CN103307248B - Reverse-flow type hydrodynamic mechanical automatic variable transmission device - Google Patents
Reverse-flow type hydrodynamic mechanical automatic variable transmission device Download PDFInfo
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- CN103307248B CN103307248B CN201310260071.0A CN201310260071A CN103307248B CN 103307248 B CN103307248 B CN 103307248B CN 201310260071 A CN201310260071 A CN 201310260071A CN 103307248 B CN103307248 B CN 103307248B
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Abstract
The invention discloses a kind of reverse-flow type hydrodynamic mechanical automatic variable transmission device, comprise input shaft, jack shaft, planet row and fluid torque converter, wherein said planet row comprises planet carrier, sun gear and gear ring, described fluid torque converter comprises pump impeller and turbine, described jack shaft one end is connected with described input shaft, the other end is connected with described planet carrier, and described sun gear is connected with described pump impeller, and described turbine and described input shaft are connected.The characteristic of the shunting that the present invention utilizes planet row intrinsic/interflow power and velocity composite, fluid torque converter is inverted in return flow path significantly to reduce power loss, and pass through the omnidistance stepless change of the whole speed variator system of continuous speed adjustment functional realiey of fluid torque converter, the characteristic utilizing power to reflux continues the effect retaining whole variable ratio drive system low speed torque increasing, reaches the objects such as transmission efficiency is high, power loss is little.
Description
Technical field
The invention belongs to technical field of mechanical transmission, specifically, relate to a kind of reverse-flow type hydrodynamic mechanical automatic variable transmission device.
Background technique
On current automobile, the transmission device of a large amount of continuously variable adopted mainly comprises metal tape/metal chain transmission and hydraulic machine gear two kinds of modes, the regulation slowest ratio of speed change gear and the ratio of minimum speed ratio are its speed ratio excursion, for a kind of desirable car stepless change system, its variator ratio range just ensures that more than 6 the steady operation point of motor under different accelerator open degree is all the time in the best then economic line.With regard to metal tape/metal chain vari-speed drive, by the restriction of physical dimension, its speed ratio excursion is generally about 5.1, lower than car speed variator system theoretical velocity ratio excursion.Under the prerequisite meeting car drive, in order to ensure engine steady state operation point all the time on best fuel-economy guide line, must widen the speed ratio excursion of metal tape/metal chain electrodeless variable-speed transmission, also there is transmission efficiency problem on the low side in metal tape/metal chain vari-speed drive.Number of patent application is 200610054549.4, name is called that the application for a patent for invention of " return flow type stepless speed change driving device for automobile " discloses a kind of automative stepless speed-variation transmission device using metal tape as backflow speed regulating mechanism, this return flow type stepless speed change driving device for automobile mainly by: metal tape stepless speed-regulating device, constant-speed ratio transmission device, planetary row device, clutch pack, break, primary speed-down gear pair, differential mechanism etc. form, and object is to overcome the problem that existing automative stepless speed-variation transmission device speed ratio excursion is partially narrow, transmission efficiency is on the low side.
With regard to hydraulic machine gear: at present, hydraulic mechanical is applied widely in driveline of construction machines, the transmission efficiency improving power train is very important.Known hydraulic mechanical is fluid torque converter, speed-changing gear box, main transmission and whole transmission composition, make full use of the effect of fluid torque converter low speed torque increasing, employing fluid torque converter is started to walk, and after automobile speed reaches a certain value locking torque converter, make hydrodynamic mechanical transmission become pure mechanical transmission, eliminate torque-converters average efficiency defect on the low side with this; The major defect of this transmission is because torque converter is low and become parabolic shape, low speed to be started from scratch increase than efficiency when operating mode and vehicle launch, usually reach 75% to think and enter efficient district, start decline by best efficiency point to enter and at a high speed start sharply to decline than time, absolute zero load is efficiency is zero.
Particularly, occurred various types of automatic transmission case such as AT, AMT, CVT, DCT, one, hydraulic automatic speed variator (AT.AutomaticTransmission), its citation form is fluid torque converter and the connecting of type rotary shaft mechanical transmission.The major advantage of this hydraulic automatic speed variator has: 1. the automatic adaptability of fluid torque converter makes it have stepless change and the bending moment ability of certain limit, has and automatically regulates and conformability, radically simplify operation to external loading; 2. hydraudynamic drive itself has certain damping performance, effectively can reduce S.acus Linnaeus exact and the rotational-torsional of power train, extend the life-span of power train; 3. vehicle starting is steady, accelerates rapid, even, soft; 4. the passing ability of vehicle is good.Current AT is the leading products of vehicular automatic transmission, but the major defect of AT be complicated mechanism, manufacture cost is high and transmission efficiency is low.Two, electric control mechanical type automatic speed variator (AMT.AutomatedManualTransmission), this speed changer is on the basis of original fixing shaft type speed-changing gear box, the maneuvering and control automation of block selecting, gearshift, clutch and engine throttle, its advantage is: 1. transmission efficiency is high; 2. the simple cost of structure is low; 3. production inheritance with great difficulty manufactures.AMT is an important development direction of automatic Transmissions Technique, but AMT is due to the restriction by fuel consumption and emission regulation, so development is subject to certain restrictions.Three, mechanical continuously-variable transmission (CVT.ContunuouslyVariableTransmission), this speed changer overcomes the shortcoming that the intrinsic gear ratio of first two automatic transmission is discontinuous and number of spare parts is too much, but because CVT is friction driving, so cause efficiency low, the driving belt used or chain manufacturing technology are difficult, requirement on machining accuracy is higher, the material used requires higher, and maintenance is difficulty especially.Four, double-clutch automatic transmission (DCT.DoubleClutchTransmission), this clutch have employed two clutches, two clutches are connected with two input shafts respectively, its main feature is in shift process, the power of motor is constantly passed to wheel all the time, and such shift process is power gear shifting, and vehicle achieves power gear shifting, great raising shifting comfort, but it is not enough also to there is the low grade of transmission efficiency.
Summary of the invention
For solving above technical problem, the object of the present invention is to provide the reverse-flow type hydrodynamic mechanical automatic variable transmission device that a kind of transmission efficiency is high, power loss is little.
The present invention seeks to realize like this: a kind of reverse-flow type hydrodynamic mechanical automatic variable transmission device, its main points are: comprise input shaft, jack shaft, planet row and fluid torque converter, wherein said planet row comprises planet carrier, sun gear and gear ring, described fluid torque converter comprises pump impeller and turbine, described jack shaft one end is connected with described input shaft, the other end is connected with described planet carrier, and described sun gear is connected with described pump impeller, and described turbine and described input shaft are connected.
Adopt above structure, make full use of the effect of fluid torque converter low speed torque increasing, adopt fluid torque converter starting, and after automobile speed reaches a certain value locking torque converter, make hydrodynamic mechanical transmission become pure mechanical transmission, eliminate fluid torque converter average efficiency defect on the low side with this.Simultaneously, the characteristic of the shunting utilizing planet row intrinsic/interflow power and velocity composite, fluid torque converter is inverted in return flow path significantly to reduce power loss, and pass through the omnidistance stepless change of the whole speed variator system of continuous speed adjustment functional realiey of fluid torque converter, the characteristic utilizing power to reflux continues the effect retaining whole variable ratio drive system low speed torque increasing, reaches the objects such as transmission efficiency is high, power loss is little.
As preferably: described input shaft and jack shaft be arranged in parallel, wherein input shaft is set with transition driven gear, described jack shaft is installed with transition driving gear, described transition driving gear engages with transition driven gear, the sun gear empty set of described planet row is on described input shaft, the planet carrier of this planet row is connected with described transition driven gear, and described turbine is positioned at the right side of described planet row.Adopt above structure, the reasonable installation of each parts can be realized, transition driving gear achieves power from input shaft to the transmission of jack shaft with engaging of transition driven gear, the power of motor passes to jack shaft by input shaft, jack shaft utilizes the effect of planet row power dividing, the power transmitted through planet carrier is most of via gear ring, then is passed to differential mechanism, output axle shaft and tire to drive automobile running by gear ring; All the other engine powers are passed to the pump impeller of fluid torque converter via sun gear, and after bending moment, be passed to turbine by the working solution of fluid torque converter, because turbine and input shaft are connected, thus form power backflow composition backflow speed governing path, so decrease the loss of power, reach energy-conservation object.
As preferably: be set with primary speed-down driving gear on described input shaft, primary speed-down axle is installed with primary speed-down driven gear, this primary speed-down driven gear and the engagement of primary speed-down driving gear, described primary speed-down axle is installed with main deceleration driving gear, main deboost axle is installed with main reduction driven gear, this main reduction driven gear and the engagement of main deceleration driving gear, described primary speed-down axle, main deboost axle and input shaft be arranged in parallel.Adopt above structure, can be good at outputing power, transmission of power is given the primary speed-down driving gear be connected with it by gear ring, and is passed to differential mechanism, output axle shaft and tire to drive automobile running by primary speed-down driven gear, main deceleration driving gear, main reduction driven gear.
As preferably: be set with C on described input shaft
1/ C
rgear clutch, C
2/ C
3gear clutch and C
4/ C
5gear clutch, wherein C
1/ C
rgear clutch, C
2/ C
3gear clutch and C
4/ C
5the driving disc of gear clutch is solidly set on described input shaft, at described C
1/ C
rdescribed input shaft on the left of gear clutch is set with a gear driven gear, this gear driven gear and a described C
1/ C
rdriven disc on the left of gear clutch is connected, at described C
2/ C
3gear the clutch left and right sides described input shaft on be set with three gear driven gears and two gear driven gears, this three gear driven gear and two gear driven gears respectively with described C
2/ C
3the driven disc of the gear clutch left and right sides is connected, at described C
4/ C
5the described input shaft of the gear clutch left and right sides is set with five gear driven gears and four gear driven gears, this five gear driven gear and four gear driven gears are respectively and C
4/ C
5the driven disc of the gear clutch left and right sides is connected; Described jack shaft is installed with a gear driving gear, two gear driving gears, three gear driving gears, four gear driving gears, five gear driving gears, a wherein said gear driving gear and a gear driven gear engagement, described two gear driving gears and two gear driven gear engagements, described three gear driving gears and three gear driven gear engagements, described four gear driving gears and described four gear driven gear engagements, described five gear driving gears and described five gear driven gear engagements.Adopt above structure, the joint of each gear clutch, segmentation speed governing of the present invention can be realized, wherein, planet carrier is as power intake, and gear ring is then clutch end, sun gear then with the pump impeller of fluid torque converter, and the transmission of power shunting out by sun gear by the working solution of fluid torque converter after bending moment is to turbine, final turbine will shunt transmission of power reversion carrier, thus form backflow arrangements for speed regulation; Fluid torque converter does not directly transmit the driving force of the driving wheels travel that motor sends, but be on backflow branch road that the sun gear of planet row and planet carrier form, its Main Function is the feature of speed ratio consecutive variations by fluid torque converter and planet row velocity composite, the speed ratio realized between motor input speed and clutch end gear ring output speed regulates continuously, thus achieves stepless time adjustment of the present invention; As underneath drive efficiency parts, fluid torque converter is in backflow branch road, and the driving power of transmission significantly reduces with the increase of planet row structural parameter a, thus can significantly improve transmission efficiency of the present invention.
As preferably: at described C
1/ C
ron described input shaft on the right side of gear clutch, empty set is reversed gear driven gear, this reverse gear driven gear and described C
1/ C
rdriven disc on the right side of gear clutch is connected, described jack shaft is installed with the driving gear that reverses gear, also be provided with the reverse gear shaft parallel with described input shaft, this reverse gear shaft is installed with the speed change intermediate idler that reverses gear, this speed change intermediate idler that reverses gear engages with the driving gear that reverses gear with the described driven gear that reverses gear, and described pump impeller is connected with the break that reverses gear.Adopt above structure, gear reversing function of the present invention can be realized, particularly, to reverse gear break locking, engine output power keeps off solenoidoperated cluthes through input shaft by the C1/CR of gear speed transmission, speed change of reversing gear driving gear, speed change of reversing gear intermediate idler, speed change of reversing gear driven gear, transition driving gear, transition driven gear are connected with the planet carrier of planet row, again through gear ring outputting power, reverse gear so achieve.
As preferably: described fluid torque converter also comprises one-level guide wheel and secondary guide wheel, this one-level guide wheel is connected with one-way element outer ring respectively with secondary guide wheel, one-way element inner ring is connected with torque converter housing, adopts above structure can realize the installation of fluid torque converter reliably.
Beneficial effect: compared with existing Hydraulic Automatic Transmission System, fluid torque converter of the present invention is in backflow branch road and is inverted, gear speed transmission is then in initial status, because the greatest differences of structure composition and speed adjusting mechanism causes its performance to occur significant change, with regard to power backflow, existing technology is thought can increase manufacture cost, namely be need transmission shaft overstriking etc. just can bear larger torque, so do not consider that power refluxes the enormous benefits brought, as with regard to some heavy machineries, its driving mechanism natively can bear very large torque, therefore this transmission device is adopted can to bring larger benefit, and effect of the present invention also has other notable features:
1, fluid torque converter of the present invention is not in engine power and drives and transmit road through upper, but (what be namely connected with input shaft is the turbine of fluid torque converter, and is positioned on power backflow speed governing path to adopt torque-converters instead to fill.Because backflow power is only 1/ (1+a) size (when torque-converters speed ratio is 1) of input power, wherein a is planet row structure parameter, equals the gear ring number of teeth of planet row and the ratio of the sun gear number of teeth.Although the transmission efficiency η of fluid torque converter own
yconstant, but concerning whole return flow type Hydraulic Automatic Transmission System, ignoring under gear-driven efficiency damaed cordition, its transmission efficiency is (η
y+ a)/(1+a), can obtain and improve significantly.
For two guide wheels four element fluid torque converter that efficient district is relatively wide: setting gear speed transmission gear-driven efficiency η
kbe 98%, as torque-converters speed ratio i
ybe 0.9, efficiency eta
ywhen being 80%, the transmission efficiency η of backflow transmission system
systo reach 93.41%, this improves nearly 15% than the efficiency (98% × 80%=78.4%) of the common Hydraulic Automatic Transmission System be not under blocking; As torque-converters speed ratio i
ybe 0.8, efficiency eta
ywhen being 92%, the transmission efficiency η of backflow transmission system
systo 95.53% be reached.As can be seen here, the present invention has obvious using value for the engineering vehicle such as loader, bulldozer of fluid torque converter not locking and special military vehicle.
But, the present invention also possesses the feature of omnidistance stepless speed regulation simultaneously, shunt compared with transmission system with have grade gear hydraulic machine variable ratio drive system and Hydro-mechanical after converter lockout, motor can be controlled preferably and be in more desirable area operation, improve the fuel utilization ratio of automobile, thus effectively compensate for a certain extent because of transmission efficiency relatively on the low side with energy loss.
2, the significantly improving of transmission efficiency of the present invention, the not locking of fluid torque converter whole process.Make full use of higher efficiency area and the function of stepless speed regulation thereof of fluid torque converter body, realize the staged investment of whole transmission system, again by there being the rational gear of grade gear speed transmission to arrange, finally realize the omnidistance stepless shift function of return flow type Hydraulic Automatic Transmission System.Wherein, the speed ratio of gear speed transmission must meet: by the determined efficient region of fluid torque converter, the minimum value of speed ratio determined backflow transmission system speed ratio is kept off by gear speed transmission n, equal with the maximum value of being kept off speed ratio determined backflow transmission system speed ratio by n+1; The maximum value of transmission system speed ratio is then ensured by the speed ratio of primary speed-down gear pair and main speed reducing gear pair; The speed ratio excursion that the gear number of gear speed transmission is proposed by target design object is determined.
3, speed ratio change control in, stepless speed regulation process of the present invention be by gear speed transmission have level shift gears and backflow speed regulating mechanism stepless change dimerous.Wherein, what the shift transformation of gear speed transmission adopted is the active mode of power gear shifting; What the stepless change of backflow speed regulating mechanism adopted is the passive autonomous mode of speed regulation of fluid torque converter.
4, in Vehicle Starting Process, the gear ring of planet row is in static or low speed state, and the moment transmitted by planet carrier determined by its output torque.Because comprising the existence of the circulating power of fluid torque converter, the output torque of gear ring will sharply increase, and the amplification of gear ring output torque is controlled by gear solenoidoperated cluthes, while the whole speed variator system low speed torque increasing effect of reservation, guarantee Security and the smoothness of whole transmission system.
In sum: the present invention is on the basis remaining hydraulic machine automatic speed changing transmission AT system low speed torque increasing characteristic, its transmission efficiency will far above the AT drive system efficiency before lockup clutch locking, and by the feature of stepless speed regulation, compensate for a certain extent with locking after AT system and Hydro-mechanical shunt transmission system existing gap in car load fuel consumption.
Accompanying drawing explanation
Fig. 1 is schematic diagram of the present invention;
Fig. 2 is transmission operation schematic diagram of the present invention.
In figure: 1-input shaft; 2-five gear driven gears; 3-five gear driving gears; 4-jack shaft; 5-four gear driving gears; 6-three gear driving gears; 7-two gear driving gears; 8-one gear driving gear; 9-reverse gear driving gear; 10-speed change of reversing gear intermediate idler; 11-transition driving gear; 12-gear ring; 13-primary speed-down driving gear; 14-turbine; 15-one-level guide wheel; 16-secondary guide wheel; 17-pump impeller; 18-reverse gear break; 19-primary speed-down driven gear; 20-main reduction driven gear; 21-main deceleration driving gear; 22-planet carrier; 23-sun gear; 24-transition driven gear; 25-reverse gear driven gear; 26-C
1/ C
rgear clutch; 27-one gear driven gear; 28-two gear driven gears 28; 29-C
2/ C
3gear clutch; 30-three gear driven gears; 31-four gear driven gears; 32-C
4/ C
5gear clutch.
In figure: i
1 ~ 5-1 ~ 5 gear speed ratios; i
r-reverse gear speed ratio; P-pump impeller; W-turbine; D
1, D
2-guide wheel; B
r-reverse gear break; i
0-transition gear speed ratio.
Embodiment
Below in conjunction with drawings and Examples, the invention will be further described:
As depicted in figs. 1 and 2: a kind of reverse-flow type hydrodynamic mechanical automatic variable transmission device, comprise input shaft 1, jack shaft 4, planet row and fluid torque converter, wherein said planet row comprises planet carrier 22, sun gear 23 and gear ring 12, described fluid torque converter comprises pump impeller 17 and turbine 14, described jack shaft 4 one end is connected with described input shaft 1, the other end is connected with described planet carrier 22, described sun gear 23 is connected with described pump impeller 17, described turbine 14 is connected with described input shaft 1, described input shaft 1 and jack shaft 4 be arranged in parallel, wherein input shaft 1 is set with transition driven gear 24, described jack shaft 4 is installed with transition driving gear 11, described transition driving gear 11 engages with transition driven gear 24, sun gear 23 empty set of described planet row is on described input shaft 1, the planet carrier 22 of this planet row is connected with described transition driven gear 24, described turbine 14 is positioned at the right side of described planet row, described fluid torque converter also comprises one-level guide wheel 15 and secondary guide wheel 16, this one-level guide wheel 15 is not connected with one-way element outer ring with secondary guide wheel 16 is dutiful, one-way element inner ring is connected with torque converter housing, described input shaft 1 is set with primary speed-down driving gear 13, primary speed-down axle is installed with primary speed-down driven gear 19, this primary speed-down driven gear 19 and primary speed-down driving gear 13 engage, described primary speed-down axle is installed with main deceleration driving gear 21, main deboost axle is installed with main reduction driven gear 20, this main reduction driven gear 20 and main deceleration driving gear 21 engage, described primary speed-down axle, main deboost axle and input shaft 1 be arranged in parallel.
It can also be seen that in FIG: on described input shaft 1, be set with C
1/ C
rgear clutch 26, C
2/ C
3gear clutch 29 and C
4/ C
5gear clutch 32, wherein C
1/ C
rgear clutch 26, C
2/ C
3gear clutch 29 and C
4/ C
5the driving disc of gear clutch 32 is solidly set on described input shaft 1, at described C
1/ C
rdescribed input shaft 1 on the left of gear clutch 26 is set with a gear driven gear 27, this gear driven gear 27 and described C
1/ C
rdriven disc on the left of gear clutch 26 is connected, at described C
2/ C
3the described input shaft 1 of gear clutch 29 left and right sides is set with three gear driven gears 30 and two gear driven gears 28, this three gears driven gear 30 and two gear driven gears 28 respectively with described C
2/ C
3the driven disc of gear clutch 29 left and right sides is connected, at described C
4/ C
5the described input shaft 1 of gear clutch 32 left and right sides is set with five gear driven gears 2 and four gear driven gears 31, this five gears driven gear 2 and four gear driven gears 31 are respectively and C
4/ C
5the driven disc of gear clutch 32 left and right sides is connected; Described jack shaft 4 is installed with a gear driving gear 8, two and keeps off driving gear 7, three gear driving gear 6, four gear driving gear 5, five gear driving gear 3, a wherein said gear driving gear 8 and a gear driven gear 27 engage, described two gear driving gears 7 and two gear driven gears 28 engage, described three gear driving gears 6 and three gear driven gears 30 engage, described four gear driving gears 5 and described four gear driven gears 31 engage, and described five gear driving gears 3 and described five gear driven gears 2 engage; At described C
1/ C
ron described input shaft 1 on the left of gear clutch 26, empty set is reversed gear driven gear 25, this reverse gear driven gear 25 and described C
1/ C
rdriven disc on the right side of gear clutch 26 is connected, described jack shaft 4 is installed with the driving gear 9 that reverses gear, also be provided with the reverse gear shaft parallel with described input shaft 1, this reverse gear shaft is installed with the speed change intermediate idler 10 that reverses gear, this speed change intermediate idler 10 that reverses gear engages with the driving gear 9 that reverses gear with the described driven gear 25 that reverses gear, and described pump impeller 17 is connected with the break 18 that reverses gear.It should be noted that: above-mentioned C
1/ C
rgear clutch 26, C
2/ C
3gear clutch 29 and C
4/ C
5gear clutch 32 is middle driving disc and is solidly set on described input shaft 1, and driving disc both sides are driven disc, and the clutch of driving disc and driven disc can realize C
1/ C
rgear clutch 26, C
2/ C
3gear clutch 29 and C
4/ C
5the clutch of gear clutch 32.
The power flow of equipment vehicle of the present invention under various driving cycle is explained:
1, start to walk operating mode
Engine start, C
1/ C
rcombine on the left of gear clutch 26, be now in a gear working state.Because now vehicle remains static, the toothrow circle 12 of planet is equivalent to lockup state.Now the flow process of power is: motor → input shaft 1 → C
1/ C
rgear clutch 26 → keeps off driven gear 27 → and keeps off driving gear 8 → transition driving gear 11 → transition driven gear 24 → planet carrier 22 → sun gear 23 → pump impeller 17 → turbine 14 → input shaft 1 ..., form a power return flow path thus.Along with the increasing of motor input power, act on moment of torsion on the gear ring 12 of planet row also in increase, and after first stage decelerator and main reducing gear increase and turn round, when it is greater than the resisting moment that vehicle applied by tire, vehicle starts starting;
2, operating mode is driven
When being in three gears for gear, now C
2/ C
3c in gear clutch 29
3gear engages, and driving power flow process of the present invention is: motor+turbine 14 → input shaft 1 → C
3gear solenoidoperated cluthes 29 → tri-keep off driven gear 30 → tri-and keep off driving gear 6 → transition driving gear 11 → transition driven gear 24 → planet carrier 22 → gear ring 12 → primary speed-down driving gear 13 → primary speed-down driven gear 19 → main deceleration driving gear 21 → main reduction driven gear 20 ... wheel.Through planet row power dividing, Partial Power passes input shaft 1 back, as the use of speed governing through sun gear 23, fluid torque converter.Backflow power transimission flow process is: ... planet carrier 22 → sun gear 23 → pump impeller 17 → turbine 14 → input shaft 1 ...The power flow of other gear is similar therewith, only need engage under different gear clutch just can make the present invention be in other gear and work;
3, astern condition
The break 18 that now reverses gear engages, and driving power flow process of the present invention is: motor → input shaft 1 → C
1/ C
rthe C of gear clutch
rkeep off → reverse gear that driven gear 25 → speed change of reversing gear intermediate idler 10 → reverse gear driving gear 9 → transition driving gear 11 → transition driven gear 24 → planet carrier 22 → gear ring 12 → primary speed-down driving gear 13 → primary speed-down driven gear 19 → main deceleration driving gear 21 → main reduction driven gear 20 ... wheel, thus realize reversing gear.
The above embodiment is only preferred embodiment of the present invention, is not restriction with the present invention, and all any amendments done within the spirit and principles in the present invention, equivalent replacement and improvement etc., all should be included within protection scope of the present invention.
Claims (3)
1. a reverse-flow type hydrodynamic mechanical automatic variable transmission device, it is characterized in that: comprise input shaft (1), jack shaft (4), planet row and fluid torque converter, wherein said planet row comprises planet carrier (22), sun gear (23) and gear ring (12), described fluid torque converter comprises pump impeller (17) and turbine (14), described jack shaft (4) one end is connected with described input shaft (1), the other end is connected with described planet carrier (22), described sun gear (23) is connected with described pump impeller (17), described turbine (14) and described input shaft (1) are connected,
Described input shaft (1) and jack shaft (4) be arranged in parallel, wherein input shaft (1) is set with transition driven gear (24), described jack shaft (4) is installed with transition driving gear (11), described transition driving gear (11) is engaged with transition driven gear (24), sun gear (23) empty set of described planet row is on described input shaft (1), the planet carrier (22) of this planet row is connected with described transition driven gear (24), and described turbine (14) is positioned at the right side of described planet row;
Described input shaft (1) is set with primary speed-down driving gear (13), primary speed-down axle is installed with primary speed-down driven gear (19), this primary speed-down driven gear (19) and primary speed-down driving gear (13) engagement, described primary speed-down axle is installed with main deceleration driving gear (21), main deboost axle is installed with main reduction driven gear (20), this main reduction driven gear (20) and main deceleration driving gear (21) engagement, described primary speed-down axle, main deboost axle and input shaft (1) be arranged in parallel;
Described input shaft (1) is set with C
1/ C
rgear clutch (26), C
2/ C
3gear clutch (29) and C
4/ C
5gear clutch (32), wherein C
1/ C
rgear clutch (26), C
2/ C
3gear clutch (29) and C
4/ C
5the driving disc of gear clutch (32) is solidly set on described input shaft (1), at described C
1/ C
rthe described input shaft (1) in gear clutch (26) left side is set with a gear driven gear (27), this gear driven gear (27) and described C
1/ C
rthe driven disc in gear clutch (26) left side is connected, at described C
2/ C
3gear clutch (29) left and right sides described input shaft (1) on be set with three gear driven gears (30) and two gear driven gear (28), this three gear driven gear (30) and two keep off driven gear (28) respectively with described C
2/ C
3the driven disc of gear clutch (29) left and right sides is connected, at described C
4/ C
5the described input shaft (1) of gear clutch (32) left and right sides is set with five gear driven gears (2) and four gears driven gear (31), this five gear driven gear (2) and four keeps off driven gear (31) respectively and C
4/ C
5the driven disc of gear clutch (32) left and right sides is connected, described jack shaft (4) is installed with a gear driving gear (8), two gears driving gear (7), three gears driving gear (6), four gears driving gear (5), five gears driving gear (3), wherein said gear driving gear (8) and gear driven gear (27) engagement, described two gears driving gear (7) and two gear driven gear (28) engagements, described three gears driving gear (6) and three gear driven gear (30) engagements, described four gears driving gear (5) and described four gear driven gear (31) engagements, described five gears driving gear (3) and described five gear driven gear (2) engagements.
2. reverse-flow type hydrodynamic mechanical automatic variable transmission device according to claim 1, is characterized in that: at described C
1/ C
rthe upper empty set of described input shaft (1) on gear clutch (26) right side is reversed gear driven gear (25), this driven gear that reverses gear (25) and described C
1/ C
rthe driven disc on gear clutch (26) right side is connected, described jack shaft (4) is installed with the driving gear that reverses gear (9), also be provided with the reverse gear shaft parallel with described input shaft (1), this reverse gear shaft is installed with the speed change intermediate idler (10) that reverses gear, this speed change intermediate idler (10) that reverses gear engages with the described driven gear that reverses gear (25) and the driving gear that reverses gear (9), and described pump impeller (17) is connected with the break that reverses gear (18).
3. reverse-flow type hydrodynamic mechanical automatic variable transmission device according to claim 1, it is characterized in that: described fluid torque converter also comprises one-level guide wheel (15) and secondary guide wheel (16), this one-level guide wheel (15) is connected with one-way element outer ring respectively with secondary guide wheel (16), and one-way element inner ring is connected with torque converter housing.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310260071.0A CN103307248B (en) | 2013-06-26 | 2013-06-26 | Reverse-flow type hydrodynamic mechanical automatic variable transmission device |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310260071.0A CN103307248B (en) | 2013-06-26 | 2013-06-26 | Reverse-flow type hydrodynamic mechanical automatic variable transmission device |
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| CN103307248B true CN103307248B (en) | 2015-11-25 |
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|---|---|---|---|---|
| CN105650236A (en) * | 2014-05-07 | 2016-06-08 | 吴志强 | Compound double-guide-wheel type hydraulic torque converter |
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| DE1133419B (en) * | 1958-04-29 | 1962-07-19 | Voith Gmbh J M | Drive set with electric motor and hydromechanical gear, especially for rail vehicles |
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