CN104832619A

CN104832619A - Adaptive continuously variable transmission for hydraulic planetary gear

Info

Publication number: CN104832619A
Application number: CN201510227536.1A
Authority: CN
Inventors: 周庆华
Original assignee: Individual
Current assignee: Individual
Priority date: 2014-12-10
Filing date: 2015-05-04
Publication date: 2015-08-12
Also published as: CN104595453A

Abstract

The invention belongs to the field of continuously variable transmissions. An adaptive continuously variable transmission for a hydraulic planetary gear has the greatest technical advantages that an auto-adaptive continuously variable transmission which is high in efficiency, high in power, low in cost, long in service life and simple in structure is achieved, and the efficiency of an engine is improved by over 30 percent. The adaptive continuously variable transmission for the hydraulic planetary gear has the greatest innovation points that an improved hydraulic torque converter and a planetary gear set adopt a parallel principle without the adoption of a conventional AT series structure, a turbine of the hydraulic torque converter is required to be connected with a fixed piece outside driving and driven elements of the planetary gear set, and a pump wheel is required to be connected with the driven element; the planetary gear set has five basic forms namely a single-row planetary gear structure, a double-row planetary gear structure, an external meshed planetary gear structure and a differential planetary gear structure; the improved hydraulic torque converter is combined with the five basic structural forms of the planetary gear set respectively to form eight specific structural types of the continuously variable transmission.

Description

Hydraulic planetary gear self adaption infinitely variable transmission

Technical field

The invention belongs to gear technical field, be practically applicable to all motor vehicle and need the equipment of speed change.

Background technique

The performance accounting for the various brands gearbox of dominant position in the prior art has his own strong points, and whom who can not eliminate.MT manual transmission with its machinery driving efficiency high and have Driving and like by a lot of people, conventional automatic gearbox AT, with its technology maturation reliable performance, simple to operate and capture very large market, CVT steel band cone disk type infinitely variable transmission, with the transmission efficiency that it is higher, stepless change performance can be in office can find the optimal match point with motor under speed ratio, so its market share rises year by year; The two clutch gearbox of DSG, and fast switching speed, and high transmission efficiency has greatly the gesture of capturing dominant position; AMT mechanical automatic speed-changing case is also developing in recent years to some extent, has two large R&D directions in infinitely variable transmission field; One is various forms of friction driving, another is so-called gear transmission, they have a common ground: structural limitations defect, friction driving cannot realize high-power, pure gear cannot realize stepless change, and reducing oscillating tooth or its structural reliability durability of imperfect gear scheme are insurmountable difficult problems forever.

The object of invention

Gearbox is one of core component of automobile, and its quality is directly connected to power performance and the fuel economy of vehicle, is also one of transnational automotive giants technology commanding height fighting for Global Auto market.But China is in high-end gearbox field very backwardness, 80% relies on import, 20% remaining Ye Shi joint venture produces, substantially be under one's control, although there are more advanced technology and ripe product in external manufacturer, but they have respective unsurmountable shortcoming: AT automatic transmission case is because fluid torque converter is direct and planetary gear set series winding, it is direct power transmitting elements, and its efficient district scope is narrow, so its efficiency is on the low side, and just need to increase gear to raise the efficiency, and so directly cause complex structure cost to increase reliability decrease, the two clutch gearbox of DSG, it is actually the assemblying body of two manual transmission, just get involved highly automated intelligentized electronic control system, so cost is very high, and reliability neither be very perfect, AMT mechanical automatic gearbox, the just automatic control of manual transmission, the slow pause and transition in rhythm or melody of its gear shift is unavoidable, although MT manual transmission structure is simple, reliable performance, cost are low, and the obvious inferior position of its complex operation gear switch pause and transition in rhythm or melody cannot make up.Above-described gearbox designs different performance is different, but there is any to be identical: to be all have a grade transmission, except MT is manual, other be all automatically control have a grade transmission, the maximum feature of grade transmission is had to be: the more efficiency of gear is higher in whole gear range, but its structure is also more complicated, reliability decrease, the larger efficiency of drop between two grades is lower, if so there is a unlimited gear in whole gear range, so certainly its transmission efficiency is the highest, travelling comfort and power performance are all best, stepless change that Here it is.But although variable transmission is universally acknowledged optimal type of belt drive, also be the ultimate aim of gear, but friction driving CVT does not also have grade efficiency of transmission MT high in the prior art, this is because friction and slide and control system consume a part of power, more crucially in the face of much fast changing road environment, its intelligent control system can not accomplish automatic adaptive stepless change ability forever, be inevitable so its efficiency is on the low side, a large defect is also had to be limited to material technology exactly in addition, high-power transmission cannot be realized, so friction driving CVT does not reach desirable transmission effect forever.Much very strange Design Conception is result in as the Research idea that some meshed transmission gear stepless change are different, but in these Design Conception, be substantially divided into two large classes: a class is by reducing gear or distortion gear etc., but all locks into structural limitations defect; Another kind of is utilize planetary pinion, realizes stepless change by controlling its one degree of freedom, but no matter how ingenious its project organization is, can only be finally: stall " stepless change " is so without any meaning.

In sum, optimal gear form is still stepless change, but prerequisite must can realize efficient high power, low cost structure is simple, reliable performance, more the more important is that must can to realize automatic adaptive stepless change ability this point extremely important, because electron controls technology does not accomplish this point forever, I am by years of researches through failure many times with after improving, and finally successfully developing this ideal infinitely variable transmission title is: " hydraulic planetary gear self adaption infinitely variable transmission ".

The content of invention

Structure of the present invention is very simple, but its combination really very ingenious, get around again the intellectual property of foreign enterprise and complicated automatical control system simultaneously, belong to original technology.Core main body part of the present invention is made up of two large divisions: the fluid torque converter after improvement and planetary gear set, planetary gear set is divided into single planetary gear construction, two-row planetary gear mono-tooth ring structure, two-row planetary gear Double gear-ring structure, differential planet gear structure and outer gearing planetary gear construction 5 kinds of citation forms, wherein single planetary gear construction is divided into two kinds of structures: two-row planetary gear mono-tooth ring structure and Double gear-ring structure, the difference that mono-tooth ring structure combines according to planet row is divided into again two kinds, these 5 kinds planetary basic structure forms respectively with improve after fluid torque converter, coaxial and the structural type connected is adopted to be combined into 8 kinds of concrete structure types of this gearbox, wherein single and compound planetary gearing, gear train can be Simpson also can be that Na Wei moves formula, but be that the Jia Nawei formula of moving is taken second place with Simpson, fluid torque converter after improvement its objective is can be coaxial and connect in order to realize fluid torque converter and planetary gear set, its technical characteristics is: a hollow axle sleeve one end is processed at the center of fluid torque converter and the housing seal of self is fixed, the other end stretches out outside housing, certain gap is retained to allow turbine shaft and guide wheel shaft from wherein passing through with housing, certain turbine shaft also needs to be processed to hollow, because this axle sleeve is from wherein passing through.The sun gear of planetary gear set of the present invention, gear ring, these three elements of planet carrier, planet carrier must be fixing output element i.e. driven member, sun gear and gear ring any one can as a fixing input element i.e. driving link, be that fixing input element is best with sun crop rotation.If planet carrier must be just fixed element when will realize reverse gear within this single or compound planetary gearing, or with sun crop rotation for inputting the best, gear ring is reverse gear output.

No matter be that planetary gears, its principle is all the same, it is fixing and need not exchange in turn that to be exactly input element and output element be all, move in formula planetary gears best as fixing output element using gear ring, so this project organization greatly reduces the complexity of structure at Na Wei.The compound mode of planetary gear set that the maximum innovative point of the present invention is the fluid torque converter after improving and combines with it, it is characterized in that: the turbine of fluid torque converter must and except input, the 3rd element outside output element namely " not moving part " link (namely traditional AT fixed block but in the present invention it really unfixed because it be connected with turbine), if will realize reverse gear in this simple planetary arrangement, third element is exactly reverse gear output element, and turbine only need be separated with it by clutch, original output element maintains static simultaneously, if Na dimension to move formula planetary gear set then different, but its principle is the same, the pump impeller of fluid torque converter must be connected with the output element of planetary gear set i.e. driven member, if two-row planetary gear structure or outer gearing planetary gear construction, then pump impeller needs and the link of front-seat output element, velocity ratio close to 1 time, for raising the efficiency pump impeller or being directly connected with input shaft by clutch, and though be that structure its planetaryly how much will to be determined by transmission power.

Accompanying drawing explanation

The present invention have chosen 6 accompanying drawings, wherein Fig. 4 is the fluid torque converter accompanying drawing after improving, Fig. 1 is single planetary gear construction, Fig. 2 is two-row planetary gear mono-tooth ring structure, Fig. 3 is two-row planetary gear Double gear-ring structure, Fig. 5 is outer gearing planetary gear construction, distressed structure (being exactly remove gear ring to increase planet row) its principle being exactly in fact Fig. 1 or Fig. 2 is living, but structural rate Fig. 1 and Fig. 2 is complicated, special more complicated than Fig. 1 a lot of and also when same velocity ratio designs radial dimension also relatively large, but its manufacturing process is relatively simple so Fig. 5 is an alternate techniques scheme, Fig. 6 is differential planet gear structure, principle and Fig. 1 of Fig. 3 are the same, also can combine with Fig. 2, Fig. 3 is a technological scheme for subsequent use in fact, it is all poor than Fig. 1 on stuctures and properties.Na Wei moves formula planet gear mechanism and does not make accompanying drawing, and its principle is the same, and just when itself and fluid torque converter combination, pump impeller, turbine are connected different with it.

Fig. 1 explanation

Fig. 1 is single planetary gear construction: 1 input shaft; 2 input end spring bearings; 3 clutches are arranged between input shaft 1 and face of fluid torque converter shell 5; 4 hollow shafts are by bearing housing on input shaft 1, and one end is then fixedly connected with a left side for planet carrier 12 (input shaft side is for left); 5 fluid torque converter shells and pump impeller are cast as one; 6 guide wheel output shafts are connected with gearbox stationary axle by overrunning clutch; 7 turbine output shafts, are directly connected with gear ring 10 or are connected with gear ring 10 by clutch; This axle sleeve of hollow shaft sleeve at 8 fluid torque converter centers is enclosed within fluid torque converter on hollow shaft 4 by unilateral bearing and bearing; 9 planetary pinions engage with gear ring 10 and sun gear 13 respectively, are fixed on planet carrier 12 by bearing and planet wheel shaft; 10 gear rings are fixed on support 11; 11 gear ring supports are by bearing and input shaft 1 concentric; 12 planet carriers by bearing housing on input shaft 1; 13 sun gears are fixedly connected with input shaft 1 as input original paper; 14 output terminal spring bearings; 15 output shafts are fixedly connected with on the right side of planet carrier 12; Clutch 3 between input shaft 1 and pump impeller shell 5 can not wanted, after removal clutch 3, face of fluid torque converter shell 5 is directly fixed on hollow shaft 4 by hollow shaft sleeve 8, and no longer need unilateral bearing, the single planetary structural type of another kind of Fig. 1 is: on described basis, remove hollow shaft 4 and clutch 3, face of fluid torque converter shell 5 is directly fixed on input shaft 1 by axle sleeve 8, and other are constant.

Fig. 2 explanation

Fig. 2 is two-row planetary gear mono-tooth ring structure, on the basis of Fig. 1, add a planet row, two planet rows share a gear ring 10, and independently of one another, the sun gear 17 of rear rows of planetary gear train is fixed on input shaft 1 equally for front-seat planet carrier 12 and rear seniority among brothers and sisters carrier 16, planet carrier 16 is fixedly connected with output shaft 15, planet wheel 18 engages with gear ring 10, sun gear 17 respectively, is fixed on planet carrier 16 by bearing and planet wheel shaft, clutch 3 can be removed rear face of fluid torque converter shell 5 equally and directly be fixed on hollow shaft 4, and no longer need unilateral bearing, the another kind of structural type of the two-row planetary gear mono-tooth ring structure of Fig. 2 is: get on to fall on described basis clutch 3, pump impeller shell 5 is directly fixed on hollow shaft 4 by axle sleeve 8, hollow shaft 4 is no longer connected with planet carrier 12, but be connected with sun gear 13, planet carrier 12 pass on left bearing and hollow shaft 4 is slidably connected, right side is fixedly connected with input shaft 1, sun gear 13 to be no longer fixed on input shaft 1 but to dissociate with it, other constant same these are also alternate techniques schemes.

Fig. 3 explanation

Fig. 3 is two-row planetary gear Double gear-ring structure: 1 input shaft; 2 spring bearings; 4 hollow shafts are connected with on the left of front planet carrier 12, and by bearing housing on input shaft 1, face of fluid torque converter shell 5 is fixed on this axle by axle sleeve 8; 5 face of fluid torque converter shells and pump impeller are connected as a single entity; 6 guide wheel output shafts are connected with gearbox stationary axle by unilateral bearing; 7 turbine output shafts and front ring gear 10 or with its support 11 directly or be connected by clutch; 8 fluid torque converter central axle sleeves; Before 9, planet wheel engages with front ring gear 10 and front sun gear 13 respectively; 10 front ring gears are fixedly connected with its support 11 (input shaft side is front); The support of 11 front ring gears 10 and input shaft 1 concentric; Planet carrier before 12; Before 13, sun gear is fixedly connected with input shaft 1; 14 output terminal spring bearings; 15 output shafts are connected with rear planet carrier 16; Planet carrier after 16; 17 rear sun gears are fixedly connected with input shaft 1 (be connected and be fixedly connected with or be affixedly one and look like); After 18, planet wheel engages with rear gear ring 20, rear sun gear 17 respectively; 19 connecting sleeves and input shaft 1 dissociate, is connected respectively with on the right side of front planet carrier 12, rear gear ring support 21 or afterwards gear ring 20 directly connect or connected by clutch; After 20, gear ring is fixedly connected with back poppet 21; The support of 21 rear gear rings 21 and input shaft 1 concentric.The another kind of structural type of this two-row planetary gear group Double gear-ring is: on described basis, remove hollow shaft 4, then fluid torque converter is fixedly mounted on the axle sleeve 19 between the planet row of front and back, for making the constant fluid torque converter of its Placement turn installation around, this is an alternative scheme.

Fig. 4 explanation

5 fluid torque converter shells and pump impeller are cast as one; 6 guide wheel output shafts; 7 turbine output shafts are processed to hollow; 8 fluid torque converter central hollow axle sleeves, one end and pump impeller body seal are fixed, and the other end stretches out outside housing and housing retains certain interval, so that by guide wheel shaft and turbine shaft.

Fig. 5 explanation

The structural principle of Fig. 5 and Fig. 1, Fig. 2 are in fact living, just it adopts outer gearing planetary gears, if left output sun gear 12 is more consistent than design with the tooth of right output sun gear 16, namely synchronization, so it is exactly the structural principle of Fig. 1, if namely design its rotating speed according to the needs of velocity ratio inconsistent asynchronous, so it is exactly the structural principle of Fig. 2.Its planet carrier 10 is the equal of the gear ring 10 of Fig. 1, Fig. 2, and left output sun gear 12 is the equal of the planet carrier 12 of the left side of the planet carrier 12 of Fig. 1, Fig. 2.Right output sun gear 16 is the equal of the planet carrier 16 of the right side of the planet carrier 12 of Fig. 1, Fig. 2.Equally with Fig. 1 Fig. 2 can design a clutch equally between input shaft 1 with pump impeller shell 5, pump impeller shell 5 is no longer fixedly connected with hollow shaft 4, but is connected by unilateral bearing.Its specific structural features is: 1 input shaft; 2 input end spring bearings; 4 hollow shafts are fixedly connected with left output sun gear 12, are contained on input shaft 1 by bearing housing, and face of fluid torque converter shell 5 is fixed on this hollow shaft 4 or is fixed on this hollow shaft 4 by unilateral bearing; 5 face of fluid torque converter shells; 6 guide wheel output shafts are fixed on the stationary axle of gearbox by overrunning clutch; 7 turbine output shafts are directly connected with planet carrier 10 or are connected with planet carrier 10 by clutch; The hollow shaft sleeve at 8 fluid torque converter centers; 9 intermediate planetary gear engage with input sun gear 13, are all fixed on planet wheel shaft 19 with left lateral star-wheel 18 right lateral star-wheel 17; 10 planet carriers and input shaft 1 concentric, its structure or three, left, center, right planet row is included in it; 12 left output sun gears are fixedly connected with by bearing housing on input shaft 1 with hollow shaft 4; 13 input sun gears are fixedly connected with input shaft 1, and 16 right output sun gears are fixedly connected with by bearing housing on input shaft 1 with output shaft 15; 14 output terminal spring bearings; 15 output shafts; 19 planet wheel shafts are fixed on planet carrier 10 by bearing; 17 right lateral star-wheels engage with right output sun gear 16; 18 left lateral star-wheels engage with left output sun gear 12; The tooth that left output sun gear and right output are taken turns very much needs and flexible design than according to designing; As required again between input shaft 1 and pump impeller shell 5 by filling a clutch, export sun gear 16 or output shaft 15 and be directly connected with back axle or the manual MT of contact in-between a simple planetary arrangement or 2 grades or 3 grades.Shift gear moment information is provided by the speed ratio of transformer turbine and pump impeller equally or the ratio of reaction force size of guide wheel provides, or the running state of gear ring provides, or three's Colaesce provides.

Fig. 6 explanation

The principle of Fig. 6 is the same with Fig. 1.Because structural limitations fluid torque converter needs oppositely to install, so need the torque-converters of antiport, 1 input shaft; 2 input end spring bearings; 4 hollow shafts are fixedly connected with by bearing housing on input shaft 1 with cone dish gear 19; 8 fluid torque converter central hollow axle sleeve fluid torque converters, by this axle sleeve, are arranged on hollow shaft (4); 7 turbine output shafts are connected with hollow shaft 4; 6 guide wheel output shafts are connected with gearbox stationary axle by unilateral bearing; 5 face of fluid torque converter shells are connected with planet carrier 21; 19 cone dish gears and input shaft 1 are slidably connected; 20 bevel gears and its axle 23 are slidably connected, and engage respectively, be fixed on planet carrier 21 by its axle with cone dish gear 19 cone dish gear 22; 21 planet carriers are by bearing and input shaft 1 concentric; 14 output shaft spring bearings; 15 output shafts are fixedly connected with planet carrier 21; 22 cone dish gears are fixed on input shaft 1; 23 bevel gear shafts; 24 bevel gear shaft fixed covers, by bearing housing on input shaft 1.

Fluid torque converter after this gearbox improves, no longer contact with planetary gear set and direct transferring power, but it is coaxial and connect with planetary gear set, by controlling and adjustment planetary gear set, the speed discrepancy of other two elements outside input thus indirectly outputting power, so the difference that designs according to velocity ratio of its size that can hold and different structural type and change to some extent, can introduce in detail in embodiment, this gearbox is because it is in whole gear range, it is all automatic adaptive stepless change, so the fluid torque converter after its improvement no longer can need lock-up clutch.

Embodiment

Existing connection with figures further illustrates transmission principle of the present invention and embodiment, the different performance of the fluid torque converter of this gearbox, the velocity ratio design of its planetary gear set will be determined, and different velocity ratio designs and the different transmission efficiencies corresponding to structure type are different, so the performance of this gearbox fluid torque converter, the velocity ratio size of planetary gear set, and be a function relation between transmission efficiency, in order to more figuratively its principle bright, use traditional AT automatic transmission case transmission principle so that the principle of the invention to be described.

Tradition AT automatic transmission case is in order to change tradition ratio, the driving link of its planetary gear set, driven member, fixed block exchanges in turn, and in order to realize shift process, multiple clutch and lock-up clutch is controlled with regard to needing complicated automatical control system, so structure is very complicated but also be have a grade transmission, fluid torque converter is directly connected with planetary gear set, that direct power transmitting elements pump impeller and engine direct connect in succession, so its rotating speed forever and engine synchronization start operating performance and resistance very large time the fast situation of arrow under its efficiency be 0 or very low substantially, and peak efficiency is also low than manual transmission by about 20%, if converter lockup, it in fact also just becomes AMT mechanical automatic speed-changing case, so the efficient district scope of fluid torque converter is rather narrow in traditional AT, the mechanics feature of distributing of planetary gear set is: driving link, driven member, in these three elements of fixed block, reaction force size suffered by fixed block equals velocity ratio all the time and subtracts 1, in tradition AT, holding of fluid torque converter needs 1 all the time, the output power of this 1 namely motor, so the efficiency of the efficiency of fluid torque converter i.e. gearbox (disregarding gear loss).In the present invention because fluid torque converter is no longer directly connected with planetary gear set but in parallel, pump impeller is connected with driven member, turbine is connected with " fixed block " (because being connected with turbine so be unfixed), so can hold for velocity ratio subtracts 1 needed for it, this velocity ratio subtracts 1, and namely the power of motor or moment of torsion are multiplied by velocity ratio, and then subtract 1, turbine because of the resistance be connected with " fixed block " suffered by it be all under any circumstance that velocity ratio subtracts 1, but pump impeller can hold size when engine speed is fixing, an inversely prroportional relationship with the size of velocity ratio, because turbine is connected with driven member, along with its rotating speed of increase of velocity ratio can decline gradually, and rotating speed decline its can hold can corresponding reduction namely absorb the power of driving link can corresponding reduction, output power on driven member can corresponding increase, the reduction that meanwhile turbine and the speed ratio of pump impeller also can be corresponding, and its displacement coefficient of the reduction of speed ratio can increase, so the output torque of turbine or power all equal velocity ratio all the time and subtract 1 when the velocity ratio design of the performance planetary gear set of fluid torque converter is mated very much.

The transmission principle of this embodiment of analysis chart 1 is carried out by above-mentioned principle, in three elements of planetary gear set, sun gear 13 is fixing active members, with input shaft 1 is affixed, it first supposes that its power or moment of torsion are 1, rotating speed is also 1, gear train velocity ratio is designed to 2, and so the reaction force of " fixed block " gear ring 10 equals velocity ratio all the time and both subtracted 1: 2-1=1, the output power of driven member planet carrier 12 or moment of torsion all equal its maximum transmission ratio 2 all the time, but the power really acted on output shaft 15 or moment of torsion are not but steady state values, but change the size variation of namely suffered resistance along with the change of velocity ratio and automatically adaptively carry out stepless change, its transmission principle is when starting rotating speed to remain unchanged, velocity ratio close to 1 time, the input power of driving link sun gear 13 or moment of torsion are 1, because maximum transmission ratio is 2 so the power that acts on planet carrier 12 or moment of torsion are always 2, but this power or moment of torsion 2 are not act on output shaft 15 completely, equal velocity ratio subtract 1:2-1=1 so have the power of half or moment of torsion to be absorbed by the pump impeller 5 of hydraulic pitch device according to holding of fluid torque converter, the reaction force of gear ring 10 equals velocity ratio all the time and subtracts 1, 2-1=1, so at the coupling operating point of fluid torque converter, the power that pump impeller absorbs or moment of torsion just by turbine output shaft by the counterforce counteraction of gear ring 10, so the moment of torsion finally acted on output shaft 15 equals 1 or close to 1, but power be less than 1 because of fluid torque converter coupling operating mode speed ratio be 0.85, namely efficiency 85% velocity ratio close to 1 time this gearbox transmission efficiency forever can not reach 100% because the coupling operating mode speed ratio of fluid torque converter is 0.85, so the rotating speed of the driven member planet carrier 12 fixed block gear ring 10 of planetary gear set can not so the present invention synchronous with driving link sun gear 13 velocity ratio close to 1 time transmission efficiency be how many actually, when namely driving link sun gear 13 is 1 with the torque ratio of output shaft 15, driven member 12 is multiplied by 100% with the speed ratio of driving link 13 is exactly efficiency, its formula is: set the rotating speed of driving link sun gear 13 as 1, driven member planet carrier 12 namely face of fluid torque converter rotating speed is x, fluid torque converter coupling operating point speed ratio 0.85, so the rotating speed of turbine 7 or " fixed block " gear ring 10 is 0.85x velocity ratio is i, formula: it is exactly efficiency that (1-0.85x) ÷ i+0.85x=x result of calculation is multiplied by 100% again, according to formula when velocity ratio is designed to 2, when velocity ratio is close to 1, its efficiency is 87%, this is calculated value, disregard gear loss but at this moment planetary gear set be become a steel body and outputting power substantially, so the consumption of gear is very small, in fact when velocity ratio is slightly less than 1, the rotating speed of pump impeller can rise automatically, and it can hold and can strengthen accordingly, and resistance suffered by turbine can corresponding reduction, at this moment the speed ratio of transformer turbine and pump impeller can more than 0.9, so at this moment the efficiency of this gearbox is minimum also more than 90%.

Velocity ratio increase gradually until maximum transmission ratio time its efficiency be how many again? along with the increase turbine 7 of velocity ratio or the wheel speed of gear ring 10 can decline until be 0 gradually, the rotating speed of pump impeller also declines accordingly, until the rotating speed of rotating speed during maximum maximum transmission ratio i.e. driving link sun gear 13 is divided by its velocity ratio, meanwhile the speed ratio of turbine and pump impeller also in corresponding reduction until be that the height of 0 its efficiency can hold penetration with the relative of fluid torque converter and displacement coefficient has quite close corresponding relation, the displacement coefficient of fluid torque converter is larger relatively can hold less, velocity ratio design its efficiency less is higher, or be 2 come illustratively with velocity ratio, its principle is: the reaction force because of gear ring 10 is all that velocity ratio subtracts 1 all the time, 2-1=1, so the output power of turbine 7 or moment of torsion must be also 1 all the time, output power or the moment of torsion of driven member planet carrier 12 also equal 2 all the time, velocity ratio close to 1 time pump impeller can hold for velocity ratio subtracts 1, 2-1=1, and when maximum transmission ratio because the rotating speed of the rotating speed of turbine 7 or gear ring 10 is 0, the rotating speed of corresponding driven member 12 namely pump impeller only has 1 ÷ 2=0.5 (driving link rotating speed is 1), so the energy appearance of its pump impeller can significantly decline accordingly, if at this moment only have 0.2 (when being 1 relative to velocity ratio 1/5) namely only to absorb 1/10 of driven member 12 power holding of pump impeller, so power on output shaft 15 or moment of torsion equal its efficiency of 2-0.2=1.8 namely 90%, but prerequisite be fluid torque converter can hold its 0 fast displacement coefficient when being 0.2 required reach 5 could the reaction force 1 of corresponding " fixed blocks " 10, so the K of fluid torque converter ₀value size and relatively can hold and velocity ratio design between be an interactive relationship, if can hold is 0.4, K ₀value is 2.5 so its efficiency namely 80%, its efficiency calculation formula is: set η as efficiency, i is velocity ratio, λ B is fluid torque converter capacity factor, K is the displacement coefficient of fluid torque converter, η=(i-λ B) ÷ i × 100%, but must be the reaction force that λ B × K just equals " fixed block " gear ring 10, so this single planetary gear construction form of computational analysis Fig. 1 by experiment, under the fluid torque converter condition of prior art, its matching range is narrow, so in order to widen fluid torque converter and planetary gear set velocity ratio design between matching range just need to use this two-row planetary gear structural type of Fig. 2, its transmission principle has been living just not repeated description.The another kind of structural type of Fig. 1, Fig. 2 is the alternate techniques scheme after the fluid torque converter going out to match for Future Development, so its principle cannot realize at fluid torque converter under prior art conditions.This embodiment of Fig. 5 of the present invention is exactly the distressed structure of Fig. 1, Fig. 2 in fact, and principle is the same, and Fig. 6 is exactly the principle of Fig. 1 in fact, so Fig. 5, Fig. 6 are alternate techniques schemes.

All embodiments in accompanying drawing of the present invention are when gear range and vehicle match, it is exactly a complete gearbox, only need design a reverse gear or increase by one or two clutch and " fixed block " of planetary gear set is increased a reverse gear function, if gear range does not reach the usage requirement of vehicle, then only need at the driven member of planetary gear set or output shaft 15 and a single or double gear mechanism of connecting again between back axle, or two grades, the manual transmission of third gear, the speed ratio of the turbine and pump impeller that have fluid torque converter provides by its gearshift information, or the ratio of reaction force size provides suffered by guide wheel, or the running state of gear ring provides, or triple combination provides.

The present invention and traditional AT automatic transmission case efficiency comparison, tradition AT when fluid torque converter not locking have certain automatic adaptive stepless shift function, so its efficiency i.e. the efficiency of gearbox, be characterized in along with lowering efficiency of speed ratio sharply declines until be 0, when the speed ratio of turbine and pump impeller is 0.5, its efficiency is about 70%, efficiency about 53% when speed ratio is 0.3, speed ratio is 0 its efficiency is also 0, but this single planetary gear construction type of the present invention Fig. 1 when fluid torque converter performance is identical, cause is principle of parallel, so when the drive element of planetary gear set and the speed ratio of active member are 0.5 efficiency more than 80%, relatively traditional AT efficiency improves more than 10%, when speed ratio 0.3, efficiency almost improves nearly 40% more than 75%, the K of fluid torque converter in traditional AT ₀when namely increasing moment of torsion 2,3 or 4 times time value is 2,3 or 4, its efficiency is 0, but in this embodiment of Fig. 1 of the present invention, time the output torque of output shaft 15 increases by 2,3 or 4 times, its efficiency is respectively: 66.6%, 75%, 80%, the present invention contrasts traditional AT and has overwhelming dominance as can be seen here, and the K of fluid torque converter ₀be worth its efficiency higher higher.

If this embodiment of Fig. 3 is designed to about 2 at the velocity ratio of fluid torque converter existence conditions planetary gear set, its transmission efficiency in whole gear range all can remain on more than 90%, first sets its velocity ratio as 2 to illustrate transmission principle.The maximum difference of Fig. 3 and Fig. 2 is exactly that mono-tooth ring is divided into two separate front ring gears 10 and rear gear ring 21, the planet carrier 12 of front planet row is connected by the gear ring 20 of hollow shaft sleeve 19 and rear planet row or gear ring support 21, if remove its structure of rear planet row and Fig. 1 is living, just eliminate clutch 3, axle sleeve 19 is output shaft 15 namely.Rear planet row is the same with the structure of front planet row, front sun gear 13, rear sun gear 17 are all fixed on input shaft 1, so these two planet rows seem independent series connection add one-level gear transmission seemingly, but be actually its transmission efficiency of parallel relationship or single planet principle.4,3 or 3,4 are designed to respectively by the velocity ratio calculating front and back planet row, be just 0.5 when the rotating speed of front ring gear 10 is that the rotating speed of gear ring is just the rotating speed of 0.25 or 0.33 (setting input shaft rotating speed as 1) output shaft 15 after 0, just in time corresponding velocity ratio is 2.First planet row velocity ratio be after 4 planet rows velocity ratio be 3 its principle is described for example, total output or the moment of torsion of input shaft 1 are set to 1, velocity ratio close to 1 time, the power of rear sun gear 17 need 0.333 or moment of torsion its act on power on output shaft 15 or moment of torsion just close to 1, but the reaction force velocity ratio of gear ring 20 subtracts 1, so the reaction force acted on gear ring 20 is 0.666, this reaction force of 0.666 acts on again on front planet carrier 12, the power of input shaft 1 is employed 0.333 by rear planet row, so just also remain 0.666, the velocity ratio ratio of front planet row is 4, so fluid torque converter can hold for velocity ratio subtracts 1 namely 0.666 × 4-0.666=2, therefore velocity ratio is 4 so the power that acts on planet carrier 12 or moment of torsion are 0.666 × 4=2.666, just absorbed 2 by face of fluid torque converter, also surplus 0.666 just by the counterforce counteraction of rear gear ring 20, and the power of pump impeller or moment of torsion 2 pass through turbine 7 by the counterforce counteraction of its front ring gear 10, Here it is velocity ratio close to 1 time power division principle, so its efficiency is how many actually, according to formula above, the planet carrier 12 of front planet row is 0.67 with the speed ratio of sun gear 13, because planet carrier 12 is connected with rear gear ring 20, so output shaft 15 or planet carrier 16 and the speed ratio of sun gear 17 are that 0.78 seemingly efficiency is very low, but in fact because of fluid torque converter can hold be 2 when velocity ratio is slightly less than 1 the rotating speed of its pump impeller can significantly rise about 30%, and the left and right that can double accordingly can be held, but the reaction force of gear ring 10 reduces relatively, so the rotating ratio of transformer turbine and pump impeller even can reach 0.95, so this embodiment of Fig. 3 velocity ratio close to 1 time its efficiency can more than 90%.Efficiency when maximum transmission ratio 2 is how many, during maximum transmission ratio, the rotating speed of gear ring 10 is 0, the rotating speed of planet carrier 12 is 0.25, so the energy appearance of fluid torque converter can decline to a great extent and displacement coefficient also reaches maximum, the rotating speed of output shaft 15 or planet carrier 16 is 0, 5, if its output power of efficiency 100% or moment of torsion are just 2, but equally because the loss of fluid torque converter can not reach 100%, if efficiency is 90%, the output power of output shaft 15 is 2 × 90%=1.8 sun gear 17 power demand: 1.8 ÷ 3=0.6, the reaction force of gear ring 20: 1.8-0.6=1.2, velocity ratio because of front planet row is 4, and input shaft 1 also remains the power of 0.4, so be just 1.2 to balance with the reaction force of gear ring 20 when the power of sun gear 13 need 0.3 acts on planet carrier 12, but meanwhile gear ring 10 creates again the reaction force (reaction force equals velocity ratio and subtracts 1) of 0.9, last input shaft 1 namely sun gear 13 also surplus 0.1 power equal 0.4 when acting on planet carrier 12, because the rotating speed of at this moment planet carrier 12 have dropped several times, so fluid torque converter can hold relative transmission ratio close to 1 time have dropped 5 times, just absorb this power of 0.4, but meanwhile gear ring 10 creates again the reaction force of 0.3, therefore total reaction force of gear ring 10 is 1.2, fluid torque converter can hold and is 0.4 and needs K ₀value is 3 just.The present invention in self adaption stepless change process, along with the reduction of speed ratio, fluid torque converter can hold also corresponding reduction, no matter so it there is not the serious problem of heating under any operating mode.This embodiment of Fig. 3 improves more than 20% relative to its efficiency when the speed ratio of transformer turbine and pump impeller is 0.5 in traditional AT, if gear range can not meet vehicle needs, only need output shaft 15 or planet carrier 16 with connect between back axle a simple planetary arrangement or 2 grades, 3 grades MT gearboxes just passable.

The feature of motor is: when throttle opening and fuel injection quantity constant, rotating speed corresponding to peak efficiency is fixing, if so power is 1 under this rotating speed, having in grade transmission process, (between because of two-stage, drop is large particularly with between 1 grade and 2 grades, after the most high-grade) if resistance is greater than 1 or be less than 1, capital makes the rotating speed of motor decline or rises thus lower efficiency, but if automatic adaptive stepless change, then the rotating speed of motor can remain unchanged, gearbox can automatic adaptive reduction rotating speed or increase moment of torsion or raise rotating speed reduce moment of torsion, so machinery driving efficiency of the present invention seems lower than manual transmission, but its minimum efficiency more than 30% improving motor, so its actual operating efficiency can be higher than automatic transmission case by more than 10%.

Contrasting this invention calculates, the actual operating efficiency of certain 6 grades of manual transmission or two clutch gearbox:

Average efficiency in whole gear range:

(0.876+0.829+0.869+0.875+0.901)÷5＝85.2％

Above result of calculation can be found out, most effective manual transmission, its actual operating efficiency is on the low side, efficiency between two grades on average only has 85.2%, the loss of gear is also not very interior, why can be this result, the transmission efficiency of gear or the transmission efficiency of manual transmission are all more than 97%, it is that machinery driving efficiency is high in fact, and for the power that motor sends, with road environment complicated and changeable, the resistance of adding different driving habits vehicle travelings is fast changing, it is an irregular curve, and the velocity ratio change of manual transmission or automatic transmission case is discontinuous, it is several points in stepless change trajectory, so its efficiency is on the low side.With the efficiency of the transmission between 1 grade and 2 grades illustratively, suppose that vehicle is now just with 1 grade of traveling, and the resistance of its resistance when being just 1 grade of maximum transmission ratio, so at this moment, its transmission efficiency is 100%, if resistance ratios 2 grades is slightly large, and less than 1 grade a lot of time, if at this moment change 2 grades, power is inadequate, but can only continue with 1 grade waste a lot of power, efficiency also reaches minimum.The practical efficiency of manual transmission most effective is as can be seen here lower than the present invention by more than 5%, and is exactly that first-class driver at every moment can not can hold best Shift gear moment, so its efficiency also will reduce by more than 5%.If its transmission efficiency of AT automatic transmission case is how many again, calculate by the highest average efficiency 80% of fluid torque converter: 85.2% × 80%=68%, the transmission efficiency of 6 grades of AT automatic transmission case is less than 70% as can be seen here, and its control system can not hold best Shift gear moment equally, so its efficiency also will reduce by more than 5%.6 grades above manually or automatically its maximum transmission ratio of gearbox are 4.15, if expand its gear range again, its efficiency also can decline, if 8 very high-end speed dual clutch or AT automatic transmission case, its efficiency can be higher by 3.3% or about 4% than the difference of 6 grades, no matter be several grades of gearboxes in fact, its the most high-grade efficiency is minimum, on average can not more than 70%, because on good road, many times the fastest ratio that runs of vehicle even can below 0.3, and the most high-grade velocity ratio of most of vehicle is about 0.7.

Structure of the present invention is simple, and without any friction means and automatical control system, its reliability and durability do not need spended time to check, and its automatic adaptability stepless change ability is that electronic technology is not accomplished forever.

Claims

1. a hydraulic planetary gear self adaption infinitely variable transmission, this gearbox subject core part is made up of two large divisions, fluid torque converter after improvement and planetary gear set, planetary gear set is divided into single planetary gear construction, two-row planetary gear mono-tooth ring structure, two-row planetary gear Double gear-ring structure, differential planet gear structure and outer gearing planetary gear construction 5 kinds of basic structure forms, respectively with improve after fluid torque converter, coaxial and the structural type connected is adopted to be combined into 8 kinds of concrete structure types of this gearbox, wherein single and two-row planetary gear structure is most basic model, the output element of planetary gear set i.e. driven member when forward gears, input element i.e. driving link, fixing need not exchanging in turn, the compound mode of planetary gear set that maximum innovative point of the present invention is the fluid torque converter after improving and combines with it, it is characterized in that: the pump impeller of fluid torque converter must be connected with the output element of planetary gear set i.e. driven member, turbine must with the input of planetary gear set, the not moving part of the third element outside output element i.e. traditional AT connects, if two-row planetary gear or outer gearing planetary gear construction then pump impeller must be connected with front-seat output element, if adopt Simpson planetary gear set, then planet carrier must be fixing output element, sun gear and gear ring are appointed can as fixing input element using one, but be that fixing input element is for the best with sun gear, if adopt Na dimension to move formula planetary gear set, then gear ring is best as fixing output element, or with input element the best that sun crop rotation is fixing, no matter be that planetary gear construction, how much it planetary will be determined by transmission power if being.

2. a kind of hydraulic planetary gear self adaption stepless gearbox according to claim 1, is characterized in that, the single planetary gear construction type of this gearbox described it comprise: input shaft (1) is fixedly connected with sun gear (13); Input end spring bearing (2); Clutch (3) is arranged between input shaft (1) and face of fluid torque converter shell (5); Hollow shaft (4) is by bearing housing on input shaft (1), and one end is fixedly connected with the left side of planet carrier (12) (input shaft side is for left); Fluid torque converter shell (5) and pump impeller are cast as one or are pump impeller shell; Guide wheel output shaft (6) is connected with gearbox stationary axle by overrunning clutch; Turbine output shaft (7) is direct or be connected with gear ring (10) by clutch; Hollow shaft sleeve (8) one end at fluid torque converter center and the housing seal of self are fixed, one end is stretched out outside housing and is retained certain interval with housing, this hollow shaft sleeve directly or by bearing and unilateral bearing fluid torque converter be arranged on hollow shaft (4) upper or after removing clutch 3 pump impeller shell (5) be directly fixed on hollow shaft (4) and do not need unilateral bearing; Planetary pinion (9) engages with gear ring (10), sun gear (13) respectively, is fixed on planet carrier (12) by bearing and planet wheel shaft; Gear ring (10) is fixed on gear ring support (11); Gear ring support (11) is by bearing and input shaft (1) concentric; Planet carrier (12) is by bearing and input shaft (1) concentric; Sun gear (13) is fixedly connected with input shaft (1) as input element; Output terminal spring bearing (14); Output shaft (15) is fixedly connected with the right side of planet carrier (12); For expanding gear range at double, as required again at output shaft (15) or between planet carrier (12) and back axle, to contact a single or compound planetary gearing, or 2 gear or 3 gears, 4 blocks move MT gearbox, its gearshift occasion information is provided by the speed ratio by transformer turbine and pump impeller or the ratio of reaction force size of guide wheel provides, or the running state of gear ring provides, or three's Colaesce provides.

3. a kind of hydraulic planetary gear self adaption infinitely variable transmission according to claim 1, it is characterized in that, the two-row planetary gear mono-tooth ring structural type of this gearbox described, it comprises: described in claim 2 single planetary gear construction type basis on add a planet row, two planet rows share gear rings (10); Front-seat planet carrier (12) is independent of one another with rear seniority among brothers and sisters carrier (16), is connected respectively with face of fluid torque converter shell (5) and output shaft (15); Sun gear (17) is fixed on input shaft (1) equally; The right side of planet carrier (16) is fixedly connected with output shaft (15); Planet wheel (18) engages with gear ring (10) sun gear (17) respectively, is fixed on planet carrier (16) by bearing and planet wheel shaft; Other technical characteristics is without any change; For providing overdirve gear or more big speed ratio, only need at the manual MT gearbox of output shaft (15) or planet carrier (16) series winding one single or compound planetary gearing or 2-3 shelves below, its Shift gear moment information is provided by the speed ratio of transformer turbine and pump impeller equally or the ratio of reaction force size of guide wheel provides, or the running state of gear ring provides, or three's Colaesce provides.

4. a kind of hydraulic planetary gear adaptive rate case according to claim 1, it is characterized in that, the two-row planetary gear Double gear-ring structural type of this gearbox described, it comprises: input shaft (1); Spring bearing (2); Hollow shaft (4) and front planet carrier (12) left side is connected (connect and affixed be one look like), by bearing housing on input shaft (1); Fluid torque converter shell (5) and pump impeller are cast as one and are pump impeller shell, by the axle sleeve (8) at its center, fluid torque converter are arranged on hollow shaft (4) upper affixed with it; Guide wheel output shaft (6) is connected with gearbox stationary axle by unilateral bearing; Turbine output shaft (7) and front ring gear (10) or with fore poppet (11) directly or be connected by clutch; Fluid torque converter central axle sleeve (8) one end and self housing seal affixed; Front planet wheel (9) engages with front ring gear (10), front sun gear (13) respectively; Front ring gear (10) and its support (11) affixed (input shaft side is front); Front ring gear support (11) and input shaft concentric; Front planet carrier (12); Front sun gear (13) is affixed with input shaft (1); Output terminal spring bearing (14); Output shaft (15) is connected with rear planet carrier (16); Rear sun gear (17) is affixed with input shaft (1); Rear planet wheel (18) engages with rear gear ring (20), rear sun gear (17) respectively; Connecting sleeve (19) and input shaft (1) dissociate, and be connected respectively, rear gear ring (20) or its support (21) directly connected or connected by clutch with front planet carrier (12) right side; Rear gear ring (20) and its support (21) are affixed with input shaft concentric; As required again rear planet carrier (16) or output shaft (15) with connect between back axle one single or double one single or compound planetary gearing or 2 keeps off, 3 keep off MT manual transmission, its gearshift occasion information is provided by the speed ratio of transformer turbine and pump impeller equally or the ratio of reaction force size of guide wheel provides, or the running state of gear ring provides, or three's Colaesce provides.

5. according to claim 1, a kind of hydraulic planetary gear self adaption infinitely variable transmission, it is characterized in that: one of subject core part of this gearbox described, fluid torque converter after improvement, because the fluid torque converter after improving adopts coaxial Parallel connection structure with planetary gear set, so its center needs the axle sleeve being processed to hollow, it comprises: fluid torque converter shell (5) and pump impeller are cast as one; Guide wheel output shaft (6); Turbine output shaft (7) is processed to hollow; Fluid torque converter central hollow axle sleeve (8), one end and pump impeller body seal are fixed, the other end stretches out outside housing and housing retains certain interval, so that guide wheel shaft (6) and turbine shaft (7) pass through, if pump impeller shell (5) directly sealing is fixed on relevant axle, then do not need hollow shaft sleeve (8).

6. a kind of hydraulic planetary gear self adaption infinitely variable transmission according to claim 1, it is characterized in that: the outer gearing planetary gear construction type of this gearbox described, it comprises: input shaft (1); Input end spring bearing (2); Hollow shaft (4) is fixedly connected with left output sun gear (12), be contained on input shaft (1) by bearing housing, face of fluid torque converter shell (5) is fixed on this hollow shaft or is fixed on this hollow shaft by unilateral bearing; Face of fluid torque converter shell (5); Guide wheel output shaft (6) is fixed on the stationary axle of gearbox by overrunning clutch; Turbine output shaft (7) is directly fixedly connected with planet carrier (10) or is connected with planet carrier (10) by clutch; The hollow shaft sleeve (8) at fluid torque converter center; Intermediate planetary gear (9) engages with input sun gear (13), is all fixed on planet wheel shaft (19) with left lateral star-wheel (18) right lateral star-wheel (17); Planet carrier (10) and input shaft (1) concentric, its structure or three, left, center, right planet row is included in it; Left output sun gear (12) is fixedly connected with by bearing housing on input shaft (1) with hollow shaft (4); Input sun gear (13) is fixedly connected with input shaft (1), and right output sun gear (16) is fixedly connected with by bearing housing upper at input shaft (1) with output shaft (15): output terminal spring bearing (14); Output shaft (15); Planet wheel shaft (19) is fixed on planet carrier (10) by bearing; Right lateral star-wheel (17) engages with right output sun gear (16); Left lateral star-wheel (18) engages with left output sun gear (12); The tooth that left output sun gear and right output are taken turns very much needs and flexible design than according to designing; As required again between input shaft (1) and pump impeller shell (5) by filling a clutch, export sun gear (16) or output shaft (15) to be directly connected with back axle or the manual MT of contact in-between a simple planetary arrangement or 2 grades or 3 grades, Shift gear moment information is provided by the speed ratio of transformer turbine and pump impeller equally or the ratio of reaction force size of guide wheel provides, or the running state of gear ring provides, or three's Colaesce provides.

7. a kind of hydraulic planetary gear self adaption infinitely variable transmission according to claim 1, it is characterized in that: the differential planet gear structural type of this gearbox described, oppositely need install fluid torque converter, it comprises: input shaft (1); Input end spring bearing (2); Hollow shaft (4) is fixedly connected with cone dish gear (19), by bearing housing on input shaft (1); Fluid torque converter central hollow axle sleeve (8), fluid torque converter is arranged on hollow shaft (4) by this axle sleeve; Turbine output shaft (7) is connected with hollow shaft (4); Guide wheel output shaft (6) is connected with gearbox stationary axle by overrunning clutch; Face of fluid torque converter shell (5) is connected with planet carrier (21); Cone dish gear (19); Bevel gear (20) and its axle (33) are slidably connected, and engage respectively, be fixed on planet carrier (21) by its axle (33) with cone dish gear (19), cone dish gear (22); Planet carrier (21) is by bearing and input shaft (1) concentric; Output shaft spring bearing (14); Output shaft (15) is fixedly connected with planet carrier (21); Cone dish gear (22) is fixed on input shaft 1; Bevel gear shaft (23); Bevel gear shaft fixed cover (24) by bearing housing on input shaft (1).

8. the single planetary gear construction type of a kind of hydraulic planetary gear self adaption stepless gearbox according to claim 2, it is characterized in that: on described basis, remove hollow shaft (4) and clutch (3), face of fluid torque converter shell (5) is directly fixed on input shaft (1) by axle sleeve (8), and other are constant.

9. the two-row planetary gear mono-tooth ring structural type of a kind of hydraulic planetary gear self adaption infinitely variable transmission according to claim 3, it is characterized in that: get on to fall on described basis clutch (3), pump impeller shell (5) is directly fixed on hollow shaft (4) by its axle sleeve (8), hollow shaft (4) is no longer connected with planet carrier (12) but is connected with sun gear (13), planet carrier (12) passes on left bearing housing on hollow shaft (4), right side and input shaft (1) affixed; Sun gear (13) is no longer fixed on input shaft (1), but dissociates with it, and other is constant.

10. the two-row planetary gear Double gear-ring structural type of a kind of hydraulic planetary gear self adaption infinitely variable transmission according to claim 4, it is characterized in that: on described basis, remove hollow shaft (4), then fluid torque converter is fixedly mounted on the axle sleeve 19 between the planet row of front and back, for making its Placement constant, fluid torque converter need turn installation around, that is: guide wheel output shaft side need towards front-seat planetary gear set, and other are constant.