CN104110471B - Automatic transmission - Google Patents
Automatic transmission Download PDFInfo
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- CN104110471B CN104110471B CN201410290449.6A CN201410290449A CN104110471B CN 104110471 B CN104110471 B CN 104110471B CN 201410290449 A CN201410290449 A CN 201410290449A CN 104110471 B CN104110471 B CN 104110471B
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- Prior art keywords
- axle
- gear
- tooth wheels
- commutating tooth
- automatic transmission
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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
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
- B60W10/06—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of combustion engines
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W20/00—Control systems specially adapted for hybrid vehicles
- B60W20/40—Controlling the engagement or disengagement of prime movers, e.g. for transition between prime movers
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
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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
- F16H2200/0073—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eleven 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
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
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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
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/40—Engine management systems
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Automation & Control Theory (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention discloses a kind of automatic transmission, comprise the first axle system being positioned at back flow side be arranged side by side in same mission case and the second axle system and three commutating tooth wheels, three planetary gear set, five clutches and the breaks that are positioned at slave end, these two axle systems are connected by the multiple power paths belonging to three commutating tooth wheels.Only just achieve at least ten forward gears with six gear shift units to reverse gear with at least one; and than between 1.090 ~ 1.217 between the gear of conventional gear; resultant gear ratio scope reaches 9.5; smooth gear shifting; structure keeps compact; the traveling dynamic performance improving vehicle also reduce further oil consumption, uses economy, and is conducive to protection of the environment.This automatic transmission is applicable to mixed power and drives and the function with applicable motor automatic start-stop.
Description
Technical field
The present invention relates to a kind of automatic transmission, particularly relate to a kind of being adapted in the power transmission system of passenger car as the automatic transmission that main transmission uses.
Background technique
In passenger car field, automatic transmission (AT) remains the speed changer structure of main flow.The most employing of automatic transmission (AT) in the early time multi-stage planetary gear group structure is not gear is exactly that structure is too complicated less.Afterwards, the automatic transmission structure that two axle systems, commutating tooth wheels and planetary gear set combinationally used starts to occur.Chinese invention patent CN101275630B, just describe a kind of like this can the multiple-speed gear-box of power gear shifting.
According to this patent, this speed changer comprises two the axle systems be disposed side by side in a shared mission case, three commutating tooth wheels, three planetary gear set and multiple gear shift unit, wherein, first axle system comprises the first axle and the 3rd axle, 4th axle and the 5th axle, second axle system comprises the second axle and the 6th axle, 7th axle and the 8th axle, wherein the 3rd axle is connected by first commutating tooth wheels with the 6th axle, 4th axle is connected by second commutating tooth wheels with the 7th axle, 5th axle is connected by the 3rd commutating tooth wheels with the 8th axle, first planet gear train is arranged on the first axle and fastens, comprise first sun gear, first gear ring and first planet carrier, second planetary gear set is arranged on the second axle and fastens, comprise second sun gear, second gear ring and second planet carrier, third planet gear train is arranged on the second axle and fastens, comprise the 3rd sun gear, 3rd gear ring and the 3rd planet carrier.Five shifting elements are provided with in this speed changer, i.e. four clutches and a break, can make thus to be interconnected between each gearbox unit or to be connected with mission case, the clear and definite motion state and power path with specific velocity ratio and moment of torsion transmission can be limited at each gear, achieving to reverse gear at least eight forward gears and at least one with the least possible speed change level and shifting element carries out powershift, length is short, compact structure and achieve high efficiency, it is the successful when preposition laterally application not only, outstanding too when longitudinally applying, be particularly useful for how shaft-driven vehicle.Therefore, the contribution of Chinese invention patent CN101275630B to automatic transmission (AT) is mathematical.
But now, vehicle is in order to reduce oil consumption further and improve the gear travelling dynamic performance and need more and less transmission to distribute.Reduce the object of oil consumption not only from the economic needs of user self, and be the important means realizing emission reduction targets, along with the enforcement of more and more stricter passenger car emission standard, higher requirement will be proposed to the performance of speed changer.
Summary of the invention
The present invention is just in order to comply with the demand and requirement proposes.Technical problem to be solved by this invention is: provide a kind of automatic transmission, powershift is carried out to reverse gear to forward gear as much as possible and at least one with the least possible speed change level and shifting element, not only axial length is short for this speed changer, compact structure, efficiency are high, and by providing more and the more gear that distributes of close steps, reduce further oil consumption and improving the traveling dynamic performance of vehicle.
For solving the problems of the technologies described above, technological scheme of the present invention is: a kind of automatic transmission, comprising: be disposed side by side on two axle systems in a shared mission case, three commutating tooth wheels, three planetary gear set and several gear shift units; Described first axle system is positioned at back flow side, comprises the first axle, the 3rd axle, the 4th axle, the 5th axle and the 6th axle, and power is from described first axle input; Described second axle system is positioned at slave end, comprises the second axle, the 7th axle, the 8th axle, the 9th axle and the tenth axle, and power exports from described second axle; Described 6th axle is connected by the first commutating tooth wheels with described tenth axle, and the first commutating tooth wheels comprise the first driving gear and the first driven gear, and described first driving gear is fixed on described 6th axle, and described first driven gear is fixed on described tenth axle; Described 4th axle is connected by the second commutating tooth wheels with described 7th axle, and the second commutating tooth wheels comprise the second driving gear and the second driven gear, and described second driving gear is fixed on described 4th axle, and described second driven gear is fixed on described 7th axle; Described 5th axle is connected by the 3rd commutating tooth wheels with described 8th axle, described 3rd commutating tooth wheels comprise the 3rd driving gear and the 3rd driven gear, described 3rd driving gear is fixed on described 5th axle, and described 3rd driven gear is fixed on described 8th axle; Described first planet gear train is arranged on the first axle and fastens, and comprises the first sun gear, the first gear ring and the first row carrier, and described first sun gear is fixed on described 3rd axle; Described second planetary gear set is arranged on the second axle and fastens, and comprises secondary sun wheel, the second gear ring and the second planet carrier, and described second gear ring is fixed on described 9th axle; Described third planet gear train is arranged on the second axle and fastens, and comprises the 3rd sun gear, the 3rd gear ring and the third line carrier; Described first axle is connected with the first gear ring of first planet gear train; Described second axle is fixedly connected with described the third line carrier; Described 4th axle is connected with the first row carrier of first planet gear train; Described 7th axle is fixedly connected with described secondary sun wheel, and described 8th axle is fixedly connected with described 3rd sun gear; Described second axle is fixedly connected with described second planet carrier; Described tenth axle is fixedly connected with described 3rd gear ring; Described gear shift unit comprises: be connected to the first break between described first sun gear and described mission case; Be connected to first clutch between described 5th axle and described the first row carrier; Be connected to the second clutch between described 8th axle and described second gear ring; Be connected to the 3rd clutch between described 4th axle and described 5th axle; Be connected to the four clutches between described 6th axle and described first sun gear; Rigidly connected 5th clutch set up by two elements controlled in described 3rd sun gear, described 3rd gear ring and described the third line carrier.
Preferably, described 5th clutch is connected between described 8th axle and described second axle.
Preferably, described 5th clutch is connected between described tenth axle and described second axle.
Preferably, the arbitrary axle in described axle system is connected with a motor.
Preferably, described 5th axle or the 8th axle are connected with a motor.
Preferably, comprise: hydraulic system, described hydraulic system comprises hydraulic power unit, hydraulic power controls and performance element and signaling control unit, described hydraulic power unit comprises an electric pump and a mechanical pump driven by the engine, the suction passage of described electric pump is in parallel with the suction passage of described mechanical pump, the oil discharge passage of described electric pump is in parallel with the oil discharge passage of described mechanical pump, the suction passage of described electric pump and the suction passage of described mechanical pump are respectively equipped with an one-way valve, described signaling control unit comprises the controller of the motor start and stop of a control electric pump.
Compared with prior art, have the following advantages effect in the present invention:
1) rigidly connected 5th clutch is set up owing to having set up two elements controlled in described 3rd sun gear, described 3rd gear ring and described the third line carrier, thus for providing more gearshift logic to provide possibility.When the 5th clutch closes, third planet gear train will become a rigid connection body, and when input power, third planet gear train is by integrated rotary.Only by setting up the 5th clutch at special position, just can realize 11 forward gears and reverse gear with at least one, reduce idle row loss by logical validity of simply shifting gears, improve the transmission efficiency of speed changer.And than all between 1.090 ~ 1.217 between gear between conventional gear, very little, powershift is more smooth-going, is not only conducive to improving the traveling dynamic performance of vehicle but also oil consumption can be reduced further, using more economical, be also more conducive to protection of the environment.Meanwhile, simple change also can make the overall structure of speed changer still keep compact.
2) resultant gear ratio scope can reach 9.5, and known speed changer, its resultant gear ratio scope is generally about 7, and this just means, adopts the speed of a motor vehicle that structure disclosed in this invention can reach higher.
3) any one axle in axle system can connect with motor, and can provide multiple preferred axle that speed changer is connected with motor, thus obtains mixed power system.Because these preferred axles have higher velocity ratio to input shaft when low-grade location, therefore a little motor just can have enough moment for quick ato unit.Meanwhile, these axles have higher velocity ratio to output shaft equally, make the motor be connected on them can help efficiently to drive work normally.
4) the present invention has the function of applicable motor automatic start-stop.Set up an electric pump in hydraulic system, the suction passage of electric pump is in parallel with the suction passage of mechanical pump, and the oil discharge passage of electric pump is in parallel with the oil discharge passage of mechanical pump, and such structure does not need to do large change to original hydraulic system, and can reduce mechanical pump.When to stall, mechanical air pump inoperative time, under the triggering of a controller, electric pump energising runs, thus makes hydraulic oil enter the hydraulic power unit of hydraulic system, ensure motor when ato unit, automatic transmission can normally work.Motor start stop system makes motor auto extinguishing when can make vehicle temporary parking in the process of moving (such as waiting red light) and step on brake petal, when needs move on time, as long as releasing of brake dubs throttle, or steering wheel rotation, motor again can horse back automatic ignition autoboot.Motor start stop system significantly can reduce the fuel consume of vehicle, is particularly suitable for the urban road blocked up.
Accompanying drawing explanation
Below in conjunction with drawings and Examples, the present invention is further described.
Fig. 1 is the structural representation of automatic transmission first embodiment of the present invention;
Fig. 2 is the structural representation of automatic transmission second embodiment of the present invention;
Fig. 3 is gearshift logic embodiment illustrated in fig. 1, the exemplary ratio of speed change level and gear range;
Fig. 4 is the schematic diagram of hydraulic system in the second embodiment shown in Fig. 2;
In figure:
0-mission case; 1-first axle; 2-second axle; 3-the 3rd axle; 4-the 4th axle; 5-the 5th axle; 6-the 6th axle; 7-the 7th axle; 8-the 8th axle; 9-the 9th axle; 10-the tenth axle;
TG610-first commutating tooth wheels; TG47-second commutating tooth wheels; TG58-the 3rd commutating tooth wheels;
G6-first driving gear; G10-first driven gear;
G4-second driving gear; G7-second driven gear;
G5-the 3rd driving gear; G8-the 3rd driven gear;
PG1-first planet gear train; PG2-second planetary gear set; PG3-third planet gear train;
Ho1-first gear ring; Pt1-the first row carrier; So1-first sun gear;
Ho2-second gear ring; Pt2-second planet carrier; So2-secondary sun wheel;
Ho3-the 3rd gear ring; Pt3-the third line carrier; So3-the 3rd sun gear;
B1-first break; C1-first clutch; C2-second clutch; C3-the 3rd clutch; C4-four clutches; C5-the 5th clutch;
In-input shaft; Out-output shaft; FD-differential mechanism; EM-motor;
P-mechanical pump; EP-electric pump.
Embodiment
Embodiment is used for further illustrating technical conceive of the present invention, and does not limit the scope of the invention.
First embodiment:
As shown in Figure 1, a kind of automatic transmission, can realize 11 forward gears and at least one reverses gear.The input shaft in of speed changer is connected for input power by starting unit with the first axle 1, and the output shaft out of speed changer is connected for outputting power with the second axle 2 by differential mechanism FD.Described starting unit can be start clutch also can be fluid torque converter etc.
This speed changer comprises and is disposed side by side on two axle systems in a shared mission case 0, three commutating tooth wheels, three planetary gear set and six gear shift units.In the art, axle and the parts be arranged on these axles with same axis form an axle system.
First axle system is positioned at back flow side, comprises described first axle 1 and the 3rd axle 3, the 4th axle 4, the 5th axle 5 and the 6th axle 6, second axle system are positioned at slave end, comprises the second described axle 2 and the 7th axle 7, the 8th axle 8 the 9th axle 9 and the tenth axle 10.
6th axle 6 is connected by the first commutating tooth wheels TG610 with the tenth axle 10, and the first commutating tooth wheels TG610 comprises the first driving gear G6 and the first driven gear G10, and the first driving gear G6 is fixed on the 6th axle 6, and the first driven gear G10 is fixed on the tenth axle 10.
4th axle 4 is connected by the second commutating tooth wheels TG47 with the 7th axle 7, and the second commutating tooth wheels TG47 comprises the second driving gear G4 and the second driven gear G7, and the second driving gear G4 is fixed on the 4th axle 4, and the second driven gear G7 is fixed on the 7th axle 7.
5th axle 5 is connected by the 3rd commutating tooth wheels TG58 with the 8th axle 8, and the 3rd commutating tooth wheels TG58 comprises the 3rd driving gear G5 and the 3rd driven gear G8, and the 3rd driving gear G5 is fixed on the 5th axle 5, and the 3rd driven gear G8 is fixed on the 8th axle 8.
First planet gear train PG1 is arranged on the first axle and fastens, and comprise the first sun gear So1, the first gear ring Ho1 and the first row carrier Pt1, the first sun gear So1 is fixed on the 3rd axle 3.Second planetary gear set PG2 is arranged on the second axle and fastens, and comprises secondary sun wheel So2, the second gear ring Ho2 and the second planet carrier Pt2, and the second gear ring Ho2 is fixed on described 9th axle 9.Third planet gear train PG3 is arranged on the second axle and fastens, and comprises the 3rd sun gear So3, the 3rd gear ring Ho3 and the third line carrier Pt3.
Each mechanism unit of this speed changer has following being fixedly connected with:
First axle 1 is connected with the first gear ring Ho1 of first planet gear train PG1;
Second axle 2 is connected with the third line carrier Pt3 of third planet gear train PG3;
4th axle 4 is connected with the first row carrier Pt1 of first planet gear train PG1;
8th axle 8 is connected with the 3rd sun gear So3 of third planet gear train PG3;
Second axle 2 is connected with the second planet carrier Pt2 of the second planetary gear set PG2;
7th axle 7 is connected with the secondary sun wheel So2 of the second planetary gear set PG2;
Tenth axle 10 is connected with the 3rd gear ring Ho3 of third planet gear train PG3.
Described six gear shift units comprise a break and five clutches, for realizing powershift, respectively:
For connecting the first break B1 of the first sun gear So1 and mission case 0;
For connecting the first clutch C1 of the 5th axle 5 and the first gear ring Ho1;
For connecting the second clutch C2 of the 8th axle 8 and the second gear ring Ho2;
For connecting the 3rd clutch C3 of the 4th axle 4 and the 5th axle 5;
For connecting the four clutches C4 of the 6th axle 6 and the first sun gear So1;
For connecting the 5th clutch C5 of the second axle 2 and the 8th axle 8.
As shown in Figure 3, gearshift logic shows and how to use the combination of these gear shift units to realize one to reverse gear and the powershift of 11 forward gears, and each gear is determined is actually a power path.In gearshift logic diagram, blank expression opens, and oblique line represents closed.Each gear switch can by realization of simply shifting gears to contiguous gear or gearshift of bypassing the immediate leadership, and that is, gearshift only just can need complete by decontroling a gear shift unit and closing another gear shift unit.Only have under special circumstances, gearshift adopts the mode of relieving two shifting elements and two other shifting element closed to carry out, simple gearshift certainly than other gearshift mode sooner, more comfortable.
For each traveling gear, three must be had in six gear shift units to close, and this is relevant with the degrees of freedom of speed changer.The present embodiment one has four degrees of freedom, obtain the kinematic relation determined, also namely between all axles, have the velocity ratio determined, need to eliminate three degree of freedom, by using gear shift unit to link together between axle and axle or between axle and mission case, degrees of freedom can be eliminated.Here it is, and each gear must have the reason that three gear shift units are closed.One reverses gear and 11 forward gears are optimal ways of the present embodiment logical combination, according to the mathematical principle of combination, can also produce more logical combination, according to prior art, those of ordinary skill in the art can know that in these combinations, which is useful.
Also show the velocity ratio of each speed change level of the first embodiment in Fig. 3, with regard to numerical value, the velocity ratio of these six speed change levels is exemplary, and the velocity ratio by these six speed change levels can also obtain other and more realize possibility.Such as the velocity ratio x of increase or reduction commutating tooth wheels doubly, just can obtain or increase the resultant gear ratio of same multiple.
By the velocity ratio of above-mentioned power path and speed change level can calculate between the velocity ratio of each gear, gear than and resultant gear ratio scope, these have all shown in figure 3.As can be seen from Figure 3, than all between 1.090 ~ 1.217 between the gear between conventional gear, very little, when shifting gears, more close steps distributes and means that powershift is more smooth-going, and the smoothness of powershift to be automatic transmission do one's utmost praises highly the low oil consumption of a step-down because this traveling dynamic performance can improving vehicle is gone forward side by side.Resultant gear ratio scope reaches 9.5, and known speed changer, its resultant gear ratio scope is generally about 7, and this just means, adopts structure disclosed in this invention can reach the speed of a motor vehicle faster.
According to the mathematical principle of combination, by increasing the quantity of clutch, provide logic of more shifting gears, thus provide more gear to export, this is known by those of ordinary skill in the art.But, it should be noted that, 1) in numerous gearbox units, annexation is set up wherein to form new power path? (the present invention at least comprises three commutating tooth wheels and three planetary gear set, each commutating tooth wheels are divided into two rotary members separately, every planetary gear set is divided into again three rotary members separately) 2) further, how to ensure the useful velocity ratio of sufficient amount, and make between gear less than enough? 3) further, how while increase exports gear, make the overall structure of speed changer still compact? these problems, those of ordinary skill in the art is difficult to be obtained by the test of limited number of time and conventional reasoning.In this sense, above-mentioned data, exactly embody the contribution that the present invention makes prior art.
By gearshift logic and the velocity ratio of each speed change level, those skilled in the art can also calculate poower flow under the torque load of all gearbox units and all gears on all axles according to prior art.Analyzing the conclusion drawn is, for the total output transmission from the first axle to the second axle, under all gears, can not be back to the first axle system by any one in three commutating tooth wheels from the second axle system.Under conventional gear, power by two or three commutating tooth wheels transmit, total load is low, thus speed changer can design compact.
Second embodiment:
Shown in Fig. 2 is another kind of application form of the present invention, is referred to as hybrid power transmission scheme.Motor EM is connected with the 5th axle 5 by additional commutating tooth wheels, and in this case, motor EM is arranged to parallel with two axle systems.
First axle 1 is along the Axis Extension of whole first axle system, and its two end supports is on mission case 0.In this case, the two ends of the first axle 1 can be connected with motor or motor EM.This technological scheme makes speed changer of the present invention can have a large amount of different application design proposals.Such structure is equally applicable to the first embodiment and the second embodiment.
Second axle 2 extends along the axis of whole second axle system, and its two end supports is on mission case 0.In this case, the second axle 2 liang of end flange can be connected with motor EM.This technological scheme also makes speed changer of the present invention can have a large amount of different application design proposals.Such structure is equally applicable to the first embodiment and the second embodiment.
Any one axle in axle system can be connected with motor.Wherein, the 5th axle 5 or the 8th axle 8 are particularly suitable for being connected with motor EM, because these axles have higher velocity ratio when low gear to input shaft in.Like this, a little motor just can have enough moment for quick ato unit.Meanwhile, these axles also have higher velocity ratio to output shaft out equally, make the motor be connected on them can help efficiently to drive work normally.When the pure motorized motions of vehicle, the connection of automatic transmission and motor can be disconnected by starting unit.Like this, just can kill engine, also not need to drag motor.
Shown in Fig. 4 is the hydraulic system principle figure of second embodiment's automatic transmission, (certainly, the program is also suitable for the first embodiment), this cover system aims at and adapts to motor start stop system and arrange, this hydraulic system comprises hydraulic power unit, hydraulic power controls and performance element and signaling control unit, and what mainly illustrate in figure is the hydraulic power unit of hydraulic system.Hydraulic power unit comprises a mechanical pump P driven by the engine, and hydraulic oil is pumped into hydraulic power from hydraulic oil container through filter cleaner and controls and performance element by it, the control oil cylinder of such as clutch, thus the opening and closing of solenoidoperated cluthes.Simultaneously, set up an electric pump EP, the suction passage of electric pump EP is in parallel with the suction passage of mechanical pump P, the oil discharge passage of electric pump EP is in parallel with the oil discharge passage of mechanical pump P, so, when to stall, mechanical pump P do not work time, under the triggering of a controller of signaling control unit, electric pump EP is energized operation, thus makes hydraulic oil enter the hydraulic power unit of hydraulic system, ensures that motor EM automatic transmission when ato unit can normally work.The oil discharge passage of mechanical pump P and electric pump EP arranges an one-way valve respectively, to prevent mechanical pump P and electric pump EP operationally hydraulic oil backflow.
Vehicle temporary parking in the process of moving (such as wait for red light) and step on brake petal time, the speed of a motor vehicle reduces to 0 and after continuing for some time, motor auto extinguishing under the control of ECU (control unit of engine); In the process that engine speed declines, engine speed is lower than after certain value, and controller starts electric pump EP with constant speed continuous running.When needs move on, as long as releasing of brake dubs throttle, or steering wheel rotation, motor can be restarted by automatic ignition again at once; After engine start, when engine speed is higher than a threshold value, controller controls electric pump EP and quits work.Motor start stop system significantly can reduce the fuel consume of vehicle, is particularly suitable for the urban road blocked up.
Second embodiment and the first embodiment also have not with being, the 5th clutch C5 is connected between the second axle 2 and the tenth axle.
As can be seen from above-mentioned two embodiments, although the setting position of the 5th clutch C5 is different, but, but its object is all set up for two elements controlled in the 3rd sun gear So3, the 3rd gear ring Ho3 and the third line carrier Pt3 to be rigidly connected, thus for providing more gearshift logic to provide possibility.When the 5th clutch closes, third planet gear train will become a rigid connection body, and during to its input power, entirety is turned round by third planet gear train.That is, in these two embodiments, under identical gearshift logical situations, speed changer is by ratio and resultant gear ratio scope between the identical velocity ratio of acquisition and gear.
The present invention is not limited to structure, principle and the method that above-described embodiment is mentioned, and the equivalent transformation that all those of ordinary skill in the art just can carry out without performing creative labour all will fall within protection scope of the present invention.
Claims (8)
1. an automatic transmission, comprising:
Be disposed side by side on two axle systems in a shared mission case (0), three commutating tooth wheels, three planetary gear set and several gear shift units, described two axle systems comprise the first axle system and the second axle system, described three commutating tooth wheels comprise the first commutating tooth wheels, the second commutating tooth wheels and the 3rd commutating tooth wheels, and described three planetary gear set comprise first planet gear train, the second planetary gear set and third planet gear train;
Described first axle system is positioned at back flow side, comprise the first axle (1), the 3rd axle (3), the 4th axle (4), the 5th axle (5) and the 6th axle (6), power inputs from described first axle (1);
Described second axle system is positioned at slave end, comprise the second axle (2), the 7th axle (7), the 8th axle (8), the 9th axle (9) and the tenth axle (10), power exports from described second axle (2);
Described 6th axle (6) is connected by the first commutating tooth wheels (TG610) with described tenth axle (10), described first commutating tooth wheels (TG610) comprise the first driving gear (G6) and the first driven gear (G10), described first driving gear (G6) is fixed on described 6th axle (6), and described first driven gear (G10) is fixed on described tenth axle (10);
Described 4th axle (4) is connected by the second commutating tooth wheels (TG47) with described 7th axle (7), described second commutating tooth wheels (TG47) comprise the second driving gear (G4) and the second driven gear (G7), described second driving gear (G4) is fixed on described 4th axle (4), and described second driven gear (G7) is fixed on described 7th axle (7);
Described 5th axle (5) is connected by the 3rd commutating tooth wheels (TG58) with described 8th axle (8), described 3rd commutating tooth wheels (TG58) comprise the 3rd driving gear (G5) and the 3rd driven gear (G8), described 3rd driving gear (G5) is fixed on described 5th axle (5), and described 3rd driven gear (G8) is fixed on described 8th axle (8);
Described first planet gear train (PG1) is arranged on the first axle and fastens, comprise the first sun gear (So1), the first gear ring (Ho1) and the first row carrier (Pt1), described first sun gear (So1) is fixed on described 3rd axle (3);
Described second planetary gear set (PG2) is arranged on the second axle and fastens, comprise secondary sun wheel (So2), the second gear ring (Ho2) and the second planet carrier (Pt2), described second gear ring (Ho2) is fixed on described 9th axle (9);
Described third planet gear train (PG3) is arranged on the second axle and fastens, and comprises the 3rd sun gear (So3), the 3rd gear ring (Ho3) and the third line carrier (Pt3);
Described second axle (2) is fixedly connected with described second planet carrier (Pt2);
Described second axle (2) is fixedly connected with described the third line carrier (Pt3);
Described 7th axle (7) is fixedly connected with described secondary sun wheel (So2);
Described 8th axle (8) is fixedly connected with described 3rd sun gear (So3);
Described tenth axle (10) is fixedly connected with described 3rd gear ring (Ho3);
Described gear shift unit comprises:
Be connected to the first break (B1) between described first sun gear (So1) and described mission case (0);
Be connected to the first clutch (C1) between described 5th axle (5) and described first gear ring (Ho1);
Be connected to the second clutch (C2) between described 8th axle (8) and described second gear ring (Ho2);
Be connected to the 3rd clutch (C3) between described 4th axle (4) and described 5th axle (5);
Be connected to the four clutches (C4) between described 6th axle (6) and described first sun gear (So1);
It is characterized in that, this speed changer also comprises
Described first axle (1) is connected with first gear ring (Ho1) of described first planet gear train (PG1);
Described 4th axle (4) is connected with the first row carrier (Pt1) of described first planet gear train (PG1);
Rigidly connected 5th clutch (C5) set up by two elements controlled in described 3rd sun gear (So3), described 3rd gear ring (Ho3) and described the third line carrier (Pt3).
2. automatic transmission as claimed in claim 1, it is characterized in that, described 5th clutch (C5) is connected between described 8th axle (8) and described second axle (2).
3. automatic transmission as claimed in claim 1, it is characterized in that, described 5th clutch (C5) is connected between described tenth axle (10) and described second axle (2).
4. the automatic transmission as described in any one of claims 1 to 3, is characterized in that, described first axle system is connected with a motor (EM) with the arbitrary axle in described second axle system.
5. the automatic transmission as described in any one of claims 1 to 3, is characterized in that, described 5th axle (5) or the 8th axle (8) are connected with a motor (EM).
6. automatic transmission as claimed in claim 4, it is characterized in that, described first axle (1) is along the Axis Extension of whole described first axle system, and its two end supports is on described mission case (0).
7. automatic transmission as claimed in claim 4, it is characterized in that, described second axle (2) is along the Axis Extension of whole described second axle system, and its two end supports is on described mission case (0).
8. automatic transmission as claimed in claim 4, it is characterized in that, comprise: hydraulic system, described hydraulic system comprises hydraulic power unit, hydraulic power controls and performance element and signaling control unit, described hydraulic power unit comprises an electric pump (EP) and a mechanical pump driven by the engine (P), the suction passage of described electric pump (EP) is in parallel with the suction passage of described mechanical pump (P), the oil discharge passage of described electric pump (EP) is in parallel with the oil discharge passage of described mechanical pump (P), the suction passage of described electric pump (EP) and the suction passage of described mechanical pump (P) are respectively equipped with an one-way valve, described signaling control unit comprises the controller of the motor start and stop in the described electric pump of a control (EP).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410290449.6A CN104110471B (en) | 2014-06-25 | 2014-06-25 | Automatic transmission |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410290449.6A CN104110471B (en) | 2014-06-25 | 2014-06-25 | Automatic transmission |
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| CN104110471A CN104110471A (en) | 2014-10-22 |
| CN104110471B true CN104110471B (en) | 2016-04-27 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201410290449.6A Active CN104110471B (en) | 2014-06-25 | 2014-06-25 | Automatic transmission |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104896042A (en) * | 2015-05-30 | 2015-09-09 | 盛瑞传动股份有限公司 | Automatic transmission of hybrid power car |
| CN108799442A (en) * | 2018-08-21 | 2018-11-13 | 盛瑞传动股份有限公司 | Multiple-speed gear-box |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101550998A (en) * | 2008-03-31 | 2009-10-07 | 通用汽车环球科技运作公司 | Automatic transmission gear and clutch arrangement |
| CN101903684A (en) * | 2007-11-01 | 2010-12-01 | Nt咨询国际有限公司 | Speed changer |
| CN103375551A (en) * | 2012-04-27 | 2013-10-30 | 腓特烈斯港齿轮工厂股份公司 | Planetary gear type multi-stage transmission |
| CN103527733A (en) * | 2012-06-14 | 2014-01-22 | 通用汽车环球科技运作有限责任公司 | Automatic transmission gear and clutch arrangement |
| CN103821886A (en) * | 2014-03-18 | 2014-05-28 | 衢州市易凡设计有限公司 | Automatic speed change gear |
| CN203948583U (en) * | 2014-06-25 | 2014-11-19 | 盛瑞传动股份有限公司 | Automatic transmission |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002347455A (en) * | 2001-05-23 | 2002-12-04 | Fuji Heavy Ind Ltd | Automatic transmission |
| JP2013204815A (en) * | 2012-03-29 | 2013-10-07 | Honda Motor Co Ltd | Power transmission device for hybrid vehicle |
-
2014
- 2014-06-25 CN CN201410290449.6A patent/CN104110471B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101903684A (en) * | 2007-11-01 | 2010-12-01 | Nt咨询国际有限公司 | Speed changer |
| CN101550998A (en) * | 2008-03-31 | 2009-10-07 | 通用汽车环球科技运作公司 | Automatic transmission gear and clutch arrangement |
| CN103375551A (en) * | 2012-04-27 | 2013-10-30 | 腓特烈斯港齿轮工厂股份公司 | Planetary gear type multi-stage transmission |
| CN103527733A (en) * | 2012-06-14 | 2014-01-22 | 通用汽车环球科技运作有限责任公司 | Automatic transmission gear and clutch arrangement |
| CN103821886A (en) * | 2014-03-18 | 2014-05-28 | 衢州市易凡设计有限公司 | Automatic speed change gear |
| CN203948583U (en) * | 2014-06-25 | 2014-11-19 | 盛瑞传动股份有限公司 | Automatic transmission |
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Inventor after: Tenberge Peter Inventor after: Su Chengyun Inventor after: Lu Xi Inventor after: Li Sanshuai Inventor after: Song Tingbin Inventor after: Liu Xiangwu Inventor before: Su Chengyun Inventor before: Lu Xi Inventor before: Li Sanshuai Inventor before: Song Tingbin Inventor before: Liu Xiangwu |
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Free format text: CORRECT: INVENTOR; FROM: SU CHENGYUN LU XI LI SANSHUAI SONG TINGBIN LIU XIANGWU TO: PETER TENBERGE SU CHENGYUN LU XI LI SANSHUAI SONG TINGBIN LIU XIANGWU |
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