CN104141751B - Planetary gear type double-clutch speed changer - Google Patents
Planetary gear type double-clutch speed changer Download PDFInfo
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- CN104141751B CN104141751B CN201410324931.7A CN201410324931A CN104141751B CN 104141751 B CN104141751 B CN 104141751B CN 201410324931 A CN201410324931 A CN 201410324931A CN 104141751 B CN104141751 B CN 104141751B
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Classifications
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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
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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
- 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
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
- F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds
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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
- 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
- F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The open a kind of planetary gear type double-clutch speed changer of the present invention: include the sun gear power shaft of the planet circular system that first clutch controls, the planet carrier power shaft of the planet circular system that second clutch controls, and the gear ring power shaft of the planet circular system of first, second clutch co-controlling；Sun gear power shaft, planet carrier power shaft, gear ring power shaft are the most sheathed, all can rotate relatively freely；Respective brake is set on each power shaft；After first jackshaft, the second jackshaft are placed in planet circular system, and being set in parallel in power shaft both sides, output shaft is arranged at power shaft rear end, and between first jackshaft the second jackshaft；Described each power shaft coordinates engaging and the switch of each brake of each clutch, all can export two kinds and two or more gear ratio.
Description
Technical field
The present invention relates to system of vehicle transmission field, relate in particular to a kind of planetary gear type double-clutch speed changer.
Background technology
Variator is one of critical piece in vehicle transmission system, and it can not only change automobile driving speed and the moment of torsion of driving wheel in a big way, and can also realize reversing and neutral position sliding.According to the arrangement form of electromotor, variator has longitudinal and horizontal point, the most longitudinal front-engine rear-drive or the 4 wheel driven vehicle of being applicable to, and horizontal is applicable to preposition forerunner's vehicle.
Typical double-clutch speed changer, refer to by two clutches two power shafts with variator respectively and connect transmission engine powers, the driving gear of the odd number even gear of variator is arranged on two power shafts, by the switching of two clutches and the combination of different lock unit or separation, realize conversion and the output of moment of torsion of speed ratio via output shaft.It is longer that existing double-clutch speed changer there is problems of axial length, and gear is less, and structure is complicated, and weight lays particular stress on；Existing double-clutch speed changer mostly uses independent reversing shaft and reverse gear wheel of falling to realize reverse gear, which increases the complexity of number of parts and layout, relatively costly；The driving gear of existing double-clutch speed changer can only export a kind of gear ratio, and gear is few, and gear is many, and controlling organization is more；This characteristic can not adapt to the higher compact of vehicle and the requirement of fuel economy.
Summary of the invention
The technical problem to be solved in the present invention is to provide a kind of brand new, can flexible combination gear and the many gears planetary gear type double-clutch speed changer arranged that changes form；The output of more gear ratio, its driving gear exportable two kinds and above gear ratio is realized on the premise of not increasing gear pair；Can realize such as drive shift: seven grades, the multiple combinations such as eight grades or 12 grades, can need to be arranged to longitudinal rear-guard or 4 wheel driven according to vehicle, it is possible to be arranged to horizontal forerunner, it is also possible to need to realize the output of high torque according to vehicle capacity；Its mechanism is compact, lighter in weight, and volume is less.
For solving above-mentioned technical problem, the technical solution adopted in the present invention is:
A kind of planetary gear type double-clutch speed changer: include planet circular system, the sun gear power shaft of the planet circular system that first clutch controls, the planet carrier power shaft of the planet circular system that second clutch controls, and the gear ring power shaft of the planet circular system of first, second clutch co-controlling；Sun gear power shaft, planet carrier power shaft, gear ring power shaft are the most sheathed, all can rotate relatively freely；Respective brake is set on each power shaft；After first jackshaft, the second jackshaft are placed in planet circular system, and being set in parallel in power shaft both sides, output shaft is arranged at power shaft rear end, and between first jackshaft the second jackshaft；It is characterized in that the front end of sun gear power shaft is sequentially connected with first clutch and sun gear, rear end arranges driving gear and brake；The front end of planet carrier power shaft connects second clutch and arranges planetary carrier brake, connects planet carrier afterwards, and the hollow power shaft of its rear end is concentric with sun gear power shaft sheathed, on driving gear is set；Arranging brake outside the front end gear ring of gear ring power shaft, the hollow power shaft of rear end is concentric with planet carrier power shaft sheathed, and it arranges driving gear；Described each power shaft coordinates engaging and the switch of each brake of each clutch, all can export two kinds and above gear ratio.
Described sun gear power shaft is sequentially connected with first clutch, sun gear, driving gear and brake, or, described sun gear power shaft is sequentially connected with first clutch and sun gear.Each power shaft can be increased or decreased the quantity of driving gear according to the change of gear；
Described first jackshaft, the corresponding main deceleration driving gear of each increase on the second jackshaft, and it is set to different gear ratios；Main deceleration driving gear suit arrange, between lock unit is set；Each main deceleration driving gear often engages with the main reduction driven gear on output shaft；
On described first jackshaft, the driven gear of suit often engages with the driving gear on power shaft；On described second jackshaft, the driven gear of suit often engages with the driving gear on power shaft, and the driven gear that the one the second jackshafts are set with intersects engagement；Arranging lock unit between the driven gear of suit on described first, second jackshaft, rear end arranges main deceleration driving gear；
It, when forerunner or 4 wheel driven, can not be contacted with each other by described first jackshaft, the second jackshaft around power shaft concentric parallel displacement, its gear；Main deceleration driving gear on described first, second jackshaft often engages with the main reduction driven gear on differential assembly or transfer case assembly；
The driving part of each brake is fixing in the housing；Planet circular system, the first jackshaft, the second jackshaft, power input shaft, power output shaft or differential assembly or transfer case assembly are all fixing in the housing with bearing, all can be freely rotatable.
A kind of planetary gear type double-clutch speed changer, including the sun gear power shaft of the planet circular system controlled by first clutch, can only drive sun gear or jointly drives sun gear and driving gear according to the needs of different gears, also can arrange brake in its back-end；The planet carrier power shaft of the planet circular system controlled by second clutch, and the gear ring power shaft of the planet circular system by the first second clutch co-controlling；Described sun gear power shaft can concentric with the planet carrier power shaft of hollow-core construction be set with, and the planet carrier power shaft of hollow-core construction is concentric with the gear ring power shaft of hollow-core construction to be set with, the most free to rotate；Double clutches are positioned at the side of planet circular system, and opposite side is the power shaft of three or two suits, and after planet circular system, the both sides of power shaft are arranged with the first jackshaft, the second jackshaft in parallel；The driven gear of different gear, lock unit and main deceleration driving gear it is set with on described the one the second jackshafts；Main reduction driven gear on output shaft or differential assembly or transfer case assembly, often engages output power with the main deceleration driving gear on the one the second jackshafts simultaneously.
Above-mentioned planetary gear type double-clutch speed changer, planetary power shaft is respectively equipped with brake, i.e. sun gear brake, planetary carrier brake and gear ring brake；Wherein sun gear brake is positioned at the tail end of sun gear power shaft, and planetary carrier brake is positioned at the side of double clutch, and it is peripheral that gear ring brake is positioned at gear ring, and the driving part of each brake is fixed in housing；Variator can optionally arrange two or three brakes according to the needs of gear；
Above-mentioned planetary gear type double-clutch speed changer, double clutches optionally with sun gear power shaft or planet carrier power shaft respectively in connection with or two simultaneously engage with, coordinate the braking of different braking device again, it is provided that driving gear output two kinds and the two or more gear ratios on power shaft；
Above-mentioned double-clutch speed changer, it is not necessary to arrange reversing shaft specially, its planetary carrier brake is reverse gear brake, more favorably reduces number of parts, reduces transmission dimensions, reduces controlling organization, alleviates weight.
In the planetary gear type double-clutch speed changer of the present invention, in order to play the dynamic trait of electromotor to a greater extent, reduce and consume, may be configured as forward gear, seven grades, eight grades or 12 grades etc., also may be disposed to longitudinal rear-guard or 4 wheel driven, horizontal forerunner, mechanism of the present invention is compact, flexible layout, can effectively reduce production cost.Making the acceleration of vehicle, fuel economy gets a new look.
Accompanying drawing explanation
Fig. 1, planetary gear type double-clutch speed changer of the present invention, longitudinal eight forward gears and the variable transmission mechanism schematic diagram of two reverse gears.
Fig. 2, planetary gear type double-clutch speed changer of the present invention, longitudinal seven forward gears and the variable transmission mechanism schematic diagram of a reverse gear.
Fig. 3, planetary gear type double-clutch speed changer of the present invention, horizontal seven forward gears and the variable transmission mechanism schematic diagram of a reverse gear.
Fig. 4, is the side view of Fig. 3, it is indicated that the position relationship of each axle.
Fig. 5, planetary gear type double-clutch speed changer of the present invention, longitudinal high torque seven forward gears of output and the variable transmission mechanism schematic diagram of a reverse gear.
Fig. 6, planetary gear type double-clutch speed changer of the present invention, longitudinal 12 forward gears and the variable transmission mechanism schematic diagram of four reverse gears.
In figure, each list of reference numerals is: C1 first clutch, C2 second clutch, B1 planetary carrier brake, B2 gear ring brake, B3 sun gear brake, b brake disc, a brake caliper, SC1 the first lock unit, SC2 the second lock unit, SC3 the 3rd lock unit, SC4 the 4th lock unit, 1 power input shaft, 2 sun gear power shafts, 3 planet carrier power shafts, 4 gear ring power shafts, 5 first jackshafts, 6 second jackshafts, 7 power output shafts.
Detailed description of the invention
The embodiment described below with reference to accompanying drawing is exemplary, is used for the present invention is explained further.
First embodiment, see figure one, eight grades of planetary gear type double-clutch speed changers of the present invention, the sun gear power shaft 2 controlled including first clutch C1, the planet carrier power shaft 3 controlled by second clutch C2, and by first clutch C1, the gear ring power shaft 4 of second clutch C2 co-controlling, described each power shaft is the most sheathed, free to rotate, it each arranges corresponding driving gear；
Sun gear power shaft 2 front end connects first clutch C1 and sun gear, and tail end connects brake disc b in 2 grades and 7 grades shared driving gears 21 and brake B3；
Planet carrier power shaft 3 is sequentially connected with the driving gear 31 that second clutch C2, planet carrier, 1 grade and 4 grades are shared；It is additionally provided with planetary carrier brake B1 in planet carrier front end；
Gear ring power shaft 4 is sequentially connected with 6 grades and 8 grades and the shared driving gear 41 of reverse gear 2, also has, 3 grades and 5 grades and the shared driving gears 42 of reverse gear 1；Its gear ring is outside equipped with gear ring brake B2；
Described first jackshaft the 5, second jackshaft 6 is set in parallel in the both sides of the power shaft after planet circular system, driven gear 51 sheathed on the first jackshaft 5 and driven gear 52, between the first lock unit SC1 is set, tail end arranges main deceleration driving gear 55；Driven gear 61 sheathed on second jackshaft 6 and driven gear 62, between the second lock unit SC2 is set, tail end arranges main deceleration driving gear 65；Main reduction driven gear 71 is set on power output shaft 7, it often engages with the main deceleration driving gear 55 on the one the second jackshafts and main deceleration driving gear 65 simultaneously, different by each lock unit engage, then coordinate the switch of different braking device, optionally output power.
On described first jackshaft the 5, second jackshaft 6, sheathed driven gear often engages with the driving gear on power shaft.
Driving gear on described each power shaft is with optimized configuration, driving gear 41 and driving gear 42 are adjacent, driving gear 31 and driving gear 32 are adjacent, and cross one another and on first jackshaft the 5, second jackshaft 6 driven gear often engages, to shorten its axial distance.
Power transmission line is described as follows.
One grade of power transmission line: the first lock unit SC1 engages with driven gear 52, gear ring brake B2 closes, and first clutch C1 closes；Electromotor imparts power to first clutch C1 by power input shaft 1, the sun gear driving planet circular system rotates, it is delivered to again on planet carrier power shaft 3, transfer power on the first jackshaft 5 via often engagement driving gear 31, driven gear 52 and the first lock unit SC1, then engage output power with the main reduction driven gear 71 on power output shaft 7 by main deceleration driving gear 55 thereon.
Two grades of power transmission lines: the second lock unit SC2 engages with driven gear 62, gear ring brake B2 opens, first clutch C1 and second clutch C2 Guan Bi；Electromotor imparts power to first clutch C1 and second clutch C2 by power input shaft 1, whole planet circular system is driven to rotate, transfer torque on the second jackshaft 6 via driving gear 21, driven gear 62 and the second lock unit SC2, then engage output power with the main reduction driven gear 71 on power output shaft 7 by main deceleration driving gear 65 thereon.
Third gear power transmission line: the second lock unit SC2 engages with driven gear 61, gear ring brake B2 opens, first clutch C1 and second clutch C2 Guan Bi；Electromotor imparts power to first clutch C1 and second clutch C2 by power input shaft 1, whole planet circular system is driven to rotate, transfer power on the second jackshaft 6 via often engagement driving gear 42, driven gear 61 and the second lock unit SC2, then engage output power with the main reduction driven gear 71 on power output shaft 7 by main deceleration driving gear 65 thereon.
Fourth gear power transmission line: the first lock unit SC1 engages with driven gear 52, gear ring brake B2 opens, first clutch C1 and second clutch C2 Guan Bi；Electromotor imparts power to first clutch C1 and second clutch C2 by power input shaft 1, whole planet circular system is driven to rotate, transfer power on the first jackshaft 5 via often engagement driving gear 31, driven gear 52 and the first lock unit SC1, then engage output power with the main reduction driven gear 71 on power output shaft 7 by main deceleration driving gear 55 thereon.
Five grades of power transmission lines: the second lock unit SC2 engages with driven gear 61, gear ring brake B2 opens, and brake B3 closes, and second clutch C2 closes；Electromotor imparts power to second clutch C2 by power input shaft 1, the planet carrier driving planet circular system rotates, transfer power on the second jackshaft 6 via often engagement driving gear 42, driven gear 61 and the second lock unit SC2, then engage output power with the main reduction driven gear 71 on power output shaft 7 by main deceleration driving gear 65 thereon.
Six grades of power transmission lines: the first lock unit SC1 engages with driven gear 51, gear ring brake B2, brake B3 open, first clutch C1 and second clutch C2 Guan Bi；Electromotor imparts power to first clutch C1 and second clutch C2 by power input shaft 1, whole planet circular system is driven to rotate, transfer power on the first jackshaft 5 via often engagement driving gear 41, driven gear 51 and the first lock unit SC1, then engage output power with the main reduction driven gear 71 on power output shaft 7 by main deceleration driving gear 55 thereon.
Seven grades of power transmission lines: the second lock unit SC2 engages with driven gear 62, gear ring brake B2 closes, and second clutch C2 closes；Electromotor imparts power to second clutch C2 by power input shaft 1, the planet carrier driving planet circular system rotates, transfer power on the second jackshaft 6 via often engagement driving gear 21, driven gear 62 and the second lock unit SC2, then engage output power with the main reduction driven gear 71 on power output shaft 7 by main deceleration driving gear 65 thereon.
Eight grades of power transmission lines: the first lock unit SC1 engages with driven gear 51, gear ring brake B2 opens, and sun gear brake B3 closes, and second clutch C2 closes；Electromotor imparts power to second clutch C2 by power input shaft 1, the planet carrier driving planet circular system rotates, transfer power on the first jackshaft 5 via often engagement driving gear 41, driven gear 51 and the first lock unit SC1, then engage output power with the main reduction driven gear 71 on power output shaft 7 by main deceleration driving gear 55 thereon.
Reverse gear one power transmission line: the second lock unit SC2 engages with driven gear 61, the closedown of planetary carrier brake B1, first clutch C1 closes；Electromotor imparts power to first clutch C1 by power input shaft 1, the sun gear driving planet circular system rotates, transfer power on the second jackshaft 6 via often engagement driving gear 42, driven gear 61 and the second lock unit SC2, then engage output power with the main reduction driven gear 71 on power output shaft 7 by main deceleration driving gear 65 thereon.
Reverse gear two power transmission line: the first lock unit SC1 engages with driven gear 51, the closedown of planetary carrier brake B1, first clutch C1 closes；Electromotor imparts power to first clutch C1 by power input shaft 1, the sun gear driving planet circular system rotates, transfer power on the first jackshaft 5 via often engagement driving gear 41, driven gear 51 and the first lock unit SC1, then engage output power with the main reduction driven gear 71 on power output shaft 7 by main deceleration driving gear 55 thereon.
Shift process illustrates:
One grade is changed two grades of processes: when one grade, and the first lock unit SC1 engages with driven gear 52, and gear ring brake B2 closes, and planetary carrier brake B1, sun gear brake B3 open, and first clutch C1 closes, and second clutch C2 opens；Double-clutch speed changer control system sends one grade and changes two grades of instructions, first clutch C1 opens, first lock unit SC1 separates with driven gear 52, second lock unit SC2 engages with driven gear 62, meanwhile, gear ring brake B2 opens, then after the second lock unit SC2 is engaged with driven gear 62 and to put in place by gear shifting actuating mechanism, first clutch C1, second clutch C2 gradually close simultaneously, and of completely closed rear gearshift terminates；Electromotor imparts power to first clutch C1 and second clutch C2 by power input shaft 1, whole planet circular system is driven to rotate, transfer power on the second jackshaft 6 via often engagement driving gear 21, driven gear 62 and the second lock unit SC2, then engage output power with the main reduction driven gear 71 on power output shaft 7 by main deceleration driving gear 65 thereon.
The shift process of other gears is ibid similar to, except that the opening and closing of clutch, the switch of each brake, the selection of the joint of lock unit differs.
Second embodiment, sees Fig. 2, essentially identical with Fig. 1, and difference is sun gear power shaft 2 the driving sun gear of the planet circular system that first clutch C1 controls；3 driving gears are set on planet carrier power shaft 3, are followed successively by driving gear 31, driving gear 32, driving gear 33, gear ring power shaft 4 arranges 1 driving gear 41, and simplifies structure, remove sun gear brake B3.
Driving gear on planet carrier power shaft 3 is followed successively by 1 grade, 5 grades and shares often engagement 32,2 grades of 6 grades of shared driving gears 33 of the shared driving gear of driving gear 31,7 grades 3 grades；Driving gear on gear ring power shaft 4 is 4 grades, reverse gear shares driving gear 41.
Power transmission line is essentially identical with first embodiment, and the gear of the driving gear output on the most each power shaft is not quite similar.
3rd embodiment, see Fig. 3, essentially identical with Fig. 2, longitudinal rear-guard also can be set to horizontal forerunner, difference is that the sun gear power shaft 2 of the planet circular system that first clutch C1 controls is set to hollow-core construction, power input shaft 1 is set to rear input power by front input, and first jackshaft the 5, second jackshaft 6 is with power shaft for the center of circle to translation together, but its gear does not allows to contact with each other；Power output shaft 7 changes differential assembly into, it is possible to change transfer case assembly into, and on it, main reduction driven gear often engages output power with the main deceleration driving gear of output on first jackshaft the 5, second jackshaft 6 simultaneously.
Driving gear on planet carrier power shaft 3 is followed successively by 1 grade, 5 grades of shared driving gears, 32,2 grades of 6 grades of shared driving gears 33 of 31,7 grades 3 grades shared driving gears；Driving gear on gear ring power shaft 4 is 4 grades, reverse gear shares driving gear 41；Power transmission line and the second embodiment are identical.
Fig. 4 is the side view of Fig. 3, it is indicated that the position relationship of each between centers.
4th embodiment, sees Fig. 5；Due to the needs of Some vehicles loading capacity, when described the one the second the 3rd embodiments can not meet the demand of its high torque output, this example will meet its needs.
Fig. 5 with Fig. 2 is essentially identical, and driven gear and lock unit that difference is on first jackshaft the 5, second jackshaft 6 are just the same；Each driving gear on power shaft often engages with the driven gear on first jackshaft the 5, second jackshaft 6 simultaneously, and during gearshift, the lock unit on two axles does same action；Output driving gear on first jackshaft the 5, second jackshaft 6, the common driven gear output power driven on power output shaft 7.
Power transmission line and the second embodiment are identical, and each gear, shift process are the most identical.
5th embodiment, sees Fig. 6；In this example, the tooth of each gear compares closeer, and gear is finer and smoother, and in vehicle acceleration, gearshift steadily, does not has strong pause and transition in rhythm or melody sense, more comfortable.
This example improves on the basis of the second embodiment, and the main deceleration driving gear that difference is on first jackshaft the 5, second jackshaft 6 respectively increases by one, is main deceleration driving gear 56, main deceleration driving gear 66 respectively；Between two main deceleration driving gears on first jackshaft the 5, second jackshaft 6, lock unit is set, is the 3rd lock unit SC3, the 4th lock unit SC4 respectively；Increasing a main reduction driven gear 72 on power output shaft 7, main deceleration driving gear often engages with main reduction driven gear, drives power output shaft 7 to export power.
The more former example of power transmission line is complicated.There are two lock units respectively on first jackshaft the 5, second jackshaft 6, need common cooperation just can complete shift process, output power.
Power transmission line is illustrated below:
One grade of power transmission line: the first lock unit SC1 engages with driven gear 52, and the 3rd lock unit SC3 engages with main deceleration driving gear 55, gear ring brake B2 closes, and first clutch C1 closes；Electromotor imparts power to first clutch C1 by power input shaft 1, the sun gear driving planet circular system rotates, it is delivered to again on planet carrier power shaft 3, transfer power on the first jackshaft 5 via often engagement driving gear 31, driven gear 52 and the first lock unit SC1, then transfer power on main deceleration driving gear 55 via the 3rd the 3rd lock unit SC3, then by often engaging output power with the main reduction driven gear 71 on power output shaft 7.
The power transmission line of other gears is essentially identical, repeats no more.
Shift process is illustrated below:
Fourth gear changes five grades of processes: during fourth gear, and the second lock unit SC2 engages with driven gear 62, and the 4th lock unit SC4 engages with main deceleration driving gear 66, and gear ring brake B2 closes, and first clutch C1 closes；Double-clutch speed changer control system sends fourth gear and changes five grades of instructions, first clutch 1, brake 2 are opened simultaneously, then the second lock unit SC2 is engaged with driven gear 62 by gear shifting actuating mechanism simultaneously, 4th lock unit SC4 engages with main deceleration driving gear 65, after joint puts in place, first clutch C1, second clutch C2 gradually close simultaneously, and of completely closed rear gearshift terminates；Electromotor imparts power to first clutch C1 and second clutch C2 by power input shaft 1, whole planet circular system is driven to rotate, transfer power on the second jackshaft 6 via often engagement driving gear 42, driven gear 61 and the second lock unit SC2, then transfer power on main deceleration driving gear 65 via the 4th lock unit SC4, then by engaging output power with the driven gear 71 on power output shaft 7.
The shift process of other gears is ibid similar to, except that the opening and closing of clutch, the switch of each brake, the selection of the joint of lock unit differs.
The present invention is elaborated by embodiment described in this article, it is intended to be used for explaining the present invention, rather than limitation of the present invention；In the case of without departing from the principle of the present invention and objective, these examples can carry out multiple change, revise, replace and deform, the scope of the present invention is limited by claim and equivalent thereof.
Claims (7)
1. a planetary gear type double-clutch speed changer: include planet circular system, the sun gear power shaft of the planet circular system that first clutch controls, the planet carrier power shaft of the planet circular system that second clutch controls, and the gear ring power shaft of the planet circular system of first, second clutch co-controlling；Sun gear power shaft, planet carrier power shaft, gear ring power shaft are the most sheathed, all can rotate relatively freely；Respective brake is set on each power shaft；After first jackshaft, the second jackshaft are placed in planet circular system, and being set in parallel in power shaft both sides, output shaft is arranged at power shaft rear end, and between first jackshaft the second jackshaft；It is characterized in that: the front end of sun gear power shaft is sequentially connected with first clutch and sun gear, rear end arranges driving gear and brake；The front end of planet carrier power shaft connects second clutch and arranges planetary carrier brake, connects planet carrier afterwards, and the hollow power shaft of its rear end is concentric with sun gear power shaft sheathed, on driving gear is set；Arranging brake outside the front end gear ring of gear ring power shaft, the hollow power shaft of rear end is concentric with planet carrier power shaft sheathed, and it arranges driving gear；Described each power shaft coordinates engaging and the switch of each brake of each clutch, all can export two kinds and above gear ratio；On described first jackshaft, the driven gear of suit often engages with the driving gear on power shaft, and on described second jackshaft, the driven gear of suit often engages with the driving gear on power shaft, and the driven gear that the one the second jackshafts are set with intersects engagement；Arranging lock unit between the driven gear of suit on described first, second jackshaft, rear end arranges main deceleration driving gear.
Planetary gear type double-clutch speed changer the most according to claim 1, is characterized in that: described sun gear power shaft is sequentially connected with first clutch, sun gear, driving gear and brake；Or described sun gear power shaft is sequentially connected with first clutch and sun gear.
Planetary gear type double-clutch speed changer the most according to claim 1, is characterized in that: each power shaft can be increased or decreased the quantity of driving gear according to the change of gear.
Planetary gear type double-clutch speed changer the most according to claim 1, is characterized in that: the corresponding main deceleration driving gear of each increase on described first jackshaft, the second jackshaft, and is set to different gear ratios；Main deceleration driving gear suit arrange, between lock unit is set；Each main deceleration driving gear often engages with the main reduction driven gear on output shaft.
Planetary gear type double-clutch speed changer the most according to claim 1, is characterized in that: on described first jackshaft, the second jackshaft, the driven gear of suit is identical with the driving gear quantity on each power shaft and often engages.
Planetary gear type double-clutch speed changer the most according to claim 1, is characterized in that: it, when forerunner or 4 wheel driven, can not be contacted with each other by described first jackshaft, the second jackshaft around power shaft concentric parallel displacement, its gear；Main deceleration driving gear on described first, second jackshaft often engages with the main reduction driven gear on differential assembly or transfer case assembly.
7. according to the planetary gear type double-clutch speed changer described in any one of claim 1-6, it is characterized in that: the driving part of each brake is fixing in the housing；Planet circular system, the first jackshaft, the second jackshaft, power input shaft, power output shaft or differential assembly or transfer case assembly are all fixing in the housing with bearing, all can be freely rotatable.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410324931.7A CN104141751B (en) | 2014-07-09 | 2014-07-09 | Planetary gear type double-clutch speed changer |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410324931.7A CN104141751B (en) | 2014-07-09 | 2014-07-09 | Planetary gear type double-clutch speed changer |
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| CN104141751A CN104141751A (en) | 2014-11-12 |
| CN104141751B true CN104141751B (en) | 2016-09-14 |
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| CN104832607B (en) * | 2014-11-13 | 2017-09-29 | 北汽福田汽车股份有限公司 | Speed changer and the vehicle with the speed changer |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010144775A (en) * | 2008-12-17 | 2010-07-01 | Honda Motor Co Ltd | Multistage transmission |
| JP5084873B2 (en) * | 2010-06-15 | 2012-11-28 | 本田技研工業株式会社 | Multi-speed transmission |
| DE102012021599B4 (en) * | 2012-10-30 | 2018-10-04 | Audi Ag | Switching device for a dual-clutch transmission |
| US9022891B2 (en) * | 2012-11-08 | 2015-05-05 | Gm Global Technology Operations, Llc | Triple clutch multi-speed transmission |
| DE102012022777A1 (en) * | 2012-11-22 | 2014-05-22 | Daimler Ag | Dual clutch transmission i.e. jackshaft transmission, for powertrain of motor car, has idle gear arranged coaxial to sleeve shaft, and switch unit connecting another idle gear with sleeve shaft in torque-proof manner |
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2014
- 2014-07-09 CN CN201410324931.7A patent/CN104141751B/en not_active Expired - Fee Related
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| CN104141751A (en) | 2014-11-12 |
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