CN103307248A - 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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- CN103307248A CN103307248A CN2013102600710A CN201310260071A CN103307248A CN 103307248 A CN103307248 A CN 103307248A CN 2013102600710 A CN2013102600710 A CN 2013102600710A CN 201310260071 A CN201310260071 A CN 201310260071A CN 103307248 A CN103307248 A CN 103307248A
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Abstract
The invention discloses a reverse-flow type hydrodynamic mechanical automatic variable transmission device. The variable transmission device comprises an input shaft, an intermediate shaft, a planetary line and a hydraulic torque converter, wherein the planetary line comprises a planet carrier, a sun gear and a gear ring; the hydraulic torque converter comprises a pump impeller and a turbine; one end of the intermediate shaft is connected with the input shaft, and the other end is connected with the planet carrier; the sun gear is connected with the pump impeller; the turbine is fixedly connected with the input shaft. The inherent shunting/converging power and rate combination property of the planetary line is utilized to reversely arrange the hydraulic torque converter in a reflow path to greatly lower power loss, the continuous speed adjustment function of the hydraulic torque converter is utilized to realize the whole-course stepless change of the whole variable-speed system, and the power reflow property is utilized to continually retain the low-speed torque boosting effect of the whole variable transmission system, so that the purposes of high transmission efficiency, low power loss and the like are achieved.
Description
Technical field
The invention belongs to the mechanical transmissioning technology field, specifically, relate to a kind of return flow type hydraulic machine automatic gear shift transmission device.
Background technique
The transmission device of a large amount of continuously variables that adopt mainly comprises metal tape/metal chain transmission and hydraulic machine gear dual mode on the automobile at present, the slowest ratio of regulation 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 guarantee more than 6 motor at the steady operation point under the different accelerator open degrees all the time in the best then on the economic line.With regard to metal tape/metal chain vari-speed drive, be subjected to the restriction of physical dimension, its speed ratio excursion is generally about 5.1, is lower than car speed variator system theoretical velocity ratio excursion.Satisfying under the prerequisite of car drive, in order to ensure the 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, the application for a patent for invention that name is called " return flow type stepless speed change driving device for automobile " discloses a kind of with the automative stepless speed-variation transmission device of metal tape as the 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 purpose is to overcome the existing problem that automative stepless speed-variation transmission device speed ratio excursion is partially narrow, transmission efficiency is on the low side.
With regard to the hydraulic machine gear: at present, the hydraulic machine transmission is used in driveline of construction machines widely, and the transmission efficiency that improves power train is very important.Known hydraulic machine transmission is that fluid torque converter, speed-changing gear box, main transmission and whole transmission form, take full advantage of the effect of fluid torque converter low speed torque increasing, the starting of employing fluid torque converter, and after automobile speed reaches a certain value locking torque converter, make hydrodynamic mechanical transmission become pure mechanical transmission, eliminate torque-converters average efficiency defective on the low side with this; The major defect of this transmission is because torque converter is low and become parabolic shape, the efficient increase of starting from scratch when low speed is vehicle launch than operating mode, usually reaching 75% thinks and enters efficient district, beginning to descend to enter by best efficiency point begins at a high speed rapid decline than the time, the absolute zero load is that efficient is zero.
Particularly, various types of automatic transmission case such as AT, AMT, CVT, DCT have appearred, and one, hydraulic automatic speed variator (AT.Automatic Transmission), 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 its stepless change with certain limit and bending moment ability, and external loading is had automatic adjusting and conformability, has fundamentally simplified operation; 2. hydraudynamic drive itself has certain damping performance, can effectively reduce spike load and the rotational-torsional of power train, has prolonged the life-span of power train; 3. vehicle starting is steady, accelerates rapid, even, soft; 4. the passing ability of vehicle is good.AT is the leading products of vehicular automatic transmission at present, but the major defect of AT is that complicated mechanism, manufacture cost are high and transmission efficiency is low.
Two, electric control mechanical type automatic speed variator (AMT.Automated Manual Transmission), this speed changer is on the basis of original fixedly shaft type speed-changing gear box, the manipulation auto-control of block selecting, gearshift, clutch and engine throttle, its advantage is: 1. transmission efficiency is high; 2. cost simple in structure is low; 3. production inheritance is with great difficulty made.AMT is an important development direction of automatic Transmissions Technique, but AMT is subject to certain restrictions so develop owing to being subjected to the restriction of fuel consumption and emission rules.Three, mechanical continuously-variable transmission (CVT.Contunuously Variable Transmission), this speed changer has overcome the discontinuous and too much shortcoming of number of spare parts of the intrinsic gear ratio of front two kinds of automatic transmission, but because CVT is friction driving, so cause efficient low, employed driving belt or chain manufacturing technology are difficult, requirement on machining accuracy is higher, the material of using requires higher, and maintenance is difficulty especially.Four, double-clutch automatic transmission (DCT.Double Clutch Transmission), this clutch has adopted two clutches, two clutches are connected with two input shafts respectively, its main feature is in shift process, the power of motor constantly is passed to wheel all the time, and such shift process is power gear shifting, and vehicle has been realized power gear shifting, still also there is the low deficiency that waits of transmission efficiency in the great shifting comfort that improves.
Summary of the invention
For solving above technical problem, the object of the present invention is to provide the return flow type hydraulic machine automatic gear shift 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 return flow type hydraulic machine automatic gear shift 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 links to each other with described pump impeller, and described turbine and described input shaft are connected.
Adopt above structure, take full advantage of the effect of fluid torque converter low speed torque increasing, adopt the 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 defective on the low side with this.Simultaneously, utilize the synthetic characteristic of the intrinsic shunting of planet row/interflow power and speed, fluid torque converter is inverted in return flow path significantly to reduce power loss, and realize the omnidistance stepless change of whole speed variator system by the continuous speed adjustment function of fluid torque converter, the characteristic of utilizing power to reflux continues to keep the effect of whole variable ratio drive system low speed torque increasing, has reached the purposes such as transmission efficiency is high, power loss is little.
As preferably: described input shaft and jack shaft be arranged in parallel, wherein be set with the transition driven gear on the input shaft, be installed with the transition driving gear on the described jack shaft, described transition driving gear and the engagement of 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, can realize the reasonable installation of each parts, the engagement of transition driving gear and transition driven gear has realized the transmission of power from input shaft to jack shaft, the power of motor passes to jack shaft by input shaft, jack shaft utilizes the effect of planet row power dividing, the power major part of transmitting through planet carrier is passed to differential mechanism, output axle shaft and tire to drive automobile running by gear ring again via gear ring; All the other engine powers are passed to the pump impeller of fluid torque converter via sun gear, and behind bending moment, be passed to turbine by the working solution of fluid torque converter, because turbine and input shaft are connected, reflux and form backflow speed governing path thereby consist of power, so reduced the loss of power, reached energy-conservation purpose.
As preferably: be set with the primary speed-down driving gear at described input shaft, be installed with the primary speed-down driven gear at the primary speed-down axle, this primary speed-down driven gear and the engagement of primary speed-down driving gear, be installed with main deceleration driving gear on the described primary speed-down axle, be installed with main deceleration driven gear at main deboost axle, this main deceleration 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, the primary speed-down driving gear that is connected with it given transmission of power 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 deceleration driven gear.
As preferably: be set with C at 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 the described input shaft, at described C
1/ C
RBe set with a gear driven gear on the described input shaft in gear clutch left side, this gear driven gear and a described C
1/ C
RThe driven disc in gear clutch left side is connected, at described C
2/ C
3Be set with three gear driven gears and two gear driven gears on the described input shaft of the gear clutch left and right sides, 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
5Be set with five gear driven gears and four gear driven gears on the described input shaft of the gear clutch left and right sides, this five gear driven gear and four keeps off driven gears respectively and C
4/ C
5The driven disc of the gear clutch left and right sides is connected; Be installed with a gear driving gear, two gear driving gears, three gear driving gears, four gear driving gears, five gear driving gears at described jack shaft, 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, can realize segmentation speed governing of the present invention, wherein, planet carrier is as power intake, and gear ring then is clutch end, sun gear then with the pump impeller of fluid torque converter, and the transmission of power of sun gear being shunted out by the working solution of fluid torque converter behind bending moment is to turbine, and final turbine will shunt transmission of power and return planet carrier, thus formation backflow arrangements for speed regulation; Fluid torque converter does not directly transmit the driving force that driving wheel that motor sends travels, but be on the sun gear of planet row and the backflow branch road that planet carrier consists of, its Main Function is the characteristics that speed ratio changes continuously and planet row speed is synthetic by fluid torque converter, speed ratio between realization motor input speed and the clutch end gear ring output speed is regulated continuously, thereby has realized stepless time adjustment of the present invention; As underneath drive efficient parts, fluid torque converter is in the backflow branch road, and the driving power of transmission is decrease with the increase of planet row structural parameter a, thereby can significantly improve transmission efficiency of the present invention.
As preferably: at described C
1/ C
RThe empty set driven gear that reverses gear on the described input shaft in gear clutch left side, this reverse gear driven gear and described C
1/ C
RThe driven disc on gear clutch right side is connected, be installed with the driving gear that reverses gear at described jack shaft, also be provided with the reverse gear shaft parallel with described input shaft, idle pulley in the middle of this reverse gear shaft is installed with the speed change of reversing gear, idle pulley and described reverse gear driven gear and the driving gear engagement of reversing gear in the middle of this speed change of reversing gear, described pump impeller is connected with the break that reverses gear.Adopt above structure, can realize gear reversing function of the present invention, particularly, the break locking of reversing gear, engine output power links to each other with the planet carrier of planet row through C1/CR gear solenoidoperated cluthes, the speed change of reversing gear driving gear, the middle idle pulley of the speed change of reversing gear, the speed change of reversing gear driven gear, transition driving gear, the transition driven gear of input shaft by gear speed transmission, again through the gear ring outputting power, so realized reversing gear.
As preferably: described fluid torque converter also comprises one-level guide wheel and secondary guide wheel, this one-level guide wheel is connected with the one-way element outer ring with the secondary guide wheel and is connected, the one-way element inner ring is connected with torque converter housing, adopts above structure can realize reliably the installation of fluid torque converter.
Beneficial effect: compare with existing Hydraulic Automatic Transmission System, fluid torque converter of the present invention is in the backflow branch road and is inverted, gear speed transmission then is in initial status, because structure forms and the greatest differences of speed adjusting mechanism causes its performance significant variation to occur, with regard to power refluxes, existing technology is thought can increase manufacture cost, namely be transmission shaft overstriking etc. just can need to be born larger torque, so do not consider the enormous benefits that power refluxes and brings, as with regard to some heavy machineries, its driving mechanism just can bear very large torque originally, therefore adopt this transmission device can 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 drive transmits the road through upper, and (what namely link to each other with input shaft is the turbine of fluid torque converter, and is positioned on the power backflow speed governing path but adopt that torque-converters is counter and fill.Because backflow power only is 1/ (1+a) of input power size (be 1 o'clock at the torque-converters speed ratio), wherein a is the planet row structure parameter, equals the ratio of the gear ring number of teeth with the sun gear number of teeth of planet row.Although the transmission efficiency η of fluid torque converter own
yConstant, but concerning whole return flow type Hydraulic Automatic Transmission System, ignoring under the gear-driven efficiency damaed cordition, its transmission efficiency is (η
y+ a)/(1+a), can obtain to improve significantly.
The two guide wheels four element fluid torque converters relatively wide take efficient district are as example: set 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%, (98% * 80%=78.4%) improves nearly 15% than the efficient that is not in the common Hydraulic Automatic Transmission System under the blocking for this; As torque-converters speed ratio i
yBe 0.8, efficiency eta
yWhen being 92%, the transmission efficiency η of backflow transmission system
SysTo reach 95.53%.This shows, the present invention has obvious using value for the engineering vehicles such as the loader of not locking of fluid torque converter, bulldozer and special military vehicle.
But, the present invention also possesses the characteristics of omnidistance stepless speed regulation simultaneously, compare with have grade gear hydraulic machine variable ratio drive system and fluid power-machinery shunting transmission system behind the converter lockout, control engine is in more desirable area operation preferably, improve the fuel utilization ratio of automobile, thus effectively compensated to a certain extent because of transmission efficiency relatively on the low side with energy loss.
2, significantly improving of transmission efficiency of the present invention, the not locking of fluid torque converter whole process.Take full advantage of higher efficiency area and the function of stepless speed regulation thereof of fluid torque converter body, realize the segmentation stepless speed regulation of whole transmission system, by the rational gear setting of grade gear speed transmission is arranged, finally realize the omnidistance stepless shift function of return flow type Hydraulic Automatic Transmission System again.Wherein, the speed ratio of gear speed transmission must satisfy: in the determined efficient region by fluid torque converter, by the minimum value of the determined backflow transmission system of gear speed transmission n gear speed ratio speed ratio, equate with the maximum value of being kept off the determined backflow transmission system of speed ratio speed ratio by n+1; The maximum value of transmission system speed ratio is then guaranteed by the speed ratio of primary speed-down gear pair and main speed reducing gear pair; The gear number of gear speed transmission is determined by the speed ratio excursion that the target design object proposes.
3, aspect speed ratio variation control, stepless speed regulation process of the present invention is dimerous by the stepless change that level gearshift and backflow speed regulating mechanism are arranged of gear speed transmission.What wherein, 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 was adopted is the passive autonomous mode of speed regulation of fluid torque converter.
4, in the Vehicle Starting Process, the gear ring of planet row is in static or low speed state, and its output torque will be determined by the moment of planet carrier transmission.Because comprising fluid torque converter in the existence of interior circulating power, the output torque of gear ring will sharply increase, and control the amplification of gear ring output torque by gear solenoidoperated cluthes, when keeping whole speed variator system low speed torque increasing effect, guarantee Security and the smoothness of whole transmission system.
In sum: the present invention is on the basis that has kept hydraulic machine automatic speed changing transmission AT system low speed torque increasing characteristic, its transmission efficiency will be far above the AT drive system efficient before the lockup clutch locking, and the characteristics by stepless speed regulation, remedied to a certain extent with locking after AT system and fluid power-machinery shunting transmission system existing gap on the car load fuel consumption.
Description of drawings
Fig. 1 is schematic diagram of the present invention;
Fig. 2 is transmission device fundamental diagram of the present invention.
Among the figure: 1-input shaft; 2-five gear speed change driving gears; 3-five gear speed change driven gears; 4-jack shaft; 5-four-speed gear shift driven gear; 6-three gear speed change driven gears; 7-two gear speed change driven gears; 8-one gear speed change driven gear; 9-the speed change of reversing gear driven gear; Idle pulley in the middle of the 10-speed change of reversing gear; 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-break reverses gear; 19-primary speed-down driven gear; 20-main deceleration driven gear; 21-main deceleration driving gear; 22-planet carrier; 23-sun gear; 24-transition driven gear; 25-the speed change of reversing gear driving gear; 26-C
1/ C
RThe gear clutch; 27-one gear speed change driving gear; 28-two gear speed change driving gears 28; 29-C
2/ C
3The gear clutch; 30-three gear speed change driving gears; 31-four-speed gear shift driving gear; 32-C
4/ C
5The gear clutch.
Among the figure: i
1～5-1～5 gear speed ratios; i
R-speed ratio reverses gear; P-pump impeller; W-turbine; D
1, D
2-guide wheel; B
R-break reverses gear; i
0-transition gear speed ratio.
Embodiment
The invention will be further described below in conjunction with drawings and Examples:
As depicted in figs. 1 and 2: a kind of return flow type hydraulic machine automatic gear shift 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 ends are connected with described input shaft 1, the other end is connected with described planet carrier 22, described sun gear 23 links to each other 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 be set with transition driven gear 24 on the input shaft 1, be installed with transition driving gear 11 on the described jack shaft 4, described transition driving gear 11 and 24 engagements of transition driven gear, sun gear 23 empty sets of described planet row are 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 connected with the secondary guide wheel and dutifully is not connected with the one-way element outer ring, the one-way element inner ring is connected with torque converter housing, be set with primary speed-down driving gear 13 at described input shaft 1, be installed with primary speed-down driven gear 19 at the primary speed-down axle, this primary speed-down driven gear 19 and 13 engagements of primary speed-down driving gear, be installed with main deceleration driving gear 21 on the described primary speed-down axle, be installed with main deceleration driven gear 20 at main deboost axle, this main deceleration driven gear 20 and 21 engagements of main deceleration driving gear, described primary speed-down axle, main deboost axle and input shaft 1 be arranged in parallel.
In Fig. 1, it can also be seen that: be set with C at described input shaft 1
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 the described input shaft 1, at described C
1/ C
RBe set with a gear driven gear 27 on the described input shaft 1 in gear clutch 26 left sides, this gear driven gear 27 and described C
1/ C
RThe driven disc in gear clutch 26 left sides is connected, at described C
2/ C
3Be set with three gear driven gears 30 and two gear driven gears 28 on the described input shaft 1 of gear clutch 29 left and right sides, this three gear 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
5Be set with five gear driven gears 1 and four gear driven gears 31 on the described input shaft 1 of gear clutch 32 left and right sides, this five gear driven gear 1 and four keeps off driven gears 31 respectively and C
4/ C
5The driven disc of gear clutch 32 left and right sides is connected; Be installed with a gear driving gear 8, two gear driving gears 7, three gear driving gears 6, four gear driving gears 5, five gear driving gears 3 at described jack shaft 4, a wherein said gear driving gear 8 and a gear driven gear 27 engagements, described two gear driving gears 7 and 28 engagements of two gear driven gears, described three gear driving gears 6 and 30 engagements of three gear driven gears, described four gear driving gears 5 and 31 engagements of described four gear driven gears, described five gear driving gears 3 and 1 engagement of described five gear driven gears; At described C
1/ C
RThe empty set driven gear 24 that reverses gear on the described input shaft 1 in gear clutch 26 left sides, this reverse gear driven gear 24 and described C
1/ C
RThe driven disc on gear clutch 26 right sides is connected, be installed with the driving gear 9 that reverses gear at described jack shaft 4, also be provided with the reverse gear shaft parallel with described input shaft 1, idle pulley 10 in the middle of this reverse gear shaft is installed with the speed change of reversing gear, idle pulley 10 and described reverse gear driven gear 24 and driving gear 9 engagements of reversing gear in the middle of this speed change of reversing gear, described pump impeller 17 is connected with the break 18 that reverses gear.Need to prove: above-mentioned C
1/ C
RGear clutch 26, C
2/ C
3Gear clutch 29 and C
4/ C
5Driving disc in the middle of gear clutch 32 is is solidly set on the described input shaft 1, and the 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.
Explain equipping the power flow of vehicle of the present invention under various driving cycles:
1, starting operating mode
Engine start, C
1/ C
RThe 26 left side combinations of gear clutch are in a gear working state this moment.Therefore vehicle remains static the time, and the toothrow circle 12 of planet is equivalent to lockup state.This moment, the flow process of power was: motor → input shaft 1 → C
1/ C
RGear clutch 26 → one gear speed change driving gears 27 → one gear speed change driven gears 8 → transition driving gear 11 → transition driven gear 24 → planet carrier 22 → sun gear 23 → pump impeller 17 → turbine 14 → input shaft 1 ..., consist of thus a power return flow path.Along with the increasing of motor input power, the moment of torsion that acts on the gear ring 12 of planet row is also increasing, and through first stage decelerator and main reducing gear increase turn round after, when resisting moment that it applies by tire greater than vehicle, vehicle begins starting;
2, drive operating mode
Be in for 3 whens gear as example take gear, this moment C
2/ C
3C in the 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 → three gear speed change driving gears 30 → three gear speed change driven gears 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 deceleration driven gear 20 ... wheel.Through the planet row power dividing, Partial Power is passed input shaft 1 back through sun gear 23, fluid torque converter, as the usefulness of speed governing.Backflow power conveying flow 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 needs the different gear clutches of joint that the present invention is under other gear and works;
3, astern condition
The break 18 that reverses gear this moment 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 the middle idle pulley 10 of the speed change driving gear 25 → speed change of the reversing gear → speed change of reversing gear driven 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 deceleration driven gear 20 ... wheel, thus realize reversing gear.
The above embodiment only is preferred embodiment of the present invention, not take the present invention as restriction, all any modifications of doing within the spirit and principles in the present invention, is equal to and replaces and improvement etc., all should be included within protection scope of the present invention.
Claims (6)
1. return flow type hydraulic machine automatic gear shift 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 ends are connected with described input shaft (1), the other end is connected with described planet carrier (22), described sun gear (23) links to each other with described pump impeller (17), and described turbine (14) is connected with described input shaft (1).
2. return flow type hydraulic machine automatic gear shift transmission device according to claim 1, it is characterized in that: described input shaft (1) and jack shaft (4) be arranged in parallel, wherein be set with transition driven gear (24) on the input shaft (1), be installed with transition driving gear (11) on the described jack shaft (4), described transition driving gear (11) and transition driven gear (24) engagement, the sun gear of described planet row (23) empty set is on described input shaft (1), the planet carrier of this planet row (22) is connected with described transition driven gear (24), and described turbine (14) is positioned at the right side of described planet row.
3. return flow type hydraulic machine automatic gear shift transmission device according to claim 2, it is characterized in that: be set with primary speed-down driving gear (13) at described input shaft (1), be installed with primary speed-down driven gear (19) at the primary speed-down axle, this primary speed-down driven gear (19) and primary speed-down driving gear (13) engagement, be installed with main deceleration driving gear (21) on the described primary speed-down axle, be installed with main deceleration driven gear (20) at main deboost axle, this main deceleration 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.
4. it is characterized in that: be set with C at described input shaft (1) according to claim 2 or 3 described return flow type hydraulic machine automatic gear shift transmission devices,
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 the described input shaft (1), at described C
1/ C
RBe set with a gear driven gear (27) on the described input shaft (1) in gear clutch (26) left side, 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
3Be set with three gear driven gears (30) and two gear driven gears (28) on the described input shaft (1) of gear clutch (29) left and right sides, this three gear driven gear (30) and two keep off 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
5Be set with five gear driven gears (1) and four gear driven gears (31) on the described input shaft (1) of gear clutch (32) left and right sides, this five gear driven gear (1) and four keeps off driven gears (31) respectively and C
4/ C
5The driven disc of gear clutch (32) left and right sides is connected; Be installed with a gear driving gear (8) at described jack shaft (4), two gear driving gears (7), three gear driving gears (6), four gear driving gears (5), five gear driving gears (3), a wherein said gear driving gear (8) and gear driven gear (a 27) engagement, described two gear driving gears (7) and two gear driven gear (28) engagements, described three gear driving gears (6) and three gear driven gear (30) engagements, described four gear driving gears (5) and described four gear driven gear (31) engagements, described five gear driving gears (3) and described five gear driven gear (1) engagements.
5. return flow type hydraulic machine automatic gear shift transmission device according to claim 4 is characterized in that: at described C
1/ C
RThe upper empty set of described input shaft (1) in gear clutch (26) the left side driven gear (24) that reverses gear, this driven gear that reverses gear (24) and described C
1/ C
RThe driven disc on gear clutch (26) right side is connected, be installed with the driving gear that reverses gear (9) at described jack shaft (4), also be provided with the reverse gear shaft parallel with described input shaft (1), idle pulley (10) in the middle of this reverse gear shaft is installed with the speed change of reversing gear, idle pulley (10) and the described driven gear that reverses gear (24) and the driving gear that reverses gear (9) engagement in the middle of this speed change of reversing gear, described pump impeller (17) is connected with the break that reverses gear (18).
6. return flow type hydraulic machine automatic gear shift 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 16 with the secondary guide wheel) be connected with the one-way element outer ring respectively, the one-way element inner ring is connected with torque converter housing.
Priority Applications (1)
| 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 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN201310260071.0A CN103307248B (en) | 2013-06-26 | 2013-06-26 | Reverse-flow type hydrodynamic mechanical automatic variable transmission device |
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| CN103307248B CN103307248B (en) | 2015-11-25 |
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| CN103939566A (en) * | 2014-05-07 | 2014-07-23 | 吴志强 | Compound type double-guide-wheel hydraulic torque converter and continuously variable transmission |
| CN103939569A (en) * | 2014-05-07 | 2014-07-23 | 吴志强 | Compound axial-flow type hydraulic torque converter and continuously variable transmission |
| CN105650236A (en) * | 2014-05-07 | 2016-06-08 | 吴志强 | Compound double-guide-wheel type hydraulic torque converter |
| WO2017004782A1 (en) * | 2015-07-07 | 2017-01-12 | 吴志强 | Combined hydraulic transmission |
| CN107504151A (en) * | 2017-10-12 | 2017-12-22 | 中国船舶重工集团公司第七0三研究所 | A kind of power multiple-limb hydraulic planetary arrangements for speed regulation |
| CN107830144A (en) * | 2017-12-18 | 2018-03-23 | 山东华山拖拉机制造有限公司 | Tractor automatic gear shifting dynamic gearshift |
| CN107850199A (en) * | 2015-07-07 | 2018-03-27 | 吴志强 | A kind of buncher |
| CN110735904A (en) * | 2019-10-23 | 2020-01-31 | 重庆大学 | Self-adaptive hydraulic mechanical transmission system of loader |
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| CN103939566A (en) * | 2014-05-07 | 2014-07-23 | 吴志强 | Compound type double-guide-wheel hydraulic torque converter and continuously variable transmission |
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| CN107830144A (en) * | 2017-12-18 | 2018-03-23 | 山东华山拖拉机制造有限公司 | Tractor automatic gear shifting dynamic gearshift |
| CN110735904A (en) * | 2019-10-23 | 2020-01-31 | 重庆大学 | Self-adaptive hydraulic mechanical transmission system of loader |
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Inventor after: Tan Xiaolong Inventor after: Mei Xiaolong Inventor after: Liu Qing Inventor after: Sun Dongye Inventor after: Wang Yong Inventor after: Liu Sheng Inventor after: Yang Yong Inventor before: Sun Dongye Inventor before: Wang Yong Inventor before: Liu Sheng Inventor before: Yang Yong |
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