CN101900190B - Auto continuously variable transmission - Google Patents
Auto continuously variable transmission Download PDFInfo
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- CN101900190B CN101900190B CN2010102831995A CN201010283199A CN101900190B CN 101900190 B CN101900190 B CN 101900190B CN 2010102831995 A CN2010102831995 A CN 2010102831995A CN 201010283199 A CN201010283199 A CN 201010283199A CN 101900190 B CN101900190 B CN 101900190B
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Abstract
The invention relates to a multi-stage compound planetary gear type high-efficiency and high-power continuously variable transmission which is applicable to load-carrying vehicles, and comprises three planetary reducers J1, J2 and J3, input spit gears z1, z2 and z3, associated gears z4, z5, z6 and z7 and regulating motors D1 and D2. The transmission has large overall speed-regulating range, and can not only realize the step speed regulation, but also realize the stepless speed regulation in a small range in each stage and synthesize the stages for realizing the stepless speed regulation in a larger range; the device uses the power of an engine gear for splitting, the split power is further amplified by electric control and be regulatable, and then the differential motion synthesis way is further utilized for realizing the re-synthesis of the power, thereby achieving a constant-power output device which alternately changes the output torque and the rotation speed, and leading the electronic logic control way to be suitable for the running laws of the vehicle; and the power regulation of the device is realized by using the electromechanical rigid way.
Description
Technical field
The present invention relates to a kind of automotive transmission, relate in particular to a kind of heavy-load automobile continuously variable transmission device.
Background technique
The truck of commodity class adopts the speed change of manual multistage shift speed change (MT), planet multi-stage hydraulic control automatic gear shifting speed changing (AT), mechanical multistage electronic control shift speed change (AMT) and steel belt hydraulic control stepless change several kinds of forms such as (CVT) at present; The three kinds of speed change gears in front belong to gear has stepped gearing; MT controls complicacy, labor intensity is big, AT, AMT complex structure, cost height, and be the variation that step change makes automobile running incompatibility road conditions and load; Though CVT is a kind of stepless speed variator but belongs to a kind of friction type transmission; Surpass under certain load and skid, the heavy load operation of incompatibility lorry, manufacture cost is high.
Also have at present more planetary transmission patent about gear type come out as: Chinese patent document (1) CN101598194 carries out electronic differential compound speed governing with one-level planetary reducer and motor driving worm gear, worm screw; (2) CN1448646 leans on the differential speed regulation of mechanical friction wheel feedback planet, and its electronic differential compound speed governing and feedback complex speed control principle are regulated by friction wheel and realized planetary stepless transmission.The problem that the planetary pinion transmission of these two kinds of forms exists is: about first kind of compound velocity ratio i=1.2 of simple one-level planetary differential; Change too little; And mechanism can only speed governing can not increase bigger moment of torsion; The variation that can not provide the mechanism of good permanent power to adapt to road conditions to automobile, additional automatically controlled required electric driving power is bigger.Also there is the shortcoming of first kind of structure in second kind of problem that exists by the planet stepless speed changing mechanism of friction wheel feedback regulation, and friction wheel efficient is low, the electronic control speed change of incompatibility Hyundai Motor.
Summary of the invention
The purpose of this invention is to provide a kind of automobile that overcomes above-mentioned defective and use especially load-carrying stepless speed variator of vehicle.
Technological scheme of the present invention is:
A kind of auto continuously variable transmission; Comprise planetary reducer J1, planetary reducer J2, planetary reducer J3 and be used to import gear z1, gear z2, gear z3 and related external toothing z4, external toothing z5, gear shaft z6, external toothing z7 and motor D 1, the motor D 2 of shunting; It is characterized in that: engine output w1 is input to planetary reducer J1; W1 is assigned to and planetary reducer J2 through gear z1, gear z2, gear z3 parallel connection simultaneously, and planetary reducer J2 is a speed increaser, and motor D 1 is set on it; Motor D 1 is with self-locking, is used to regulate the output speed n5 of planetary reducer J2; Planetary reducer J1 is the planetary reducer of sun gear input, planet carrier output, the external toothing z5 of planetary reducer J1 and gear shaft z6 engagement, and gear shaft z6 connects motor D 2, and motor D 2 is with self-lockings, is used to regulate the output speed n4 of planetary reducer J1; The output of planetary reducer J2 is through the external toothing z4 engagement of its external toothing z7 and planetary reducer J3; Be input to planetary reducer J3; The output of planetary reducer J1 also is input to planetary reducer J3; Planetary reducer J3 is the differential planetary retarder, obtains one in the outlet of planetary reducer J3 with motor D 1, the corresponding speed n2 of motor D 2 forward and backwards adjusting variation, and synthetic speed changer output power w2 output.
This stepless speed variator is preferably planetary reducer J1 and comprises input shaft-sun gear za1 assembly parts, planet carrier-output shaft assembly parts, three small planetary gear zc1, ring gear zb1-external toothing z5 assembly parts; On case of transmission and planet carrier-output shaft assembly parts, planet carrier-output shaft assembly parts is through on the bearings case of transmission through bearings for said input shaft-sun gear za1 assembly parts; The sun gear za1 of input shaft-sun gear za1 assembly parts and three small planetary gear zc1 engagements, on planet carrier-output shaft assembly parts, while and ring gear zb1-external toothing z5 assembly parts mesh the planet wheel shaft of three small planetary gear zc1 through bearings; Ring gear zb1-external toothing z5 assembly parts passes through bearings on case of transmission.
This stepless speed variator is preferably motor D 2 output shafts and is fixed in the gear shaft z6 hole through flat key, and on case of transmission, the gear z5 of the ring gear zb1-external toothing assembly parts of gear shaft z6 and planetary reducer J1 meshes gear shaft z6 through bearings.
This stepless speed variator is preferably planetary reducer J3 and comprises sun gear za2, planet carrier-output shaft assembly parts, three small planetary gear zc2, ring gear zb2-external toothing z4 assembly parts; The spline of the planet carrier of said planetary reducer J1-output shaft assembly parts right-hand member inserts in the sun gear za2 endoporus of planetary reducer J3, and sun gear za2 passes through bearings on case of transmission; Planet carrier-output shaft assembly parts passes through bearings on case of transmission; Said sun gear za2 and three small planetary gear zc2 engagements, on planet carrier-output shaft assembly parts, while and ring gear zb2-external toothing z4 assembly parts mesh the planet wheel shaft of three small planetary gear zc2 through bearings; Ring gear zb2-external toothing z4 assembly parts passes through bearings on case of transmission.
This stepless speed variator is preferably planetary reducer J2 and comprises input shaft-planet carrier assembly parts, sun gear za3, three small planetary gear zc3, ring gear zb3-external toothing z7 assembly parts; Said input shaft-planet carrier assembly parts pass through bearings on case of transmission; Said sun gear za3 left end passes through bearings at the right endoporus of input shaft-planet carrier assembly parts; On case of transmission, the endoporus of sun gear za3 is connected with motor D 1 through spline right-hand member through bearings; Said sun gear za3 and three small planetary gear zc3 engagements; The planet wheel shaft of three small planetary gear zc3 passes through bearings on input shaft-planet carrier assembly parts; Mesh simultaneously and in the ring gear zb3-external toothing z7 assembly parts, ring gear zb3-external toothing z7 assembly parts passes through bearings on case of transmission; The ring gear zb2-external toothing z4 assembly parts outer gearing of said ring gear zb3-external toothing z7 assembly parts and planetary reducer J3.
This stepless speed variator is preferably said input shunting gear z1, gear z2, gear z3 and is fixed on input shaft-planet carrier assembly parts of input shaft-sun gear za1 assembly parts, axle, planetary reducer J2 of planetary reducer J1 with flat key respectively, and axle passes through bearings on case of transmission.
The housing of this speed changer is not an integral body; Consider from the angle that technology realizes; Can adopt the shell combination of a plurality of segmentations to form according to the needs of part assembling; As the gear z1, gear z2, the gear z3 that import shunting can be arranged in the housing, and planetary reducer J1, planetary reducer J2 and planetary reducer J3 can be respectively in housings separately.These are that those skilled in the art are easy to realize.
Stepless speed variator of the present invention can reach following effect and function:
1) the multistage composite planetary gear type efficient high power stepless speed variator that, is suitable for lorry;
2), the total speed adjustable range of this speed changer greatly not only can realize step speed regulation, but also can be implemented between each grade the stepless speed regulation that realizes among a small circle, combined realization stepless speed regulation in a big way to what;
3), this device is used the engine gear power dividing; Again shunting power automatically controlled amplification, adjustable in addition; And then the mode of utilizing differential motion to synthesize; Realize the synthetic more permanent power output device that reaches the alternate of output torque and rotating speed of power, and realize that the electronic logic control mode adapts to the moving law of automobile.
Description of drawings
Fig. 1 is the sectional view of a specific embodiment of stepless speed variator of the present invention.
Fig. 2 is the designs simplification schematic representation of a specific embodiment of stepless speed variator of the present invention.
Fig. 3 is the transmission of movement route schematic representation of a specific embodiment of stepless speed variator of the present invention.
Embodiment
Further specify enforcement of the present invention below in conjunction with accompanying drawing.
Fig. 2 and Fig. 3 are the designs simplification and the transmission of movement route schematic representation of this speed changer.This stepless speed variator comprises three planetary reducer J1, J2, J3 and input shunting gear z1, z2, z3 and related gear z4, z5, z6, z7 and gear motor D1, D2.Engine output w1 is input to the J1 planetary reducer; Be assigned to differential planetary reducer structure J2 through gear z1, z2, z3 parallel connection again; J2 is a speed increaser; Have the gear motor D1 of band self-locking to be used to regulate the output speed n5 of J2 on it, J1 is a conventional sun gear input, the planetary reducer of planet carrier output, also has the gear motor D2 of band self-locking to be used to regulate the output speed n4 of J1 on it.The output of J2 and J1 is input to differential planetary retarder J3 more respectively, obtains one in the outlet of J3 with gear motor D1, the corresponding speed n2 of D2 forward and backward adjusting variation, synthetic again speed changer output power w2 output.
Referring to Fig. 1, be the sectional view of a specific embodiment of this stepless speed variator:
On planet carrier-output shaft assembly parts 4 of left shell 28, planetary reducer J1 left shell 30 and planetary reducer J1, planet carrier-output shaft assembly parts 4 passes through bearings on planetary reducer J1 left shell 30 and planetary reducer J1 right shell body 8 to input shaft-sun gear za1 assembly parts 1 by bearings; Input shaft-sun gear za1 assembly parts 1 is through sun gear za132 and three small planetary gear zc1 2 engagements; On planet carrier-output shaft assembly parts 4, while and ring gear zb1-external toothing z5 assembly parts 3 mesh the planet wheel shaft 33 of three small planetary gear zc1 2 through bearings; Ring gear zb1-external toothing z5 assembly parts 3 passes through bearings on planetary reducer J1 left shell 30 and planetary reducer J1 right shell body 8.
Gear motor D2 5 left ends are connected with housing 6 screws; The output shaft of gear motor D2 5 is fixed in gear shaft z6 7 holes through flat key; Gear shaft z6 7 passes through bearings on housing 6; Housing 6 and planetary reducer J1 left shell 30 and planetary reducer J1 right shell body 8 link into an integrated entity the gear z5 engagement of the ring gear zb1-external toothing assembly parts 3 of gear shaft z6 7 and planetary reducer J1 through screw.
The spline of the planet carrier of planetary reducer J1-output shaft assembly parts 4 right-hand members inserts in sun gear za2 9 endoporus of planetary reducer J3, and sun gear za2 9 passes through bearings on planetary reducer J3 left shell 15 and planetary reducer J3 right shell body 14.
Planet carrier-output shaft assembly parts 13 passes through bearings on planetary reducer J3 left shell 15 and planetary reducer J3 right shell body 14; Sun gear za2 9 and three small planetary gear zc2 12 engagements, on planet carrier-output shaft assembly parts 13, while and ring gear zb2-external toothing z4 assembly parts 11 mesh the planet wheel shaft 10 of three small planetary gear zc2 12 through bearings; Ring gear zb2-external toothing z4 assembly parts 11 passes through bearings on planetary reducer J3 left shell 15 and planetary reducer J3 right shell body 14.
Gear z1 32, gear z2 31, gear z3 26 are fixed on input shaft-planet carrier assembly parts 27 of input shaft-sun gear za1 assembly parts 1, axle 29, planetary reducer J2 with flat key respectively; Axle 29 passes through bearings on left shell 28 and right shell body 25; On left shell 28, input shaft-planet carrier assembly parts 27 passes through bearings on planetary reducer J2 left shell 23 and planetary reducer J2 right shell body 17 to the left end of the input shaft of planetary reducer J2-planet carrier assembly parts 27 through bearings; Sun gear za3 19 left ends pass through bearings at input shaft-planet carrier assembly parts 27 right endoporus; Right-hand member passes through bearings on planetary reducer J2 right shell body 17; Sun gear za3 19 endoporus are connected with gear motor D1 18 through spline; Gear motor D1 18 shells are connected with planetary reducer J2 right shell body 17 through screw; Sun gear za3 19 and three small planetary gear zc3 22 engagements; Three small planetary gear zc3 22 planet wheel shafts 20 pass through bearings on input shaft-planet carrier assembly parts 27, mesh simultaneously and in the ring gear zb3-external toothing z7 assembly parts 21, and ring gear zb3-external toothing z7 assembly parts 21 passes through bearings on planetary reducer J2 left shell 23 and planetary reducer J2 right shell body 17; Ring gear zb3-external toothing z7 assembly parts 21 and 11 outer gearings of ring gear zb2-external toothing z4 assembly parts; Planetary reducer J2 left shell 23 is connected with housing 25 screws through connecting cylinder 24.
The concrete transmission of movement route of present embodiment is as shown in Figures 2 and 3:
Motor output speed n1 one tunnel transfer route through planetary reducer J1; Za1-zc1-zb1 is to planet carrier; 1), to act on the moving direction of planet carrier by D2-z6-z5-zb1 identical with the moving direction that n1-za1-zc1-zb1 acts on planet carrier producing two kinds of results by these two motions of gear motor D2 input z6-z5-zb1 with the synthetic back of its planet carrier in addition:, this retarder J1 speedup is moved.2), to act on the moving direction of planet carrier by D2-z6-z5-zb1 opposite with moving direction that n1-za1-zc1-zb1 acts on planet carrier, this retarder J1 retarded motion.
Another road of motor output speed n1 is through the transfer route planet carrier-zc3 of gear z1-z2-z3 to planetary reducer J2; 1), to act on the moving direction of planet carrier by D1-za3-zc3-zb3 identical with the moving direction that n1-z1-z2-z3-zc3 acts on planet carrier gear motor D1 input is producing two kinds of results by this two-way motion of za3-zc3-zb3 with the synthetic back of its planet carrier in addition:, this retarder J1 speedup is moved.2), to act on the moving direction of planet carrier by D1-za3-zc3-zb3 opposite with moving direction that n1-z1-z2-z3-zc3 acts on planet carrier, this retarder Z3 retarded motion.Move at last and accomplish output by J1-za2-zc2-zb2 and the synthetic back of J3-z4-zb2 J3.
Velocity ratio is analyzed: according to Fig. 2, shown in Figure 3:
Gear motor D1, when D2 is constant-seed motor, is just changeing (+), counter-rotating (-), stopping (0) and relation such as the following table of exporting gear (n2):
Can find out just changeing, reverse, stopping three states and just can realize 9 velocity variations of keeping off through control motor D 1, D2 from above-mentioned logical relation table.
Motor D 1, when D2 is variable speed machine, except by just changeing (+), counter-rotating (-), stop (0) and exporting the concerning the speed governing of gear (n2), also can be according to stepless variation between that this gear of speed adjustable range of D1, D2.
The computational process of velocity ratio is following:
Retarder J2:
Retarder J1:
Retarder J3:
Through the computational analysis to velocity ratio, the speed adjustable range of this speed changer can be the wherein variation of one-level, also can be the two-stage collaborative variation, has so just greatly increased speed adjustable range and speed-regulating mode.
Protection scope of the present invention is not limited to the above embodiments, and obviously, those skilled in the art can carry out various changes and distortion and do not depart from the scope of the present invention and spirit the present invention.If these changes and distortion belong in the scope of claim of the present invention and equivalent technologies thereof, then the intent of the present invention also comprises these changes and is out of shape interior.
Claims (6)
1. auto continuously variable transmission; Comprise planetary reducer J1, planetary reducer J2, planetary reducer J3 and be used to import gear z1, gear z2, gear z3 and related external toothing z4, external toothing z5, gear shaft z6, external toothing z7 and motor D 1 and the motor D 2 of shunting; It is characterized in that: engine output w1 is directly inputted to planetary reducer J1, and is assigned to planetary reducer J2 through gear z1, gear z2, gear z3 parallel connection; Planetary reducer J2 is a speed increaser, and motor D 1 is set on it, and motor D 1 is with self-locking, is used to regulate the output speed n5 of planetary reducer J2; Planetary reducer J1 is the planetary reducer of sun gear input, planet carrier output, the external toothing z5 of planetary reducer J1 and gear shaft z6 engagement, and gear shaft z6 connects motor D 2, and motor D 2 is with self-lockings, is used to regulate the output speed n4 of planetary reducer J2; The output of planetary reducer J2 is through the external toothing z4 engagement of its external toothing z7 and planetary reducer J3; Be input to planetary reducer J3; The output of planetary reducer J1 also is input to planetary reducer J3; Planetary reducer J3 is the differential planetary retarder, obtains one in the outlet of planetary reducer J3 with motor D 1, the corresponding speed n2 of motor D 2 forward and backwards adjusting variation, and synthetic speed changer output power w2 output.
2. auto continuously variable transmission according to claim 1; Wherein, planetary reducer J1 includes input shaft-sun gear za1 assembly parts (1), planet carrier-output shaft assembly parts (4), three small planetary gear zc1 (2), ring gear zb1-external toothing z5 assembly parts (3); On case of transmission and planet carrier-output shaft assembly parts (4), planet carrier-output shaft assembly parts (4) passes through bearings on case of transmission to said input shaft-sun gear za1 assembly parts (1) through bearings; The sun gear za1 of input shaft-sun gear za1 assembly parts (1) and three small planetary gear zc1 (2) engagement; On planet carrier-output shaft assembly parts (4), while and ring gear zb1-external toothing z5 assembly parts (3) mesh the planet wheel shaft (33) of three small planetary gear zc1 (1) through bearings; Ring gear zb1-external toothing z5 assembly parts (3) passes through bearings on case of transmission.
3. according to the auto continuously variable transmission of claim 2; Wherein, The output shaft of said motor D 2 (5) is fixed in gear shaft z6 (7) hole through flat key; On case of transmission, the external toothing z5 of the ring gear zb1-external toothing z5 assembly parts (3) of gear shaft z6 (7) and planetary reducer J1 meshes gear shaft z6 (7) through bearings.
4. according to the auto continuously variable transmission of claim 1 or 2; Wherein, said planetary reducer J3 comprises sun gear za2 (9), planet carrier-output shaft assembly parts (13), three small planetary gear zc2 (12), ring gear zb2-external toothing z4 assembly parts (11); The spline of the planet carrier of said planetary reducer J1-output shaft assembly parts (4) right-hand member inserts in sun gear za2 (9) endoporus of planetary reducer J3, and sun gear za2 (9) passes through bearings on case of transmission; The planet carrier of planetary reducer J3-output shaft assembly parts (13) passes through bearings on case of transmission; Said sun gear za2 (9) and three small planetary gear zc2 (12) engagement; On planet carrier-output shaft assembly parts (13) of planetary reducer J3, while and ring gear zb2-external toothing z4 assembly parts (11) mesh the planet wheel shaft (10) of three small planetary gear zc2 (12) through bearings; Ring gear zb2-external toothing z4 assembly parts (11) passes through bearings on case of transmission.
5. according to the auto continuously variable transmission of claim 1 or 2; Wherein, said planetary reducer J2 comprises input shaft-planet carrier assembly parts (27), sun gear za3 (19), three small planetary gear zc3 (22), ring gear zb3-external toothing z7 assembly parts (21); Said input shaft-planet carrier assembly parts (27) pass through bearings on case of transmission; Said sun gear za3 (19) left end passes through bearings at input shaft-right endoporus of planet carrier assembly parts (27); On case of transmission, the endoporus of sun gear za3 (19) is connected with motor D 1 (18) through spline right-hand member through bearings; Said sun gear za3 (19) and three small planetary gear zc3 (22) engagement; The planet wheel shaft (20) of three small planetary gear zc3 (22) passes through bearings on input shaft-planet carrier assembly parts (27); Mesh simultaneously and in the ring gear zb3-external toothing z7 assembly parts (21), ring gear zb3-external toothing z7 assembly parts (21) passes through bearings on case of transmission; Ring gear zb2-external toothing z4 assembly parts (11) outer gearing of said ring gear zb3-external toothing z7 assembly parts (21) and planetary reducer J3.
6. auto continuously variable transmission according to claim 1; Wherein, Said gear z1 (32), gear z2 (31), gear z3 (36) are fixed on input shaft-planet carrier assembly parts (27) of input shaft-sun gear za1 assembly parts (1), axle (29), planetary reducer J2 of planetary reducer J1 with flat key respectively, axle (29) through bearings on case of transmission.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010102831995A CN101900190B (en) | 2010-09-16 | 2010-09-16 | Auto continuously variable transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010102831995A CN101900190B (en) | 2010-09-16 | 2010-09-16 | Auto continuously variable transmission |
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| Publication Number | Publication Date |
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| CN101900190A CN101900190A (en) | 2010-12-01 |
| CN101900190B true CN101900190B (en) | 2012-05-23 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2010102831995A Expired - Fee Related CN101900190B (en) | 2010-09-16 | 2010-09-16 | Auto continuously variable transmission |
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Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN103032534A (en) * | 2011-10-06 | 2013-04-10 | 汤思查 | Force transfer continuously variable transmission with two-sided gear rings |
| CN107863845A (en) * | 2017-11-17 | 2018-03-30 | 浙江奥耐德电气科技有限公司 | The preceding preposition deceleration variable frequency motor of output |
| CN109915542A (en) * | 2019-04-02 | 2019-06-21 | 闫德林 | Applied to the Double-power transmission control device on mining equiment |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5453060A (en) * | 1992-03-16 | 1995-09-26 | Ishikawajima-Harima Jukogyo Kabushiki Kaisha | Power transmission for mechanical press |
| CN2848617Y (en) * | 2005-11-18 | 2006-12-20 | 比亚迪股份有限公司 | Improved power transmission system |
| CN200986008Y (en) * | 2006-12-21 | 2007-12-05 | 上海振华港口机械（集团）股份有限公司 | Planet differential brake device |
| CN201003576Y (en) * | 2007-02-06 | 2008-01-09 | 煤炭科学研究总院太原分院 | Gear change of crawler running mechanism |
| CN101149095A (en) * | 2007-10-25 | 2008-03-26 | 同济大学 | Hybrid power drive device based on double clutch automatic speed-changer |
| CN201763905U (en) * | 2010-09-16 | 2011-03-16 | 重庆嘉卡变速箱有限公司 | Automotive continuously variable transmission |
-
2010
- 2010-09-16 CN CN2010102831995A patent/CN101900190B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5453060A (en) * | 1992-03-16 | 1995-09-26 | Ishikawajima-Harima Jukogyo Kabushiki Kaisha | Power transmission for mechanical press |
| CN2848617Y (en) * | 2005-11-18 | 2006-12-20 | 比亚迪股份有限公司 | Improved power transmission system |
| CN200986008Y (en) * | 2006-12-21 | 2007-12-05 | 上海振华港口机械（集团）股份有限公司 | Planet differential brake device |
| CN201003576Y (en) * | 2007-02-06 | 2008-01-09 | 煤炭科学研究总院太原分院 | Gear change of crawler running mechanism |
| CN101149095A (en) * | 2007-10-25 | 2008-03-26 | 同济大学 | Hybrid power drive device based on double clutch automatic speed-changer |
| CN201763905U (en) * | 2010-09-16 | 2011-03-16 | 重庆嘉卡变速箱有限公司 | Automotive continuously variable transmission |
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