CN103273842A - Planet-gear differential device and hybrid power continuously variable transmission system and vehicle - Google Patents
Planet-gear differential device and hybrid power continuously variable transmission system and vehicle Download PDFInfo
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- CN103273842A CN103273842A CN2013102590259A CN201310259025A CN103273842A CN 103273842 A CN103273842 A CN 103273842A CN 2013102590259 A CN2013102590259 A CN 2013102590259A CN 201310259025 A CN201310259025 A CN 201310259025A CN 103273842 A CN103273842 A CN 103273842A
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Abstract
The invention relates to a differential device for a vehicle, in particular to a planet-gear differential device. The differential device comprises a gear ring. A differential mechanism is arranged in a planet carrier and comprises a first sun gear, a second sun gear, a first planet gear and a second planet gear. The first sun gear and the second sun gear are coaxial with the gear ring and arranged at an interval, the first planet gear is fixed on a rotary shaft rotatably connected onto the planet carrier and is meshed with the first sun gear, and the second planet gear is fixed on a rotary shaft rotatably connected onto the planet carrier and is meshed with the first planet gear and the second sun gear simultaneously, and the first planet gear and the second planet gear are coaxially arranged. Meanwhile, the invention further relates to a hybrid power continuously variable transmission system with the planet-gear differential device and a vehicle with the system. By means of the design of the planet-gear differential device, power is transmitted, the axial size of the device is reduced, and the cost is reduced.
Description
Technical field
The present invention relates to a kind of for motor vehicle differential gear, relate in particular to a kind of planetary gear differential device, the invention still further relates to a kind of have the hybrid variable-speed system of this planetary gear differential device and the vehicle with this system simultaneously.
Background technology
Along with society to improving constantly that energy-conserving and environment-protective require, each major company of the world drops into great amount of manpower one after another and financial resources are researched and developed the new forms of energy vehicle.Present various forms of hybrid power vehicle is released, wherein, Toyota general sharp this as research and development, the most successful hybrid power vehicle the earliest, developed into the third generation at present, the hybrid power system of Toyota is referred to as THS(and Toyoda hybrid system) hybrid power system, the core of THS hybrid power system is ECVT technology (electric controlling stepless variable speed technology), its ECVT that adopts mainly is made up of two planet rows, wherein, one of them planet row's the high-power motor deceleration of high speed that act as increases and turns round; Another planet row is responsible for power distribution, and this is the core of ECVT, and in the structure, driving engine connects pinion carrier in this section, and electrical generator connects sun wheel, and gear ring is responsible for power output.Adopt this structure, because it is gear ring is responsible for power output, therefore, higher to the gear ring requirement of strength, in addition, owing to adopt the structure of double planet wheel rows of mixing, make that its axial dimension is bigger, the layout that is unfavorable for preposition forerunner's hybrid vehicle, and technology acuracy requires and cost is higher, processing difficulties.
Summary of the invention
Be to solve the deficiencies in the prior art, the invention provides and a kind ofly dwindle axial dimension planetary gear differential device when guaranteeing power output, it can reduce its difficulty of processing.
For achieving the above object, planetary gear differential device of the present invention, it has:
Gear ring, it links to each other with the transmission shaft that transmits from drive source drives power;
Pinion carrier, with gear ring coaxial line and the setting that is connected, it forms the support to the box of tricks that is positioned at it;
Described box of tricks comprises first sun wheel and second sun wheel that arranges with gear ring coaxial line and spacing, be fixed on first satellite gear in the rotating shaft that is rotationally connected with on the pinion carrier, that link to each other with the engagement of first sun wheel, and be fixed in the rotating shaft that is rotationally connected with on the pinion carrier, mesh second satellite gear that links to each other simultaneously with first satellite gear and second sun wheel, described first satellite gear and the second satellite gear coaxial line arrange.
As the restriction to aforesaid way, described first satellite gear is uniform circumferential a plurality of of first sun wheel that are arranged on.
In addition, the present invention provides a kind of hybrid variable-speed system simultaneously, comprise the driving engine as drive source, electrical generator, planetary gear differential device, electrokinetic cell, electrical motor, the inverter that links to each other with electrical generator, electrokinetic cell and electrical motor, and the main reduction gear group that links to each other with the motor power mouth, described planetary gear differential device has aforesaid structure; The rotor coaxial line of described first sun wheel and electrical generator is connected, be provided with between driving engine and the planetary gear differential device in conjunction with the time rotary power of transmission shaft can be directly passed to the multiple disk clutch of first sun wheel; Also comprise the power take-off shaft that is connected with second sun wheel, but be provided with the Locking Device that the locking power take-off shaft rotates at power take-off shaft, and in conjunction with the time can the output power rotary power of axle flow to the power-transfer clutch of main reduction gear.
As the restriction to aforesaid way, interactional two groups of friction linings of described multiple disk clutch link to each other with transmission shaft, first sun wheel respectively.
The present invention also provides a kind of motor vehicle driven by mixed power, and it is that aforesaid hybrid variable-speed system is carried as the Poewr transmission mechanism that drives the vehicle front-wheel.
Adopt technical scheme of the present invention, design by the planetary gear differential apparatus structure, make the planetary gear differential device when realizing transmission of power, dwindled its axial dimension, reduced cost, and simultaneously with the power output gear of second sun wheel as the planetary gear differential device, to the requirement of gear ring intensity, and be beneficial to processing and manufacturing when having reduced gear ring as clutch end.
Description of drawings
Below in conjunction with the drawings and the specific embodiments, technical scheme of the present invention is done further to describe in detail:
Fig. 1 is the structure annexation simplified schematic diagram of the embodiment of the invention one;
Fig. 2 is the structure annexation simplified schematic diagram of the embodiment of the invention two;
Among the figure:
1, gear ring; 2, pinion carrier; 3, box of tricks; 31, first sun wheel; 32, second sun wheel; 33, first satellite gear; 34, second satellite gear; 35, first rotating shaft; 36, second rotating shaft; 37, connecting panel; 4, transmission shaft; 5, driving engine; 6, electrical generator; 7, electrokinetic cell; 8, electrical motor; 9, inverter; 10, main reduction gear group; 101, driving gear; 102, driven gear; 11, axle sleeve; 12, multiple disk clutch; 13, power take-off shaft; 14, Locking Device; 15, power-transfer clutch.
The specific embodiment
Embodiment one
Present embodiment relates to a kind of planetary gear differential device, by shown in Figure 1, it comprises gear ring 1, it links to each other with the transmission shaft 4 of transmission as described below from drive source drives power, in the present embodiment, the middle part of gear ring 1, radially be fixed with connecting panel 37 along it, transmission shaft directly is connected in the center of connecting panel 37; Pinion carrier 2, with gear ring 1 coaxial line and the setting that is connected, it forms the support to the box of tricks 3 that is positioned at it.
Box of tricks 3 comprises with first sun wheel 31 of gear ring 1 coaxial line and second sun wheel, 32, the first sun wheels 31 and second sun wheel 32 in the axial spacing setting of the two.Box of tricks 3 also comprises first satellite gear 33 that links to each other with 31 engagements of first sun wheel, and second satellite gear 34 that links to each other with 32 engagements of second sun wheel.For realizing first setting of satellite gear 33 on pinion carrier 2, pinion carrier 2 be connected with first rotating shaft, 35, the first rotating shafts 35 can be on pinion carrier 2 serve as that axle rotates with self axis, 33 of first satellite gears are fixed in first rotating shaft 35; For realizing second setting of satellite gear 34 on pinion carrier 2, pinion carrier 2 be connected with second rotating shaft, 36, the second rotating shafts 36 can be on pinion carrier 2 serve as that axle rotates with self axis, 34 of second satellite gears are fixed in second rotating shaft 36; First rotating shaft 35 and second rotating shaft, 36 coaxial line settings, and first satellite gear 33 links to each other with 34 engagements of second satellite gear.
In the present embodiment, first satellite gear 33 is identical with the quantity of second satellite gear 34, and first satellite gear 33 is two, the footpath that these two first planetary wheels 33 are arranged on first sun wheel 31 upwards so that first satellite gear 33 is along the circumferential uniform setting of first sun wheel 31.Accordingly, second satellite gear 34 is two, the footpath that these two second satellite gears 34 are arranged on second sun wheel 32 upwards so that second satellite gear 34 is along the circumferential uniform setting of second sun wheel 32.
In use, drive source drives transmission shaft and rotates, transmission shaft drives gear ring 1 and rotates, because pinion carrier 2 is connected with gear ring 1, pinion carrier 2 is rotated synchronously, because the rotation of pinion carrier 2 drives first satellite gear 33 and second satellite gear 34 that arrange on it and revolves round the sun or rotation around first sun wheel 31 and second sun wheel 32, realization is to the transmission of power, and its detailed process will be described in detail in the following embodiments.
Embodiment two
Present embodiment relates to a kind of hybrid variable-speed system, is the concrete application to embodiment one planet gear differential gear.By shown in Figure 2, it comprises the driving engine 5 as drive source, electrical generator 6, the planetary gear differential device, electrokinetic cell 7, electrical motor 8, the inverter 9 that links to each other with electrical generator 6, electrokinetic cell 7 and electrical motor 8, and the main reduction gear group 10 that links to each other with electrical motor 8 clutch ends, main reduction gear group 10 comprises the driving gear 101 that links to each other with driving engine 8 power take-off shafts and the driven gear 102 that meshes with driving gear 101.Wherein, the planetary gear differential device has the structure of embodiment one.
In addition, in the structure of present embodiment, also comprise the power take-off shaft 13 that is connected with second sun wheel 32, be provided with Locking Device 14 at power take-off shaft 13, the effect of this Locking Device 14 is lockings that power take-off shaft 13 is rotated, and namely when Locking Device 14 lockings, power take-off shaft 13 can not rotate, and when Locking Device 14 disconnected, power take-off shaft 13 can rotate.
On the power take-off shaft 13 between Locking Device 14 and the driving gear 101, also be provided with power-transfer clutch 15, power-transfer clutch 15 in conjunction with the time, power take-off shaft 13 can directly send power to driving gear 101, thereby drive the rotation of driving gear 101, when power-transfer clutch 15 disconnected, the power transmission between power take-off shaft 13 and the master control gear 101 was interrupted.
Present embodiment is arranged on preposition forerunner's the motor vehicle driven by mixed power as the Poewr transmission mechanism that drives the vehicle front-wheel, followingly only its six different operational modes is described.
The one, series model, this kind pattern generally is applied to the situation of low speed and electrokinetic cell 7 electric weight deficiencies.Under this pattern, control Locking Device 14 axle that outputs power is 13 locked, and power-transfer clutch 15 disconnects, and multiple disk clutch 12 disconnects.Axle 13 is locked because Locking Device 14 outputs power, and power take-off shaft 13 can not rotate, therefore, and second sun wheel, 32 transfixions.Driving engine 5 operations also drive transmission shaft 4 rotations, and gear ring 1 drives pinion carrier 2 and rotates.At this moment, because second sun wheel, 32 transfixions, when second satellite gear 34 links to each other with 33 engagements of first satellite gear, first satellite gear 33 revolves round the sun around first sun wheel 31, second satellite gear 34 revolves round the sun around second sun wheel 32, and rotation does not all take place for first satellite gear 33 and second satellite gear 34.Because first satellite gear 33 is around the revolution of first sun wheel 31, and then drive first sun wheel 31 and rotate, this moment, the rotating speed of first sun wheel 31 was identical with the rotating speed of transmission shaft 4, the rotor that first sun wheel 31 drives electrical generator 6 rotates, electrical generator 6 generating and pass to inverter 9 after, pass to electrical motor 8, electrical motor 8 drives driving gear 101 and drives driven gear 102 rotations, thus outputting power.
The 2nd, paralleling model, this pattern be mainly used in the speed of a motor vehicle higher, meet bigger vehicle working condition.Under this pattern, Locking Device 14 disconnects, power-transfer clutch 15 combinations, and multiple disk clutch 12 disconnects.At this moment, driving engine 5 outputting powers, transmission shaft 4 drives gear ring 1 and pinion carrier 2 is rotated synchronously, pinion carrier 2 drives first satellite gear 33 and second satellite gear 34 revolves round the sun around first sun wheel 31 and second sun wheel 32 respectively, this revolution drives first sun wheel 31 and second sun wheel 32 is rotated, at this moment, the direct current (DC) that vehicle ECU control inverter 9 does not receive from electrical generator 6, second sun wheel 32 drives power take-off shaft 13 and rotates, power take-off shaft 13 drives driving gear 101 and rotates, simultaneously, the electric weight that stores in the electrokinetic cell 7 passes to inverter 9, inverter 9 control electrical motors 8 drive driving gear 101 simultaneously and rotate, and finally output power by driven gear 102.
The 3rd, series-parallel connection pattern, this pattern are mainly used in the operating mode that the more common speed of a motor vehicle is higher or load is bigger.Under this pattern, Locking Device 14 disconnects, power-transfer clutch 15 combinations, and multiple disk clutch 12 disconnects.This kind pattern and above-mentioned second kind of pattern are basic identical, and difference is that vehicle ECU control inverter 9 receives the electric weight that electrical generator 6 produces, and the electric weight that will receive after transforming flows to electrical motor 8 simultaneously.
The 4th, electric-only mode, this kind pattern is applied to the operating mode of the lower and electrokinetic cell 7 electric weight abundances of the speed of a motor vehicle, and under this operating mode, engine efficiency is lower, and therefore, it is comparatively economical to use electric model.Under this pattern, Locking Device 14 disconnects, and power-transfer clutch 15 disconnects, and multiple disk clutch 12 disconnects.At this moment, driving engine 5 is not worked, by electrokinetic cell 7 electric energy stored is flowed to inverter 9 after, drive main reduction gears 101 by electrical motor 8 and rotate, and then drive driven gear 102 and rotate with outputting power.
The 5th, ICE pattern, this kind pattern are applicable to vehicle high speed state only by engine drive, and its transmission efficiency is higher.Under this pattern, Locking Device 14 disconnects power-transfer clutch 15 combinations, multiple disk clutch 12 combinations.At this moment, driving engine 5 flows to first sun wheel 31 and gear ring 1 simultaneously with power, and the rotating speed of the two is identical, gear ring 1 drives pinion carrier 2 and rotates synchronously, because first satellite gear 33 and 34 engagements of second satellite gear, and first sun wheel 31 is identical with the rotating speed of pinion carrier 2, first satellite gear 33 just revolves round the sun around first sun wheel 31, itself not rotation, simultaneously, second satellite gear 34 is around 32 revolution of second sun wheel, himself not rotation equally because the revolution of second satellite gear 34, drives second sun wheel 32 to rotate with the same rotating speed of transmission shaft 4, second sun wheel 32 drives power take-off shaft 13 and rotates, and then with a transmission of power driving gear 101.Under this state, whole planetary gear differential device is inoperative, is equivalent to a rigid shaft, and directly the power with driving engine flows to main reduction gear group 10.
The 6th, the energy take-back model, this pattern is applicable to the out-of-run vehicle idling situation of driving engine.In this pattern, Locking Device 14 disconnects, and power-transfer clutch 15 disconnects, and multiple disk clutch 12 disconnects.Main reduction gear group 10 passes to inverter with energy by electrical motor, and the electric weight of Chan Shenging passes to electrokinetic cell the most at last, realizes the charging to electrokinetic cell.
More than six kinds of operational modes, vehicle can be selected automatically according to running conditions such as road, the speed of a motor vehicle, loads, and can be according to the electric weight situation of electrokinetic cell, under operating mode arbitrarily, by vehicle ECU control electrical generator electrokinetic cell is charged.
Claims (5)
1. planetary gear differential device is characterized in that having:
Gear ring, it links to each other with the transmission shaft that transmits from drive source drives power;
Pinion carrier, with gear ring coaxial line and the setting that is connected, it forms the support to the box of tricks that is positioned at it;
Described box of tricks comprises first sun wheel and second sun wheel that arranges with gear ring coaxial line and spacing, be fixed on first satellite gear in the rotating shaft that is rotationally connected with on the pinion carrier, that link to each other with the engagement of first sun wheel, and be fixed in the rotating shaft that is rotationally connected with on the pinion carrier, mesh second satellite gear that links to each other simultaneously with first satellite gear and second sun wheel, described first satellite gear and the second satellite gear coaxial line arrange.
2. planetary gear differential device according to claim 1 is characterized in that: described first satellite gear is uniform circumferential a plurality of of first sun wheel that are arranged on.
3. hybrid variable-speed system, comprise the driving engine as drive source, electrical generator, the planetary gear differential device, electrokinetic cell, electrical motor, the inverter that links to each other with electrical generator, electrokinetic cell and electrical motor, and the main reduction gear group that links to each other with the motor power mouth, it is characterized in that: described planetary gear differential device has structure as claimed in claim 1 or 2; The rotor coaxial line of described first sun wheel and electrical generator is connected, be provided with between driving engine and the planetary gear differential device in conjunction with the time rotary power of transmission shaft can be directly passed to the multiple disk clutch of first sun wheel; Also comprise the power take-off shaft that is connected with second sun wheel, but be provided with the Locking Device that the locking power take-off shaft rotates at power take-off shaft, and in conjunction with the time can the output power rotary power of axle flow to the power-transfer clutch of main reduction gear.
4. hybrid variable-speed according to claim 3 system, it is characterized in that: interactional two groups of friction linings of described multiple disk clutch link to each other with transmission shaft, first sun wheel respectively.
5. motor vehicle driven by mixed power is characterized in that: claim 3 or 4 described hybrid variable-speed systems are carried as the Poewr transmission mechanism that drives the vehicle front-wheel.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013102590259A CN103273842A (en) | 2013-06-26 | 2013-06-26 | Planet-gear differential device and hybrid power continuously variable transmission system and vehicle |
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| Application Number | Priority Date | Filing Date | Title |
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| CN2013102590259A CN103273842A (en) | 2013-06-26 | 2013-06-26 | Planet-gear differential device and hybrid power continuously variable transmission system and vehicle |
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| CN103273842A true CN103273842A (en) | 2013-09-04 |
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| CN2013102590259A Pending CN103273842A (en) | 2013-06-26 | 2013-06-26 | Planet-gear differential device and hybrid power continuously variable transmission system and vehicle |
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106458020A (en) * | 2014-04-30 | 2017-02-22 | Gkn动力传动系统国际公司 | Selectable differential |
| WO2017050101A1 (en) * | 2015-09-25 | 2017-03-30 | 比亚迪股份有限公司 | Power driving system and vehicle having same |
| CN107676570A (en) * | 2017-11-02 | 2018-02-09 | 西安石油大学 | Self-adapting pipe robot under complex working condition |
| CN107685828A (en) * | 2017-09-19 | 2018-02-13 | 八方电气(苏州)股份有限公司 | Electric bicycle infinitely variable speed transmission |
| CN109421525A (en) * | 2017-09-01 | 2019-03-05 | 三菱自动车工业株式会社 | Driving force adjustment equipment |
| CN113246714A (en) * | 2021-03-25 | 2021-08-13 | 陈伟 | Power transmission system for vehicle and vehicle |
| CN115042610A (en) * | 2021-03-09 | 2022-09-13 | 比亚迪股份有限公司 | Hybrid power system and vehicle with same |
| WO2024044904A1 (en) * | 2022-08-29 | 2024-03-07 | 宁德时代(上海)智能科技有限公司 | Differential device and electric device |
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| WO2004089680A1 (en) * | 1994-06-06 | 2004-10-21 | Shuzo Moroto | Hybrid vehicle |
| US20090082171A1 (en) * | 2007-09-10 | 2009-03-26 | Gm Global Technology Operations, Inc. | Output Split Electrically-Variable Transmission with Electric Propulsion Using One or Two Motors |
| WO2013013960A1 (en) * | 2011-07-28 | 2013-01-31 | Schaeffler Technologies AG & Co. KG | Spur-gear differential |
| CN102951007A (en) * | 2012-11-20 | 2013-03-06 | 长城汽车股份有限公司 | Power distribution device of hybrid power automobile |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4677876A (en) * | 1984-02-13 | 1987-07-07 | Tractech, Inc. | Torque-proportioning differential with cylindrical spacer |
| WO2004089680A1 (en) * | 1994-06-06 | 2004-10-21 | Shuzo Moroto | Hybrid vehicle |
| US20090082171A1 (en) * | 2007-09-10 | 2009-03-26 | Gm Global Technology Operations, Inc. | Output Split Electrically-Variable Transmission with Electric Propulsion Using One or Two Motors |
| WO2013013960A1 (en) * | 2011-07-28 | 2013-01-31 | Schaeffler Technologies AG & Co. KG | Spur-gear differential |
| CN102951007A (en) * | 2012-11-20 | 2013-03-06 | 长城汽车股份有限公司 | Power distribution device of hybrid power automobile |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106458020A (en) * | 2014-04-30 | 2017-02-22 | Gkn动力传动系统国际公司 | Selectable differential |
| US10052950B2 (en) | 2014-04-30 | 2018-08-21 | Gkn Automotive Ltd. | Selectable differential |
| CN106458020B (en) * | 2014-04-30 | 2019-06-11 | 吉凯恩汽车有限公司 | Selective differential mechanism |
| WO2017050101A1 (en) * | 2015-09-25 | 2017-03-30 | 比亚迪股份有限公司 | Power driving system and vehicle having same |
| CN109421525A (en) * | 2017-09-01 | 2019-03-05 | 三菱自动车工业株式会社 | Driving force adjustment equipment |
| CN107685828A (en) * | 2017-09-19 | 2018-02-13 | 八方电气(苏州)股份有限公司 | Electric bicycle infinitely variable speed transmission |
| CN107676570A (en) * | 2017-11-02 | 2018-02-09 | 西安石油大学 | Self-adapting pipe robot under complex working condition |
| CN107676570B (en) * | 2017-11-02 | 2023-09-01 | 西安石油大学 | Self-adaptive pipeline robot under complex working condition |
| CN115042610A (en) * | 2021-03-09 | 2022-09-13 | 比亚迪股份有限公司 | Hybrid power system and vehicle with same |
| CN113246714A (en) * | 2021-03-25 | 2021-08-13 | 陈伟 | Power transmission system for vehicle and vehicle |
| WO2024044904A1 (en) * | 2022-08-29 | 2024-03-07 | 宁德时代(上海)智能科技有限公司 | Differential device and electric device |
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Application publication date: 20130904 |