition of each gear velocity ratio of table 5 seven speed transmissions, ratio level and synchronizer
In addition, in all transmission modes, two clutch components and output shaft can suitably change in the output form of the same side, referring to Fig. 9, reduce the first gear 181 and the second gear 182 diameters, two gears and main reducing gear driven gear 190 directly mesh, and by the external outputting power of differential mechanism 191.
Claims (9)
1. a double-clutch speed changer driving mechanism, comprise the first clutch and the first corresponding input shaft, the second clutch and the second corresponding input shaft, a plurality of synchronizers, output shaft, the sheathed setting of described first and second input shaft, also comprise first, second double planetary gear train, intermeshing the first gear and the second gear and the 3rd gear and the 4th gear; It is characterized in that: in described first, second double planetary gear train, have at least a double planetary gear train to adopt CR-CR formula gear shift, two planet rows before and after comprising, in front planet row, front ring gear is connected by synchronizer or clutch with rear planet carrier, front planet carrier is connected and is connected as power and exports with output shaft with rear gear ring, power is inputted by front sun gear, or is input on rear sun gear or rear planet carrier by synchronizer or clutch.
2. double-clutch speed changer driving mechanism according to claim 1, it is characterized in that: the front sun gear of the first double planetary gear train is connected with the second input shaft, and the planet carrier of front planet row is connected with the gear ring of rear planet row and the first gear; Rear sun gear is connected with the first external axle sleeve, and rear planet carrier is connected with axle sleeve in the middle of first.
3. double-clutch speed changer driving mechanism according to claim 2, it is characterized in that: the front sun gear of described the second double planetary gear train is connected with the second jack shaft and the 4th gear, the planet carrier of the front planet row of the second double planetary gear train is connected with the gear ring of rear planet row and the second gear, rear sun gear is connected with the second external axle sleeve, and rear planet carrier is connected with axle sleeve in the middle of second.
4. double-clutch speed changer driving mechanism according to claim 3, it is characterized in that: the first normal engagement synchronizer is located between the first double planetary gear train front ring gear and rear planet carrier, the second synchronizer is arranged between the rear planet carrier and the first external axle sleeve of the first double planetary gear train, the 3rd synchronizer is arranged between the first middle axle sleeve of the second input shaft and the first double planetary gear train, the second normal engagement synchronizer is located between the second double planetary gear train front ring gear and rear planet carrier, the 5th synchronizer is arranged between the rear planet carrier and the second external axle sleeve of the second double planetary gear train, the 6th synchronizer is arranged between the 7th synchronizer and the second external axle sleeve of the second double planetary gear train, the 7th synchronizer is arranged between the second middle axle sleeve of the 4th gear and the second double planetary gear train.
5. double-clutch speed changer driving mechanism according to claim 1, it is characterized in that: first, second clutch is arranged on the first double planetary gear train right side, output shaft be arranged on the second double planetary gear train and from first, second clutch at different axis, six grades of synchronizers are set between the rear sun gear of the second input shaft and the first row star wheel series.
6. double-clutch speed changer driving mechanism according to claim 1, it is characterized in that: first, second clutch is arranged on the first double planetary gear train right side, output shaft be arranged on the first double planetary gear train and with first, second clutch on same axis.
7. double-clutch speed changer driving mechanism according to claim 1, is characterized in that: the described first double planetary gear train employing CR-CR formula gear shift, the second double planetary gear train employing La Weinashi gear shift.
8. double-clutch speed changer driving mechanism according to claim 1, is characterized in that: the described first double planetary gear train employing Simpson gear shift, the second double planetary gear train employing CR-CR formula gear shift.
9. according to the described arbitrary double-clutch speed changer driving mechanism of claim 1 to 8, it is characterized in that: described the first gear or the second gear and the engagement of main reducing gear driven gear, main reducing gear driven gear connected with differential.
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106068402A (en) * | 2014-02-17 | 2016-11-02 | 工程中心斯太尔有限两合公司 | The double-clutch speed changer that can shift gears under full load |
| CN108136889A (en) * | 2015-10-27 | 2018-06-08 | 舍弗勒技术股份两合公司 | CVT differential mechanisms |
| CN109654180A (en) * | 2019-02-15 | 2019-04-19 | 络优集成科技(无锡)有限公司 | Planet and dead axle compound variable speed mechanism |
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| US5445042A (en) * | 1993-10-21 | 1995-08-29 | General Motors Corporation | Transmission and control with hydraulically actuated synchronizers |
| US20040121877A1 (en) * | 2002-12-19 | 2004-06-24 | Lee Chunhao J. | Six-speed dual-clutch transmissions having four planetary gear sets and two brakes |
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| CN106068402A (en) * | 2014-02-17 | 2016-11-02 | 工程中心斯太尔有限两合公司 | The double-clutch speed changer that can shift gears under full load |
| CN106068402B (en) * | 2014-02-17 | 2018-07-20 | 工程中心斯太尔有限两合公司 | The double-clutch speed changer that can be shifted gears under full load |
| CN108136889A (en) * | 2015-10-27 | 2018-06-08 | 舍弗勒技术股份两合公司 | CVT differential mechanisms |
| CN108136889B (en) * | 2015-10-27 | 2021-01-26 | 舍弗勒技术股份两合公司 | CVT differential mechanism |
| CN109654180A (en) * | 2019-02-15 | 2019-04-19 | 络优集成科技(无锡)有限公司 | Planet and dead axle compound variable speed mechanism |
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| CN103470699B (en) | 2017-06-27 |
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