CN102537269B - Three-section hydraulic mechanical continuous stageless transmission device - Google Patents

Three-section hydraulic mechanical continuous stageless transmission device Download PDF

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CN102537269B
CN102537269B CN 201210025921 CN201210025921A CN102537269B CN 102537269 B CN102537269 B CN 102537269B CN 201210025921 CN201210025921 CN 201210025921 CN 201210025921 A CN201210025921 A CN 201210025921A CN 102537269 B CN102537269 B CN 102537269B
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planet row
clutch
speed
transmission device
break
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CN102537269A (en
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胡纪滨
彭增雄
李雪原
荆崇波
魏超
刘洪�
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Beijing Institute of Technology BIT
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Abstract

The invention discloses a three-section hydraulic mechanical continuous stageless transmission device and a method thereof. The three-section hydraulic mechanical continuous stageless transmission device comprises a planet transmission part, a hydraulic speed regulation part and a section change operation part. The whole device uses two planet rows as basis to reasonably control reunion or separation of the section change operation part and smoothly join a speed-division moment-converge flow-split mode, a speed-division speed-converge flow-split mode and a moment-division speed-converge flow-split mode to fully develop performance advantages of all flow-split modes. In addition, the transmission device can achieve a reverse-gear pure hydraulic work condition and pure mechanical transmission work condition of two fixed gears. The transmission device has the advantages of being simple in structure, continuous in stepless speed change, good in starting characteristics, small in system volume, small in mass and the like.

Description

3 stops Hydro-Mechanical Variable Transmission device
Technical field
The present invention relates to a kind of continuously variable transmittion, be specifically related to a kind of 3 stops Hydro-Mechanical Variable Transmission device, belong to the power transmission field.
Background technique
Vehicle drive system is the important component part of vehicle propulsion system, and its performance has great impact to power character, fuel economy, discharging and the reliability of whole vehicle.Multistage Hydro-Mechanical Variable Transmission system has wider stepless speed regulation scope, good starting characteristic and the higher advantages such as transmission efficiency, can be according to pavement behavior, optimize engine behavior, make vehicle obtain best rideability, can adapt to the requirement of vehicle economy, power character and travelling comfort, be a kind of desirable type of belt drive.This is in energy shortage, and the 21 century that environmental pollution increasingly sharpens is significant.
Abroad systematic research mainly is as main take two stage mode about the multistage Hydro-Mechanical Variable Transmission at present, invention about three stage modes is less, and construct as the basis take three planet rows at least about the scheme of three stage modes, cause the whole system structure comparatively complicated, this is for improving system effectiveness, and the volume of mitigation system and weight are comparatively unfavorable.
Summary of the invention
In view of this, the invention provides a kind of 3 stops Hydro-Mechanical Variable Transmission device, this device is take two planet rows as the basis, reasonable link divides speed remittance square, divides speed remittance speed, divides square remittance speed three kinds of shunt modes, form 3 stops continuous stepless gear structure, have the advantages such as simple in structure, that volume is little.
3 stops Hydro-Mechanical Variable Transmission device of the present invention comprises Gear Planet Transmission parts, Hydraulic Adjustable Speed parts and the section of changing control member.Wherein the Gear Planet Transmission parts comprise planet row k1 and planet row k2; The section of changing control member comprises clutch C1, clutch C2, break B1 and break B2; The Hydraulic Adjustable Speed parts comprise speed governing element H1 and speed governing element H2, and speed governing element H1 and speed governing element H2 adopt Closed Hydraulic transmission loop and bidirectional variable control.
Its annexation is: input shaft one end of transmission device is connected with motor, thereby for whole device provides power, the other end links to each other with k1 planet row planet carrier by the stationary axle gear A; K1 planet row gear ring links to each other with the active part of clutch C1, links to each other with speed governing element H1 by the stationary axle gear B simultaneously; K1 planet row sun gear links to each other with the active part of clutch C2 by its central shaft, the central shaft of break B2 braking k1 planet row sun gear; Central shaft one end of k2 planet row sun gear is connected with speed governing element H2, and the other end links to each other with the passive part of clutch C2; K2 planet row gear ring links to each other with the passive part of clutch C1, break B1 braking k2 planet row gear ring; K2 planet row planet carrier links to each other with the output shaft of transmission device by the stationary axle gear C.
Working principle of the present invention is: the discharge capacity ratio of at first determining speed governing element H1 and speed governing element H2 according to the travel situations of vehicle, according to combination or the separation of determined discharge capacity than the reasonable control section of changing control member, just can realize 3 stops continuous partial flow operating mode, be respectively a minute speed remittance square, minute fast remittance speed and divide speed remittance square.In addition this transmission device pure mechanical transmission operating mode of pure hydraulic pressure operating mode and two fixed stop that can also realize reversing gear.
The first shunt mode---minute speed remittance square: break B1 braking, clutch C2 combination, break B2 and clutch C1 do not work.This moment, k1 planet row gear ring linked to each other with speed governing element H1, and k1 planet row sun gear links to each other with speed governing element H2 by k2 planet row sun gear.
The second shunt mode---minute speed is converged fast: this moment clutch C1 and equal combination of clutch C2, break B2 and break B1 do not work.This moment, k1 planet row gear ring linked to each other with k2 planet row gear ring with speed governing element H1 respectively, and k1 planet row sun gear links to each other with speed governing element H2 by the sun gear of planet row k2.
The third shunt mode---minute square converges fast: break B2 braking, and clutch C1 combination, clutch C2 and break B1 do not work.This moment, k1 planet row gear ring linked to each other with k2 planet row gear ring with speed governing element H1 respectively, the whole revolution of k1 planet row.Speed governing element H2 links to each other with k2 planet row sun gear.
When break B1 and break B2 brake simultaneously, when clutch C1 and clutch C2 did not work, system realized pure hydraulic pressure sternway operating mode.The pure machinery gear of two of system operating modes are respectively fixing shelves 1 and fixing shelves 2,1 o'clock clutch C1 of fixing shelves and simultaneously combination of clutch C2, and break B1 braking, break B2 does not work.2 o'clock clutch C1 of fixing shelves and simultaneously combination of clutch C2, break B2 braking, break B1 does not work.
Beneficial effect:
(1) utilize two planet row structures to have the 3 stops Hydro-Mechanical Variable Transmission device of three shunt modes, can realize stepless change in a big way, and simple in structure.
(2) transmission device of the present invention has a minute speed remittance square, divides speed remittance speed, divides square remittance speed three kinds of shunt modes, adopt a minute speed remittance square shunt mode in the starting stage of vehicle, has the characteristic that starts to walk preferably, and need not to design start clutch in the whole device, make vehicle have preferably driving power.
(3) by velocity ratio behind the Proper Match, minute speed converge square pattern and minute speed converge fast mode in low speed of a motor vehicle interval can obtain higher transmission efficiency; In high velocity, system is in a minute square remittance fast mode, even the speed governing road power dividing of system increases than with speed of a motor vehicle increase, but can remain in the rational scope, and system still can obtain considerable transmission efficiency.
(4) power linking, vehicle power raising can not be cut off in the linking of each section shunt mode conversion.
(5) during the section of changing, the section of changing control member substantially without sliding rub in conjunction with separate, friction pair can be chosen static friction coefficient, structural design reduces volume and weight greatly, in the using process, reliability also can significantly improve.
(6) this transmission device can make vehicle be in best travelling state according to pavement behavior and engine behavior, and motor is worked near best power source linearity curve or optimal economic characteristic curve, improves the fuel economy of vehicle, reduces noise.
Description of drawings
Fig. 1 is 3 stops Hydro-Mechanical Variable Transmission device transmission sketch;
Fig. 2 is that first paragraph divides speed remittance square shunt mode linkage structure and power flow diagram;
Fig. 3 is that second segment divides the speed fast shunt mode linkage structure of remittance and power flow diagram;
Fig. 4 is that three section minute square converges fast shunt mode linkage structure and power flow diagram;
Fig. 5 is motor, speed governing element H1, speed governing element H2 and system's output shaft speed curves;
Fig. 6 is the speed curves of each member of k1 planet row;
Fig. 7 is the speed curves of each member of k2 planet row;
Fig. 8 is speed governing element H1, the discharge capacity ratio of H2 and the variation relation curve of system's output speed ratio;
Fig. 9 is 3 stops Hydro-Mechanical Variable Transmission device curve of traction characteristics.
Wherein: 1-motor, 2-stationary axle gear A, 3-k1 planet row sun gear central shaft, 7-stationary axle gear B, 8-k1 planet row gear ring, 12-k2 planet row gear ring, 13-transmission device output shaft, 14-stationary axle gear C, 17-k2 planet row sun gear, 18-k2 planet row planet carrier, 21-k1 planet row planet carrier, 22-k1 planet row sun gear, 23-transmission device input shaft.
Embodiment
Below in conjunction with the accompanying drawing embodiment that develops simultaneously, describe the present invention.
In the present embodiment 3 stops Hydro-Mechanical Variable Transmission device is used on the city bus, as shown in Figure 1, this device comprises Gear Planet Transmission parts (k1 planet row and k2 planet row), Hydraulic Adjustable Speed parts (speed governing element H1 and speed governing element H2), the section of changing control member (clutch C1, clutch C2, break B1 and break B2).In the present embodiment, speed governing element H1 and speed governing element H2 all adopt hydraulic variable displacement pump, and realize the hydraulic stepless speed regulating of this transmission device by the mode of Closed Hydraulic transmission loop and bidirectional variable control.
Its annexation is: an end of transmission device input shaft 23 is connected with motor 1, and for whole device provides power, the other end links to each other with k1 planet row planet carrier 21 by stationary axle gear A 2; K1 planet row gear ring 12 links to each other with the active part of clutch C1, links to each other with speed governing element H1 by stationary axle gear B 7 simultaneously; K1 planet row sun gear central shaft 3 links to each other with the active part of clutch C2, break B2 braking k1 planet row sun gear central shaft 3; Central shaft one end of k2 planet row sun gear 17 is connected with speed governing element H2, and the other end links to each other with the passive part of clutch C2; K2 planet row gear ring 12 links to each other with the passive part of clutch C1, break B1 braking k2 planet row gear ring; K2 planet row planet carrier 18 links to each other with transmission device output shaft 13 by stationary axle gear C 14.
The 3 stops continuous partial flow operating mode that this transmission device can be realized is respectively: first paragraph---minute speed remittance square section; Second segment---minute speed is converged fast section; The 3rd section---minute square converges fast section.Other system's pure mechanical transmission operating mode of pure hydraulic pressure operating mode and two fixed stop that can also realize reversing gear.
When dividing speed to converge the square section, the braking of B1 break, the combination of C2 clutch, B2 break and C1 clutch are not worked, and the structure of this section system and power stream are as shown in Figure 2.For realizing the increase of transmission device output shaft 13 rotating speeds, i.e. realization system exports the increase of speed ratio, and speed governing element H1 changes shown in the first paragraph scope among Fig. 8 with speed governing element H2 discharge capacity ratio.At this section end, system reaches first pure mechanical. points, and the rotating speed of speed governing element H1 is 0, C1 clutch combination this moment, and the B1 break discharges, and the C2 clutch still is in bonding state, and the B2 break is not worked.System enters second segment---and minute speed is converged fast section, and the structure Connecting format of realization and power stream are as shown in Figure 3.Speed governing element H1 and speed governing element H2 discharge capacity be than continuing to change continuously shown in the second segment scope among Fig. 8, and continuation that can realization system output speed ratio increases, thereby the continuation that has realized the output shaft rotating speed increases.Second segment is terminal, and system reaches second pure mechanical. points, and the rotating speed of speed governing element H2 is 0, and this moment, the C2 clutch discharged, the braking of B2 break, and the C1 clutch still is in bonding state, and the B1 break is not worked.System enters the 3rd section---and minute speed remittance square section, the structure Connecting format of realization and power stream are as shown in Figure 4.For the continuation that realizes the output shaft rotating speed increases, speed governing element H1 can continue to change continuously shown in the 3rd segment limit among Fig. 8 with speed governing element H2 discharge capacity ratio, until this section end, vehicle reaches highest line and sails the speed of a motor vehicle.
When B1, B2 break are braked simultaneously, C1, when the C2 clutch is not worked, system can realize pure hydraulic pressure sternway operating mode.The discharge capacity ratio of speed governing element H2 remains the forward maximum, and toward being adjusted to maximum in the other direction, the continuous negative sense of feasible system output speed increases the discharge capacity of speed governing element H1 than continuously.
The realization of two pure machinery gear operating modes of system is respectively in addition:
Fixing shelves 1:C1, the simultaneously combination of C2 clutch, the braking of B1 break, the B2 break is not worked.
Fixing shelves 2:C1, the simultaneously combination of C2 clutch, the braking of B2 break, the B1 break is not worked.
Table 1 is that above each operating mode operating element is handled abridged table.
Table 1
Driving cycle Shunt mode Clutch C1 Clutch C2 Break B1 Break B2
Hydro-mechanical segment I Divide speed remittance square ● ●
Hydro-mechanical segment II It is fast to divide speed to converge ● ●
Hydro-mechanical segment III It is fast to divide square to converge ● ●
Sternway Pure hydraulic pressure ● ●
Fixing shelves 1 Pure machinery ● ● ●
Fixing shelves 2 Pure machinery ● ● ●
In the table 1, ●---represent this member combination.
According to above scheme, each section of transmission device rotation speed relation formula of the present invention is in addition:
Rotation speed relation formula when transmission device is in hydro-mechanical segment I section:
n o = 1 i h ( 1 + k 2 ) n 2 = 1 i h ( 1 + k 2 ) n 1 i v = i p i v ( 1 + k 1 ) n in i 1 ( 1 + k 2 ) i h ( i p i v + k 1 ) - - - ( 1 )
In the formula: n 0Rotating speed for hydro-mechanical segment I section timer output shaft;
n 1Rotating speed for speed governing element H1;
n 2Rotating speed for speed governing element H2;
i 1Be the velocity ratio of transmission device input shaft to the planet carrier of k1 planet row;
i hBe the planet carrier of planet row 2 velocity ratio to the wheel semiaxis;
k 1Be k1 planet row special parameter;
k 2Be k2 planet row special parameter;
n InBe transmission device input shaft rotating speed;
i PSpeed governing element H1 is to the velocity ratio of k1 planet row gear ring;
i vBe speed governing element speed ratio
Figure GDA00002815818500062
Rotation speed relation formula when transmission device is in hydraulic machinery II section:
n o = ( k 2 + i p i v ) ( 1 + k 1 ) n in i 1 ( 1 + k 2 ) i h ( i p i v + k 1 ) - - - ( 2 )
Rotation speed relation formula when transmission device is in hydraulic machinery III section:
n o = ( k 2 + i p i v ) ( 1 + k 1 ) n in i 1 k 1 ( 1 + k 2 ) i h - - - ( 3 )
Rotation speed relation formula when transmission device is in the sternway operating mode:
n o = i p i v ( 1 + k 1 ) n in i 1 k 1 ( 1 + k 2 ) i h - - - ( 4 )
Transmission device is in 1 o'clock rotation speed relation formula of fixing shelves:
n o = ( 1 + k 1 ) n in k 1 ( 1 + k 2 ) i h i 1 - - - ( 5 )
Transmission device is in 2 o'clock rotation speed relation formula of fixing shelves:
n o = k 2 ( 1 + k 1 ) n in k 1 ( 1 + k 2 ) i h i 1 - - - ( 5 )
Fig. 5 has provided motor under the continuous working conditions, speed governing element H1, and H2 and output shaft rotating speed are with the change curve of the speed of a motor vehicle, and y coordinate is each component speed, and abscissa is the speed of a motor vehicle and the residing active section of transmission device.
Can find out that from Fig. 6 and 7 speed range of each planet row member is normal, the ultrahigh rotating speed situation not occur.
In the present embodiment whole-car parameters and main performance index choose as follows:
The vehicle performance index:
Engine power P f: 132kW/2300r/min;
Idling speed: 800r/min;
All-up weight: 8t;
Top speed: 90km/h;
Max. climb slope (being fully loaded with): 17 °;
0～32km/h time for acceleration＜10s;
The complete vehicle structure parameter:
The driving wheel radius r z: 0.59m;
Front face area of automobile is: A=6m 2
Coefficient of air resistance: C d=0.6
Driving front compares i 1=2.3
Speed governing element H1 is to the velocity ratio i of k1 planet row gear ring p=2
K1 planet row special parameter k 1: 1.58;
K2 planet row special parameter k 2: 2.78;
Rear velocity ratio: i h=5.1;
Hydraulic Adjustable Speed element major parameter:
Specified input speed n Max: 3300r/min;
Rated working pressure P Max: 40MPa;
Pump range of variables: 0～V GmaxAdjustable continuously
Pump, motor displacement V Gmax: 71cm 3/ r; Nominal torque: T M=451Nm;
Rated power: P M=155kW.
Fig. 8 has provided speed governing element H1, the discharge capacity ratio of speed governing element H2 and the variation relation curve of system's output speed ratio.System output speed ratio is the output shaft rotating speed and the ratio of engine speed.
The curve of traction characteristics of present embodiment as shown in Figure 9.
In sum, more than be preferred embodiment of the present invention only, be not for limiting protection scope of the present invention.Within the spirit and principles in the present invention all, any modification of doing, be equal to replacement, improvement etc., all should be included within protection scope of the present invention.

Claims (9)

1. a 3 stops Hydromechanical Stepless Transmission device is characterized in that: comprise Gear Planet Transmission parts, Hydraulic Adjustable Speed parts and the section of changing control member; Wherein the Gear Planet Transmission parts comprise k1 planet row and k2 planet row; The section of changing control member comprises clutch C1, clutch C2, break B1 and break B2; The Hydraulic Adjustable Speed parts comprise speed governing element H1 and speed governing element H2, and speed governing element H1 and speed governing element H2 adopt closed hydraulic pressure transmission loop and bidirectional variable control; This device can be realized 3 stops continuous partial flow operating mode, is respectively a minute speed remittance square, minute fast remittance speed and divides square to converge fast;
Its annexation is: an end of transmission device input shaft (23) is connected with motor (1), and the other end links to each other with k1 planet row planet carrier (21) by stationary axle gear A (2); K1 planet row gear ring (8) links to each other with the active part of clutch C1, links to each other with speed governing element H1 by stationary axle gear B (7) simultaneously; K1 planet row sun gear central shaft (3) links to each other with the active part of clutch C2, and break B2 brakes k1 planet row sun gear central shaft (3); Central shaft one end of k2 planet row sun gear (17) is connected with speed governing element H2, and the other end links to each other with the passive part of clutch C2; K2 planet row gear ring (12) links to each other with the passive part of clutch C1, and break B1 brakes k2 planet row gear ring (12); K2 planet row planet carrier (18) links to each other with the output shaft (13) of transmission device by stationary axle gear C (14).
2. a kind of 3 stops Hydromechanical Stepless Transmission device as claimed in claim 1, it is characterized in that: described speed governing element H1 and speed governing element H2 all adopt hydraulic variable displacement pump.
3. a kind of 3 stops Hydromechanical Stepless Transmission device as claimed in claim 1 or 2, it is characterized in that, speed remittance square operating mode was in described minute: break B1 braking, clutch C2 combination, break B2 and clutch C1 do not work, k1 planet row gear ring this moment (8) links to each other with speed governing element H1, and k1 planet row sun gear (22) links to each other with speed governing element H2 by k2 planet row sun gear (17).
4. a kind of 3 stops Hydromechanical Stepless Transmission device as claimed in claim 1 or 2, it is characterized in that, the fast operating mode of speed remittance was in described minute: clutch C1 and the equal combination of clutch C2, break B2 and break B1 do not work, k1 planet row gear ring this moment (8) links to each other with k2 planet row gear ring (12) with speed governing element H1 respectively, and k1 planet row sun gear (22) links to each other with speed governing element H2 by k2 planet row sun gear (17).
5. a kind of 3 stops Hydromechanical Stepless Transmission device as claimed in claim 1 or 2, it is characterized in that, described minute square converges fast operating mode and is: break B2 braking, clutch C1 combination, clutch C2 and break B1 do not work, k1 planet row gear ring this moment (8) links to each other with k2 planet row gear ring (12) with speed governing element H1 respectively, the whole revolution of k1 planet row, and speed governing element H2 links to each other with k2 planet row sun gear (17).
6. a kind of 3 stops Hydromechanical Stepless Transmission device as claimed in claim 1 or 2 is characterized in that, when break B1 and break B2 brake simultaneously, clutch C1 and the clutch C2 timer of not working is realized pure hydraulic pressure sternway operating mode.
7. a kind of 3 stops Hydromechanical Stepless Transmission device as claimed in claim 1 or 2 is characterized in that, when clutch C1 and simultaneously combination of clutch C2, and break B1 braking, this transmission device was not realized pure machinery gear operating mode when break B2 did not work.
8. a kind of 3 stops Hydromechanical Stepless Transmission device as claimed in claim 1 or 2 is characterized in that, simultaneously combination of clutch C1 and clutch C2, and break B2 braking, this transmission device was not realized pure machinery gear operating mode when break B1 did not work.
9. a kind of 3 stops Hydromechanical Stepless Transmission device as claimed in claim 1 or 2 is characterized in that, the special parameter of described k1 planet row is that the special parameter of 1.58, k2 planet row is 2.78.
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