CN1294992A - Automatic variable-speed drive system - Google Patents
Automatic variable-speed drive system Download PDFInfo
- Publication number
- CN1294992A CN1294992A CN00121619A CN00121619A CN1294992A CN 1294992 A CN1294992 A CN 1294992A CN 00121619 A CN00121619 A CN 00121619A CN 00121619 A CN00121619 A CN 00121619A CN 1294992 A CN1294992 A CN 1294992A
- Authority
- CN
- China
- Prior art keywords
- simple planetary
- clutch
- gear
- planetary group
- group
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
-
- 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
-
- 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
- F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
A power train for an automatic transmission is disclosed, including a composite planetary gear set. The set of planetary gears incorporates a first and second set of single planetary gears. One planetary gear holder of the first set is connected to a hollow wheel of the second set. A hollow wheel of the first set is connected to a planetary wheel holder of the second set. One planetary wheel holder of the first set acts as reaction element. A input device is set. One drive mechanism is set, and first one-way cluth is positioned between a gear housing and one element of the second set. Second one-way clutch selectively connects the first one-way coupling and the sun wheel of the second set.
Description
The present invention relates to an automatic variable-speed drive system, and especially relate to, make and to carry out the automatic variable-speed drive system that asynchronous gear shift improves shift feel to all shift rangies by using two free-wheel clutchs and a conventional power-transfer clutch.
A derailleur control device that is included in the automatic transmission with hydraulic torque converter is automatically controlled a gear shift ratio according to the variation of the speed of a motor vehicle and load.One compound miniature gears compound planet gear is as the multistage gearshift in the derailleur control device.
Compound planet gear generally includes an input component that is used to receive engine power; Be used for engine power is passed to an output of a main reduction gear after speed change; Be passed to a reaction member of output after the certain limit in speed change with the engine power that is used to make input component to receive.Output is fixedly joined on the main reduction gear usually.But because input component changes, input component is just by placing a friction member therebetween to be connected on the element that transmits engine power.In like manner, reaction member is also by placing a friction member therebetween to be connected on the case of transmission.
Such friction member can be divided into drg and power-transfer clutch substantially, and it has as a power-transfer clutch of input component with as a drg of reaction member.And a free-wheel clutch can be used to carry out asynchronous gear shift.
Numerous traditional automatic variable-speed drive system with above-mentioned feature is disclosed.One structure of an automatic variable-speed drive system like this is shown among Fig. 4.One dual planetary gear group 50 is center piece of this transmission system.In one first speed of drive range D, a first clutch C1 and one first free-wheel clutch F1 engagement; In the second speed of drive range D, first clutch C1, one the 3rd drg B3 and one second free-wheel clutch F2 engagement; In the third speed of drive range D, first clutch C1 and second clutch C2 engagement; In one the 4th speed of drive range D, second clutch C2, one second drg B2 and drg B3 engagement; In a reverse gear scope R, second clutch C2 and one first drg B1 engagement.
As mentioned above, realized asynchronous gear shift by the operation free-wheel clutch to first and second speed of drive range D.But owing to carry out synchronized gear shift when third and fourth speed of drive range D is arrived in gear shift, if in of short duration shift intervals, the bad timing between the engagement of friction member and the disengagement is true, then can cause various problems.Especially, the stall of driving engine possibility perhaps may take place otherwise the impaired retardance phenomenon of friction member, thus otherwise the high-speed operation phenomenon that the temporary transient free wheel gear shift engine speed of change-speed box sharply rises.All these problems have influenced shift feel greatly.
Though proposed to improve the engagement of friction member and timer-operated design and the method between the disengagement, such prior art structure is very complicated and can not fundamentally solve the problem relevant with synchronized gear shift.
The present invention is devoted to address the above problem.
A purpose of the present invention provides an automatic variable-speed drive system, wherein by using two free-wheel clutchs and a conventional power-transfer clutch, makes and can asynchronous gear shift improve shift feel to all shift rangies.
For achieving the above object, the invention provides a kind of automatic transmission drive train, comprise: a dual planetary gear group, this gear cluster comprises one first simple planetary group and one second simple planetary group, one pinion carrier of the first simple planetary group is fixedly joined on the gear ring of the second simple planetary group, and a gear ring of the first simple planetary group is fixedly joined on the pinion carrier of the second simple planetary group, and the pinion carrier of the first simple planetary group is operated as a reaction member; Be used for a input media that three elements of the first and second simple planetary groups are operated selectively as input component; Be used for two brake gears that element is operated selectively as reaction member with the first and second simple planetary groups; One first free-wheel clutch is placed between the element of a case of transmission and the second simple planetary group, thereby when gear shift during to first and second speed, this element is operated as a reaction member, and when gear shift during to third and fourth speed, this element is manipulated into free gear; One second free-wheel clutch is placed between the pinion carrier of first free-wheel clutch and the second simple planetary group; A clutch equipment that is connected with each other selectively with a sun gear that is used for first free-wheel clutch and the second simple planetary group.
According to a feature of the present invention, input media comprises the sun gear that places the first simple planetary group and the first clutch between the input shaft, place the pinion carrier of the second simple planetary group and the second clutch between the input shaft, and place the sun gear of the second simple planetary group and the three-clutch between the input shaft.
According to another characteristic of the invention, brake gear comprises one first drg that places between case of transmission and a connector, and this adaptor union is connected with each other the gear ring of the first simple planetary group and the pinion carrier of the second simple planetary group; And place one second drg between the sun gear of the case of transmission and the second simple planetary group.
According to a feature more of the present invention, clutch equipment is a multidisc clutch, and this multidisc clutch places between the sun gear of a connector and the second simple planetary group, and described adaptor union connects first and second free-wheel clutchs.
According to an also feature of the present invention, first clutch, second clutch and three-clutch are multidisc clutchs.
According to another feature of the present invention, first drg and second drg are polydisc clamping shape power-transfer clutchs.
Be incorporated into this accompanying drawing that also constitutes a specification sheets part and represented one embodiment of the invention, itself and specification sheets one are used from explains principle of the present invention:
Fig. 1 is a scheme drawing of one transmission system of one first preferred embodiment according to the present invention;
Fig. 2 is a scheme drawing of a transmission system of the present invention's one second preferred embodiment;
Fig. 3 is an operating chart of the interior friction member of each shift range of transmission system shown in Figure 1; With
Fig. 4 is a scheme drawing of a traditional transmission system.
Describe the preferred embodiments of the present invention with reference to the accompanying drawings in detail.
Fig. 1 represents a scheme drawing of one transmission system of one first preferred embodiment according to the present invention.
The power of one driving engine E is delivered to a dual planetary gear group 1 by the torque converter T that a bent axle and the fluid between the change-speed box as driving engine E link through an input shaft 9.The predetermined speed of gear shift in dual planetary gear group 1, power is passed on the main reduction gear (not shown) through a transmission driven wheel 3 then.
Dual planetary gear group 1 comprises one first simple compound planet gear 5 and one second simple compound planet gear 7.One pinion carrier Ca1 of the first simple planetary group 5 is fixedly joined on the gear ring R2 of the second simple planetary group 7, and a gear ring R1 of the first simple planetary group 5 is fixedly joined on the pinion carrier Ca2 of the second simple planetary group 7.
Realize the gear shift of dual planetary gear group 1 as a particular components of an input component or a reaction member by operation.Though select which element can change as input component or reaction member, the element that is used as output remains unchanged.That is, the pinion carrier Cal of the first simple planetary group 5 is fixedly joined on the transmission driven wheel 3, thereby as output.
In order to change input component, first, second and three-clutch C1, C2, C3 are placed between the input shaft 9 and particular components of dual planetary gear group 1.In order to change reaction member, the first and second drg B1, B2 are arranged between the particular components of a case of transmission 11 and dual planetary gear group 1.Below these variations will be described in more detail.
In order asynchronous gear shift to arrive all scopes, the first and second free-wheel clutch F1, F2 are placed between case of transmission 11 and one second adaptor union 13, and this first adaptor union 13 is connected with each other the pinion carrier Ca2 of the second simple planetary group 7 and the gear ring R1 of the first simple planetary group 5.Thus, the rotation of the gear ring R1 of the pinion carrier Ca2 of the second simple planetary group 7 and the first simple planetary group 5 can be limited to a single direction.In addition, a four clutches C4 is placed between the sun gear S2 of one second adaptor union 15 and the second simple planetary group 7, wherein this second adaptor union 15 is connected with each other the first and second power-transfer clutch F1, F2.
To describe first, second, third and four clutches C1, C2, C3, C4 below in more detail; The first and second drg B1, B2; And location and the operation of the first and second free-wheel clutch F1, F2.
First clutch C1 is placed between the sun gear S1 and input shaft 9 of the first simple planetary group 5.By engagement with disconnect first clutch C1, engine power is with first, second and third speed in the drive range D; First and second speed in the low-speed range 2; And the speed in the low-speed range L passes to the sun gear S1 of the first simple planetary group 5 selectively.
Second clutch C2 is placed between the pinion carrier Ca2 and input shaft 9 of the second simple planetary group 7.Therefore, by engagement and the disconnection of second clutch C2, engine power is delivered to the pinion carrier Ca2 of the second simple planetary group 7 selectively with third and fourth speed in the drive range D.
Three-clutch C3 is placed between the sun gear S2 and input shaft 9 of the second simple planetary group 7, and engagement and disconnection are to pass to engine power the sun gear S2 of the second simple planetary group 7 selectively with the speed in the reverse gear scope R.
The first drg B1 is placed between first adaptor union 13 and the case of transmission 11, and this first adaptor union 13 is connected with each other the pinion carrier Ca2 of the second simple planetary group 7 and the gear ring R1 of the first simple planetary group 5 as mentioned above.By engagement with disconnect the first drg B1, the rotation of the gear ring R1 of the first simple planetary group 5 and the pinion carrier Ca2 of the second simple planetary group 7 can be limited in reverse gear scope R and the low-speed range L, thereby gear ring R1 and pinion carrier Ca2 are as reaction member.
The second drg B2 is placed between the sun gear S2 and case of transmission 11 of the second simple planetary group 7.By meshing and disconnecting the second drg B2, the rotation of the sun gear S2 of the second simple planetary group 7 is limited in the second and the 4th speed of drive range D and the second speed of low-speed range 2, thereby sun gear S2 is as a reaction member.
The first and second free-wheel clutch F1, F2 are placed between first adaptor union 13 and the case of transmission 11, and this first adaptor union 13 is connected with each other the pinion carrier Ca2 of the second simple planetary group 7 and the gear ring R1 of the first simple planetary group 5 as mentioned above.By engagement with disconnect the first and second free-wheel clutch F1, F2, the rotation of the gear ring R1 of the first simple planetary group 5 and the pinion carrier Ca2 of the second simple planetary group 7 can be limited in first speed of drive range D and low-speed range 2, thereby gear ring R1 and pinion carrier Ca2 are as reaction member.
In addition, in the second speed of drive range D, the first free-wheel clutch F1 and four clutches C4 engagement limit the rotation of the sun gear S2 of the second simple planetary group 7, thereby sun gear S2 are as reaction member.Four clutches C4 is placed between the sun gear S2 of second adaptor union 15 and the second simple planetary group 7, and be connected on the second drg B2 and the three-clutch c3, wherein said second adaptor union 15 is connected with each other the first and second free-wheel clutch F1, F2.
Fig. 3 represents an operating chart of the friction member in each shift range of transmission system of first preferred embodiment of the invention.
Friction member meshes with different combinations and throws off, and arrives in all speed and scope with asynchronous gear shift.That is, in first speed of drive range D, first clutch C1, the first free-wheel clutch F1 and second free-wheel clutch F2 engagement; In the second speed of drive range D, first and four clutches C1, C4, the second drg B2 and the first free-wheel clutch F1; In the third speed of drive range D, first, second and four clutches C1, C2, C4 mesh; In the 4th speed of drive range D, second clutch C2, four clutches C4 and second drg B2 engagement; In reverse gear scope R, three-clutch C3 and first drg B1 engagement.
In third and fourth speed of drive range D, because the first free-wheel clutch F1 disconnects, therefore the engagement of four clutches C4 is for not influence of gear shift.In addition, by first, second and four clutches C1, C2, C4 in the third speed of engagement drive range D, dual planetary gear group 1 just is driven as an integral unit, and the engine power that is delivered to the pinion carrier Ca2 of the sun gear S1 of the first simple planetary group 5 and the second simple planetary group 7 just is directly delivered on the driven wheel 3 through the pinion carrier Ca1 of the first simple planetary group 5, and need not at first to pass through gear shift.
For the 4th speed from the third speed gear shift of drive range D to drive range D, derailleur control device just disconnects first clutch C1, and keeps an engine operation to drive power by the four clutches C4 and the second free-wheel clutch F2.Therefore, in this gearshift procedure, only mesh the second drg B2 in addition, thereby can obtain to be used for a simple structure of a hydraulic control system.
As a result, the engine speed that passes to the pinion carrier Ca2 of the second simple planetary group 7 through second clutch C2 is amplified by the sun gear S2 of the second simple planetary group 7, and this sun gear S2 operates as a reaction member by the engagement second drg B2.The engine speed that is exaggerated passes to transmission driven wheel 3 through the pinion carrier Ca1 of the first simple planetary group 5 then.
Fig. 2 represents a scheme drawing of one transmission system of one second preferred embodiment according to the present invention.
In the transmission system of second preferred embodiment of the present invention, input component is arranged on a side that is adjacent to torque converter T of dual planetary gear group 1.This makes more compact structure.The remainder of transmission system is identical structure and operating aspect and first preferred embodiment.Therefore, do not provide its detailed description.
In the transmission system of first and second preferred embodiments of the invention described above, when from third speed gear shift to the four speed of drive range D, realized asynchronous gear shift, thereby the open circuited time of first clutch C1 and the second drg B2 ingear time do not need exactly regularly.That is, all can carry out asynchronous gear shift, improve shift feel thus for all gear shift.
And, when gear shift during to the second speed of the second and the 4th speed of drive range D and low-speed range 2, because only by second drg B2 control gear shift, therefore the fluid control that puts on the transmission system can be constructed simply.
Though described the preferred embodiments of the present invention above in detail, but understand with should be understood that: for the person of ordinary skill of the art, in many variations of this basic inventive concept of instructing and/or revise and still fall in the aim of the present invention and scope that limits by claims.
Claims (6)
1. automatic transmission drive train comprises:
One dual planetary gear group, this gear cluster comprises one first simple planetary group and one second simple planetary group, one pinion carrier of the first simple planetary group is fixedly joined on the gear ring of the second simple planetary group, and a gear ring of the first simple planetary group is fixedly joined on the pinion carrier of the second simple planetary group, and the pinion carrier of the first simple planetary group is operated as a reaction member;
Be used for three input medias that element is operated selectively as input component with the first and second simple planetary groups;
Be used for two brake gears that element is operated selectively as reaction member with the first and second simple planetary groups;
Place one first free-wheel clutch between the element of a case of transmission and the second simple planetary group, thereby when gear shift during to first and second speed, this element is operated as a reaction member, and when gear shift during to third and fourth speed, this element is manipulated into free gear;
Place one second free-wheel clutch between the pinion carrier of first free-wheel clutch and the second simple planetary group; With
Be used for the clutch equipment that the sun gear with first free-wheel clutch and the second simple planetary group is connected with each other selectively.
2. transmission system as claimed in claim 1 is characterized in that input media comprises:
Place a sun gear of the first simple planetary group and the first clutch between the input shaft;
Place the pinion carrier of the second simple planetary group and the second clutch between the input shaft; With
Place the sun gear of the second simple planetary group and the three-clutch between the input shaft.
3. transmission system as claimed in claim 1 is characterized in that brake gear comprises:
Place one first drg between case of transmission and a connector, this adaptor union is connected with each other the gear ring of the first simple planetary group and the pinion carrier of the second simple planetary group; With
Place one second drg between the sun gear of the case of transmission and the second simple planetary group.
4. transmission system as claimed in claim 1 is characterized in that clutch equipment is a multidisc clutch, and this multidisc clutch places between the sun gear of a connector and the second simple planetary group, and described adaptor union connects first and second free-wheel clutchs.
5. transmission system as claimed in claim 2 is characterized in that first clutch, second clutch and three-clutch are multidisc clutchs.
6. transmission system as claimed in claim 3 is characterized in that first drg and second drg are polydisc clamping shape power-transfer clutchs.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1019990049402A KR100357545B1 (en) | 1999-11-09 | 1999-11-09 | Power train for auto transmission |
| KR49402/1999 | 1999-11-09 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1294992A true CN1294992A (en) | 2001-05-16 |
Family
ID=19619169
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN00121619A Pending CN1294992A (en) | 1999-11-09 | 2000-07-21 | Automatic variable-speed drive system |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JP2001140998A (en) |
| KR (1) | KR100357545B1 (en) |
| CN (1) | CN1294992A (en) |
| AU (1) | AU4380300A (en) |
| DE (1) | DE10033474A1 (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101566217A (en) * | 2009-06-03 | 2009-10-28 | 奇瑞汽车股份有限公司 | 6-speed automatic transmission and transmission system thereof |
| CN101649889A (en) * | 2009-06-23 | 2010-02-17 | 奇瑞汽车股份有限公司 | Six-gear gearbox for vehicle and transmission system thereof |
| CN101042174B (en) * | 2006-03-22 | 2011-09-07 | 现代自动车株式会社 | Automatic transmission's power train |
| CN101663505B (en) * | 2007-05-15 | 2012-11-28 | Zf腓德烈斯哈芬股份公司 | Multi-step transmission |
| CN102954158A (en) * | 2011-08-25 | 2013-03-06 | 现代自动车株式会社 | Gear train in multistage transmission for vehicles |
| CN103818238A (en) * | 2012-11-15 | 2014-05-28 | 舍弗勒技术股份两合公司 | Transmission-motor-assembly |
| CN102954158B (en) * | 2011-08-25 | 2016-12-14 | 现代自动车株式会社 | Gear train in the multiple-speed gear-box of vehicle |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100828687B1 (en) * | 2006-11-08 | 2008-05-09 | 현대자동차주식회사 | Eight speed powertrain of automatic transmission for vehicle |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3362728B2 (en) * | 1988-09-27 | 2003-01-07 | トヨタ自動車株式会社 | Transmission friction engagement device for transmission |
| KR100293656B1 (en) * | 1997-08-30 | 2001-08-07 | 이계안 | Power train for automatic transmission |
| KR100293664B1 (en) * | 1997-10-10 | 2001-10-24 | 이계안 | Automatic transmission of full shifting stage non-synchronous shifting two-simple type |
| JP3080057B2 (en) * | 1997-12-01 | 2000-08-21 | トヨタ自動車株式会社 | Automatic transmission |
-
1999
- 1999-11-09 KR KR1019990049402A patent/KR100357545B1/en not_active IP Right Cessation
-
2000
- 2000-06-26 JP JP2000191674A patent/JP2001140998A/en active Pending
- 2000-06-30 AU AU43803/00A patent/AU4380300A/en not_active Abandoned
- 2000-07-10 DE DE10033474A patent/DE10033474A1/en not_active Withdrawn
- 2000-07-21 CN CN00121619A patent/CN1294992A/en active Pending
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101042174B (en) * | 2006-03-22 | 2011-09-07 | 现代自动车株式会社 | Automatic transmission's power train |
| CN101663505B (en) * | 2007-05-15 | 2012-11-28 | Zf腓德烈斯哈芬股份公司 | Multi-step transmission |
| CN101566217A (en) * | 2009-06-03 | 2009-10-28 | 奇瑞汽车股份有限公司 | 6-speed automatic transmission and transmission system thereof |
| CN101649889A (en) * | 2009-06-23 | 2010-02-17 | 奇瑞汽车股份有限公司 | Six-gear gearbox for vehicle and transmission system thereof |
| CN102954158A (en) * | 2011-08-25 | 2013-03-06 | 现代自动车株式会社 | Gear train in multistage transmission for vehicles |
| CN102954158B (en) * | 2011-08-25 | 2016-12-14 | 现代自动车株式会社 | Gear train in the multiple-speed gear-box of vehicle |
| CN103818238A (en) * | 2012-11-15 | 2014-05-28 | 舍弗勒技术股份两合公司 | Transmission-motor-assembly |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2001140998A (en) | 2001-05-22 |
| KR100357545B1 (en) | 2002-10-19 |
| DE10033474A1 (en) | 2001-05-10 |
| AU4380300A (en) | 2001-05-10 |
| KR20010045890A (en) | 2001-06-05 |
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