CN215908345U - Double-planet liquid-discharge mechanical stepless gearbox - Google Patents

Double-planet liquid-discharge mechanical stepless gearbox Download PDF

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Publication number
CN215908345U
CN215908345U CN202122460016.9U CN202122460016U CN215908345U CN 215908345 U CN215908345 U CN 215908345U CN 202122460016 U CN202122460016 U CN 202122460016U CN 215908345 U CN215908345 U CN 215908345U
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gear
clutch
mechanical
hydraulic
shaft
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朱忠祥
李江
翟志强
杜岳峰
毛恩荣
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China Agricultural University
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China Agricultural University
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Abstract

The utility model relates to a double-planet liquid-discharge mechanical stepless gearbox, which comprises a gearbox box body, a mechanical transmission system and a variable pump-fixed displacement motor hydraulic system, wherein the mechanical transmission system and the variable pump-fixed displacement motor hydraulic system are arranged in the gearbox box body; the mechanical transmission system comprises a gear shaft mechanism, a double-planet-row confluence mechanism and a clutch section changing mechanism; the variable pump-fixed displacement motor hydraulic system comprises a variable pump and a fixed displacement motor which are connected with each other. The utility model does not need to carry out clutch conversion on the same planetary gear mechanism during gear shifting, reduces gear shifting impact and transmissionThe movement is more stable; the transmission efficiency of the hydraulic mechanical section is more than 86%; the maximum shift impact is 14m/s3Within.

Description

Double-planet liquid-discharge mechanical stepless gearbox
Technical Field
The utility model belongs to the field of tractors, relates to a tractor gearbox, and particularly relates to a double-planet liquid-discharge mechanical stepless gearbox.
Background
The hydraulic mechanical stepless speed changing box has the advantages of hydraulic transmission stepless speed regulation and high mechanical transmission efficiency, adopts a double-power flow coupling transmission mode, has continuously adjustable transmission ratio so as to realize stepless speed change in a stage section, has stable transmission power, convenient operation and high transmission efficiency, and has important significance for improving the quality and the operation comfort of agricultural machinery operation and reducing the operation cost.
The existing hydraulic mechanical gearbox is mostly driven by a single planet row, although the single planet row gearbox is simple in structure, the transmission efficiency is low, the precision required by hydraulic system components is high, the manufacturing cost is high, and the period is long. If the design is not reasonable in the design stage, the assembled hydraulic mechanical continuously variable transmission cannot meet the performance requirement, and the design development cycle is delayed.
Disclosure of Invention
In view of the above technical problems, an object of the present invention is to provide a double-planetary hydraulic mechanical stepless transmission, which does not require clutch conversion on the same planetary gear mechanism during shifting, reduces shifting impact, and provides more stable transmission compared with the single-row hydraulic mechanical stepless transmission currently used in many cases.
In order to achieve the purpose, the utility model provides the following technical scheme:
a double-planet liquid-discharge mechanical stepless gearbox comprises a gearbox box body 31, and a mechanical transmission system and a variable pump-fixed displacement motor hydraulic system in the gearbox box body 31.
The mechanical transmission system comprises a gear shaft mechanism, a double-planet-row confluence mechanism and a clutch section changing mechanism.
The gear shaft mechanism comprises an input shaft 1, a first intermediate shaft 3, a second intermediate shaft 5, a third intermediate shaft 18, a variable speed output shaft 20, a pump input shaft 24, a PTO shaft 22, a first-stage pure hydraulic section gear 15, a second-stage pure hydraulic section gear 14, an output gear 16, a pump input shaft gear 23, a motor output shaft gear 25, a forward section gear 30, a reverse gear 32, a pump transmission gear 39, a motor transmission gear 40, a motor output shaft 41, a variable speed output shaft gear 42, a second-stage pure hydraulic section transmission gear 43 and a first-stage pure hydraulic section shaft 44.
The double row bus comprises a first row planet carrier 29, a second row planet carrier 26, a second row sun gear 27, a first row sun gear 28, a first row ring gear 9 and a second row ring gear 10.
The clutch section changing mechanism comprises a forward running clutch 4, a reverse gear clutch 2, a pure hydraulic section clutch 17, a first hydraulic mechanical section clutch 13, a second hydraulic mechanical section clutch 7, a third hydraulic mechanical section clutch 11 and a fourth hydraulic mechanical section clutch 8.
The variable pump-constant motor hydraulic system comprises a variable pump 21 and a constant motor 19 which are connected with each other, wherein the variable pump 21 is connected with a pump input shaft 24, and the constant motor 19 is connected with a motor output shaft 41.
Wherein, the forward section gear 30, the reverse gear 32 and the pump transmission gear 39 are fixedly connected on the input shaft 1; the PTO shaft 22 is connected to the input shaft 1; the pump input shaft gear 23 is fixedly connected to the pump input shaft 24; the motor output shaft gear 25 is fixed to the motor output shaft 41.
The forward running clutch 4, the reverse clutch 2 and the first planet carrier 29 are mounted on the first countershaft 3.
And the first hydraulic mechanical section clutch 13, the second hydraulic mechanical section clutch 7, the third hydraulic mechanical section clutch 11, the fourth hydraulic mechanical section clutch 8, the second-stage pure hydraulic section gear 14 and the output gear 16 are arranged on the second intermediate shaft 5.
The pure hydraulic section clutch 17, the second planetary row sun gear 27, the first planetary row sun gear 28, and the motor drive gear 40 are mounted on the third countershaft 18.
The change output shaft gear 42 is fixedly connected to the change output shaft 20.
The first stage pure hydraulic section gear 15 and the second stage pure hydraulic section transmission gear 43 are fixedly connected on a first stage pure hydraulic section shaft 44.
The forward gear 30 is meshed with a gear of the forward driving clutch 4; the reverse gear 32 is engaged with a gear of the reverse clutch 2; the pump drive gear 39 meshes with the pump input shaft gear 23.
The first planet carrier 29 is meshed with the first planet sun gear 28 and is fixed with the second planet ring gear 10 through a pin; the first planet row gear ring 9 is respectively meshed with gears of a second hydraulic mechanical section clutch 7 and a fourth hydraulic mechanical section clutch 8; the second planet row carrier 26 is meshed with the second planet row sun gear 27, and the gears of the first hydro-mechanical section clutch 13 and the third hydro-mechanical section clutch 11 respectively; the motor transmission gear 40 is meshed with the motor output shaft gear 25; the first stage pure hydraulic section gear 15 is meshed with a gear of a pure hydraulic section clutch 17.
The second stage pure hydraulic section transmission gear 43 is meshed with the second stage pure hydraulic section gear 14.
The output gear 16 meshes with a variable output shaft gear 42.
The first hydraulic mechanical section clutch 13 and the second hydraulic mechanical section clutch 7 are connected through a first clutch connecting shaft sleeve 6; the third hydromechanical section clutch 11 and the fourth hydromechanical section clutch 8 are connected by a second clutch connection sleeve 12.
The double-planet liquid-discharge hydraulic mechanical stepless gearbox comprises a forward direction pure hydraulic section, a forward direction first hydraulic mechanical section, a forward direction second hydraulic mechanical section, a forward direction third hydraulic mechanical section, a forward direction fourth hydraulic mechanical section, a backward direction pure hydraulic section, a backward direction first hydraulic mechanical section and a backward direction second hydraulic mechanical section;
the forward direction pure hydraulic section: the pure hydraulic section clutch 17 is combined, and the rest clutches are separated;
the forward direction first hydro-mechanical section: the forward driving clutch 4 is combined with the first hydraulic mechanical section clutch 13, and the other clutches are separated;
the advancing direction second hydraulic mechanical section: the forward driving clutch 4 is combined with the second hydraulic mechanical section clutch 7, and the other clutches are separated;
the forward direction third hydro-mechanical section: the forward driving clutch 4 is combined with the third hydraulic mechanical section clutch 11, and the other clutches are separated;
the forward direction fourth hydro-mechanical section: the forward driving clutch 4 is combined with the fourth hydraulic mechanical section clutch 8, and the other clutches are separated;
the backward direction pure hydraulic section: the reverse gear clutch 2 is combined with the pure hydraulic section clutch 17, and the other clutches are separated;
the backward direction first hydro-mechanical section: the reverse clutch 2 is combined with the first hydraulic mechanical section clutch 13, and the other clutches are separated;
the backward direction second hydraulic mechanical section: the reverse clutch 2 is engaged with the second hydromechanical section clutch 7, and the remaining clutches are disengaged.
The transmission efficiency of the hydraulic mechanical section of the double-planet liquid-discharge mechanical stepless gearbox is over 86 percent; the maximum shift impact is 14m/s3Within.
Compared with the prior art, the utility model has the beneficial effects that:
compared with the existing single-row hydraulic mechanical stepless speed changing box which is used more, the double-planet-row structure mode is adopted, clutch conversion is not needed to be carried out on the same planet gear mechanism during gear shifting, gear shifting impact is reduced, and transmission is more stable. Compared with a pump-motor hydraulic system with high precision, the double-planet-row hydraulic system has the advantages that compared with a single-planet-row hydraulic system output shaft, the double-planet-row hydraulic system output shaft is combined with different planetary gear mechanism components during section changing, so that the displacement ratio needs to be accurately controlled, and the pump-motor hydraulic system with high precision is connected.
The utility model is divided into 5 forward sections and 3 backward sections, and a pure hydraulic section can be adopted for smooth start to reduce start impact during start, and four hydraulic mechanical sections are adopted during forward operation; the pure hydraulic section can make the tractor back stably at a low speed during backing, and the hydraulic mechanical section can make the tractor reach a calibration position quickly during backing.
Stepless speed change in the sections can be realized by controlling the variable pump-the fixed displacement motor, and stepless speed change between the sections can be realized by controlling the combination of different clutches and the displacement ratio. The gear box can be in a full mechanical mode by controlling the displacement ratio, the efficiency is high, and the gear box is suitable for long-time operation; the speed can be continuously changed in the hydraulic mechanical section, the adaptability is strong, the speed regulation characteristic is good, and the hydraulic mechanical section is suitable for most working conditions; the torque characteristic is good in the pure hydraulic section, and the hydraulic control device is suitable for the working condition of low speed and large load.
The transmission efficiency of the hydraulic mechanical section (main working interval) is more than 86%, and the transmission efficiency is high.
The utility model does not need to carry out clutch conversion on the same planetary gear mechanism during gear shifting, so the smoothness of a shifting section is good, the gear shifting quality is good, and the maximum gear shifting impact degree is 14m/s3Within, the comfort level of operation and driving has been improved, the life of clutch has been increased.
Drawings
FIG. 1 is a schematic structural view of a double planetary row hydromechanical continuously variable transmission of the present invention;
FIG. 2 is a forward direction pure hydraulic section drive schematic of the present invention;
FIG. 3 is a drive schematic of the forward first hydromechanical section of the present invention;
FIG. 4 is a drive schematic of the second forward direction hydromechanical section of the present invention;
FIG. 5 is a drive schematic of the third hydro-mechanical segment in the forward direction of the present invention;
FIG. 6 is a drive schematic of the fourth hydro-mechanical segment in the forward direction of the present invention;
FIG. 7 is a reverse direction purely hydraulic segment drive schematic of the present invention;
FIG. 8 is a schematic diagram of the drive of the first hydro-mechanical section in the reverse direction of the present invention;
FIG. 9 is a reverse direction second hydromechanical section drive schematic of the present invention;
FIG. 10 is a schematic diagram of a testing system using a dSPACE semi-physical simulation platform.
Wherein the reference numerals are:
1. input shaft 2 and reverse gear clutch
3. First intermediate shaft 4, forward running clutch
5. Second intermediate shaft 6 and first clutch connecting shaft sleeve
7. Second hydraulic mechanical section clutch 8 and fourth hydraulic mechanical section clutch
9. A first planet row gear ring 10 and a second planet row gear ring
11. Third hydraulic mechanical section clutch 12 and second clutch connecting shaft sleeve
13. First hydraulic mechanical section clutch 14 and second stage pure hydraulic section gear
15. First-stage pure hydraulic section gear 16 and output gear
17. Pure hydraulic section clutch 18 and third intermediate shaft
19. Fixed-displacement motor 20 and variable-speed output shaft
21. Variable displacement pump 22, PTO axle
23. Pump input shaft gear 24 and pump input shaft
25. Motor output shaft gear 26, second planet row planet carrier
27. Second planet row sun gear 28, first planet row sun gear
29. A first planet carrier 30, a forward stage gear
31. Gearbox casing 32, reverse gear
33. dSPACE semi-physical simulation platform box frame 34 and upper computer
35. dSPACE semi-physical simulation platform 36 and CAN bus
37. Controller 38, double-planet liquid-discharge mechanical stepless gearbox
39. Pump drive gear 40, motor drive gear
41. Motor output shaft 42, variable speed output shaft gear
43. Second-stage pure hydraulic section transmission gear 44 and first-stage pure hydraulic section shaft
Detailed Description
The utility model is further illustrated with reference to the following figures and examples.
As shown in fig. 1, a double planetary row hydro-mechanical continuously variable transmission includes a transmission case 31, and a mechanical transmission system and a variable pump-fixed motor hydraulic system in the transmission case 31.
The mechanical transmission system comprises a gear shaft mechanism, a double-planet-row confluence mechanism and a clutch section changing mechanism.
The gear shaft mechanism comprises an input shaft 1, a first intermediate shaft 3, a second intermediate shaft 5, a third intermediate shaft 18, a variable speed output shaft 20, a pump input shaft 24, a PTO shaft 22, a first-stage pure hydraulic section gear 15, a second-stage pure hydraulic section gear 14, an output gear 16, a pump input shaft gear 23, a motor output shaft gear 25, a forward section gear 30, a reverse gear 32, a pump transmission gear 39, a motor transmission gear 40, a motor output shaft 41, a variable speed output shaft gear 42, a second-stage pure hydraulic section transmission gear 43 and a first-stage pure hydraulic section shaft 44.
The double row bus comprises a first row planet carrier 29, a second row planet carrier 26, a second row sun gear 27, a first row sun gear 28, a first row ring gear 9 and a second row ring gear 10.
The clutch section changing mechanism comprises a forward running clutch 4, a reverse gear clutch 2, a pure hydraulic section clutch 17, a first hydraulic mechanical section clutch 13, a second hydraulic mechanical section clutch 7, a third hydraulic mechanical section clutch 11 and a fourth hydraulic mechanical section clutch 8.
The variable pump-constant motor hydraulic system comprises a variable pump 21 and a constant motor 19 which are connected with each other, wherein the variable pump 21 is connected with a pump input shaft 24, and the constant motor 19 is connected with a motor output shaft 41.
Wherein, the forward section gear 30, the reverse gear 32 and the pump transmission gear 39 are fixedly connected on the input shaft 1; the PTO shaft 22 is connected to the input shaft 1; the pump input shaft gear 23 is fixedly connected to the pump input shaft 24; the motor output shaft gear 25 is fixedly connected to the motor output shaft 41;
the forward running clutch 4, the reverse gear clutch 2 and the first planet carrier 29 are arranged on the first intermediate shaft 3;
the first hydraulic mechanical section clutch 13, the second hydraulic mechanical section clutch 7, the third hydraulic mechanical section clutch 11, the fourth hydraulic mechanical section clutch 8, the second-stage pure hydraulic section gear 14 and the output gear 16 are arranged on the second intermediate shaft 5;
the pure hydraulic section clutch 17, the second planet row sun gear 27, the first planet row sun gear 28 and the motor transmission gear 40 are arranged on the third intermediate shaft 18;
the speed change output shaft gear 42 is fixedly connected to the speed change output shaft 20;
the first stage pure hydraulic section gear 15 and the second stage pure hydraulic section transmission gear 43 are fixedly connected on a first stage pure hydraulic section shaft 44.
The forward gear 30 is meshed with a gear of the forward driving clutch 4; the reverse gear 32 is engaged with a gear of the reverse clutch 2; the pump drive gear 39 meshes with the pump input shaft gear 23.
The first planet carrier 29 is meshed with the first planet sun gear 28 and is fixed with the second planet ring gear 10 through a pin; the first planet row gear ring 9 is respectively meshed with gears of a second hydraulic mechanical section clutch 7 and a fourth hydraulic mechanical section clutch 8; the second planet row carrier 26 is meshed with the second planet row sun gear 27, and the gears of the first hydro-mechanical section clutch 13 and the third hydro-mechanical section clutch 11 respectively; the motor transmission gear 40 is meshed with the motor output shaft gear 25; the first stage pure hydraulic section gear 15 is meshed with a gear of a pure hydraulic section clutch 17.
The second stage pure hydraulic section transmission gear 43 is meshed with the second stage pure hydraulic section gear 14.
The output gear 16 meshes with a variable output shaft gear 42.
Preferably, the first hydromechanical section clutch 13 and the second hydromechanical section clutch 7 are connected through a first clutch connecting sleeve 6; the third hydromechanical section clutch 11 and the fourth hydromechanical section clutch 8 are connected by a second clutch connection sleeve 12.
The working process of the utility model is as follows:
the present invention achieves the change of different speed segments based on different clutch combinations as shown in table 1, thereby enabling the tractor to reach a calibrated speed. The double-planet-row hydraulic mechanical stepless gearbox is divided into four forward direction hydraulic mechanical sections (a forward direction first hydraulic mechanical section, a forward direction second hydraulic mechanical section, a forward direction third hydraulic mechanical section and a forward direction fourth hydraulic mechanical section), a forward direction pure hydraulic section, a backward direction pure hydraulic section and two backward direction hydraulic mechanical sections (a backward direction first hydraulic mechanical section and a backward direction second hydraulic mechanical section).
TABLE 1 Clutch control strategy
In table 1, H denotes a forward direction pure hydraulic section, HM1 denotes a forward direction first hydraulic mechanical section, HM2 denotes a forward direction second hydraulic mechanical section, HM3 denotes a forward direction third hydraulic mechanical section, HM4 denotes a forward direction fourth hydraulic mechanical section, RH denotes a reverse direction pure hydraulic section, RHM1 denotes a reverse direction first hydraulic mechanical section, RHM2 denotes a reverse direction second hydraulic mechanical section, "+" denotes a clutch engagement, "-" denotes a clutch disengagement, and 2, 4, 7, 8, 11, 13, and 17 denote a reverse clutch, a forward travel clutch, a second hydraulic mechanical section clutch, a fourth hydraulic mechanical section clutch, a third hydraulic mechanical section clutch, a first hydraulic mechanical section clutch, and a pure hydraulic section clutch, respectively.
When the tractor starts, the pure hydraulic section clutch 17 is combined, and the rest clutches are separated, so that the tractor is in a pure hydraulic section in the forward direction, as shown in fig. 2, and the rotating speed and the torque are regulated by a hydraulic system consisting of a variable pump 21 and a fixed-displacement motor 19. All torque and rotation speeds are output by the input shaft 1 through the pump input shaft gear 23, the pump input shaft 24, the variable pump 21, the fixed-displacement motor 19, the motor output shaft 41, the first-stage pure hydraulic section shaft 44, the second-stage pure hydraulic section transmission gear 43, the second-stage pure hydraulic section gear 14, the second intermediate shaft 5 and the output gear 16, and finally by the variable-speed output shaft 20.
When the speed is increased to enter a first hydraulic mechanical section in the forward direction, as shown in fig. 3, the forward running clutch 4 and the first hydraulic mechanical section clutch 13 are simultaneously combined, and a part of the rotating speed and the torque are transmitted to the second planet row ring gear 10 from the input shaft 1 through the forward section gear 30, the first intermediate shaft 3 and the first planet row planet carrier 29; part of the rotating speed and the torque are transmitted to a second planet row sun gear 27 from the input shaft 1 through a pump input shaft gear 23, a pump input shaft 24, a variable pump 21, a fixed-displacement motor 19, a motor output shaft gear 25 and a third intermediate shaft 18. The two parts of the rotating speed and the torque are converged through the second planet carrier 26, the first hydro-mechanical section clutch 13, the second intermediate shaft 5 and the output gear 16, and finally output by the variable speed output shaft 20.
As the speed increases into the forward direction second hydro-mechanical segment, as shown in fig. 4, the first hydro-mechanical segment clutch 13 is disengaged and the second hydro-mechanical segment clutch 7 is engaged. A part of the rotating speed and the torque are transmitted to a first planet row planet carrier 29 by an input shaft 1 through a forward section gear 30 and a first intermediate shaft 3; part of the rotating speed and the torque are transmitted to a first planet row sun gear 28 through a pump input shaft gear 23, a pump input shaft 24, a variable pump 21, a fixed displacement motor 19, a motor output shaft gear 25 and a third intermediate shaft 18 from an input shaft 1. The two parts of rotating speed and torque are converged to flow through the first planet row gear ring 9, the second hydraulic mechanical section clutch 7, the second intermediate shaft 5 and the output gear 16, and are finally output by the variable speed output shaft 20.
As the speed increases into the forward direction third hydromechanical section, as shown in fig. 5, the second hydromechanical section clutch 7 is disengaged and the third hydromechanical section clutch 11 is engaged; a part of the rotating speed and the torque are transmitted to the second planet row ring gear 10 from the input shaft 1 through the forward section gear 30, the first intermediate shaft 3 and the first planet row planet carrier 29; part of the rotating speed and the torque are transmitted to a first planet row sun gear 28 from the input shaft 1 through a pump input shaft gear 23, a pump input shaft 24, a variable pump 21, a fixed-displacement motor 19, a motor output shaft gear 25 and a third intermediate shaft 18. The two parts of the rotating speed and the torque are converged through the second planet carrier 26, the third hydro-mechanical section clutch 11, the second intermediate shaft 5 and the output gear 16, and finally output by the variable speed output shaft 20.
As the speed increases into the forward direction fourth hydro-mechanical segment, as shown in fig. 6, the third hydro-mechanical segment clutch 11 is disengaged and the fourth hydro-mechanical segment clutch 8 is engaged; part of the rotating speed and the torque are transmitted to a first planet row planet carrier 29 by an input shaft 1 through a forward section gear 30 and a first intermediate shaft 3; part of the rotating speed and the torque are transmitted to a first planet row sun gear 28 through a pump input shaft gear 23, a pump input shaft 24, a variable pump 21, a fixed displacement motor 19, a motor output shaft gear 25 and a third intermediate shaft 18 from an input shaft 1. The two parts of the rotating speed and the torque are converged through the first planet row gear ring 9, the fourth hydraulic mechanical section clutch 8, the second intermediate shaft 5 and the output gear 16, and finally output by the variable speed output shaft 20.
When the tractor moves backwards, as shown in fig. 7, the reverse clutch 2 and the pure hydraulic section clutch 17 are simultaneously engaged, and the reverse of the output rotation speed is realized by the operation of the reverse clutch 2, at which time the tractor is in the pure hydraulic section of the reverse gear.
As the dragging backward speed increases, the reverse clutch 2 and the first hydro-mechanical segment clutch 13 are simultaneously combined to enter the first hydro-mechanical segment in the backward direction; and the reverse gear clutch 2 is continuously combined, and the first hydraulic mechanical section clutch 13 is controlled to be separated and combined with the second hydraulic mechanical section clutch 7 to enter a second hydraulic mechanical section in a reverse direction.
When the tractor is operating in the reverse direction for the first hydromechanical stage, the reverse clutch 2 and the first hydromechanical stage clutch 13 are engaged simultaneously, respectively, as shown in fig. 8. A part of the rotating speed and the torque are transmitted to the first planet carrier 29 from the input shaft 1 through the reverse gear 32 and the first intermediate shaft 3; part of the rotating speed and the torque are transmitted to a first planet row sun gear 28 from the input shaft 1 through a pump input shaft gear 23, a pump input shaft 24, a variable pump 21, a fixed-displacement motor 19, a motor output shaft gear 25 and a third intermediate shaft 18. The two parts of rotating speed and torque are converged to flow through the first planet row gear ring 9, the second hydraulic mechanical section clutch 7, the second intermediate shaft 5 and the output gear 16, and are finally output by the variable speed output shaft 20.
As the speed increases into the reverse direction second hydro-mechanical segment, the reverse clutch 2 is engaged, the first hydro-mechanical segment clutch 13 is disengaged, and the second hydro-mechanical segment clutch 7 is engaged, as shown in fig. 9. A part of the rotating speed and the torque are transmitted to the first planet carrier 29 from the input shaft 1 through the reverse gear 32 and the first intermediate shaft 3; part of the rotating speed and the torque are transmitted to a first planet row sun gear 28 from the input shaft 1 through a pump input shaft gear 23, a pump input shaft 24, a variable pump 21, a fixed-displacement motor 19, a motor output shaft gear 25 and a third intermediate shaft 18. The two parts of rotating speed and torque are converged to flow through the first planet row gear ring 9, the second hydraulic mechanical section clutch 7, the second intermediate shaft 5 and the output gear 16, and are finally output by the variable speed output shaft 20.
As shown in fig. 10, the testing system of the dsace semi-physical simulation platform is adopted for testing, and the dsace semi-physical simulation platform testing system comprises a dsace semi-physical simulation platform box frame 33, an upper computer 34, a dsace semi-physical simulation platform 35, a CAN bus 36 and a controller 37. The double-planet liquid-discharge mechanical continuously variable transmission 38 of the utility model is downloaded to the dSPACE semi-physical simulation platform 35 after being processed by a mathematical model and is connected to the controller 37. The controller 37 realizes stepless speed change by controlling the opening and closing of different clutches and the change of the displacement ratio of the variable pump-fixed displacement motor hydraulic system.
Through testing by a dSPACE semi-physical simulation platform testing system, the transmission efficiency of a hydraulic mechanical section (a main working interval) is over 86 percent; the maximum shift impact is 14m/s3Within.
The utility model uses the dSPACE semi-physical simulation test platform to carry out control test and test verification on the designed double-planet-row hydraulic mechanical stepless speed changer, thereby reducing the cost of real vehicle verification and improving the safety coefficient of the test. The dSPACE semi-physical simulation platform and the real controller are used for verifying the control strategy, the designed parameters can be modified and adjusted, the error probability in real vehicle testing is reduced, the design efficiency of the whole gearbox is improved, and the development period is shortened. The hydraulic stepless speed change box can also be used as other types of hydraulic mechanical stepless speed change boxes for test verification and control verification, and has good expansion performance.

Claims (4)

1. A double-planet liquid-discharge mechanical stepless gearbox is characterized by comprising a gearbox box body (31), a mechanical transmission system and a variable pump-fixed displacement motor hydraulic system, wherein the mechanical transmission system and the variable pump-fixed displacement motor hydraulic system are arranged in the gearbox box body (31);
the mechanical transmission system comprises a gear shaft mechanism, a double-planet-row confluence mechanism and a clutch section changing mechanism;
the gear shaft mechanism comprises an input shaft (1), a first intermediate shaft (3), a second intermediate shaft (5), a third intermediate shaft (18), a variable speed output shaft (20), a pump input shaft (24), a PTO shaft (22), a first-stage pure hydraulic section gear (15), a second-stage pure hydraulic section gear (14), an output gear (16), a pump input shaft gear (23), a motor output shaft gear (25), a forward section gear (30), a reverse gear (32), a pump transmission gear (39), a motor transmission gear (40), a motor output shaft (41), a variable speed output shaft gear (42), a second-stage pure hydraulic section transmission gear (43) and a first-stage pure hydraulic section shaft (44);
the double-planet-row confluence mechanism comprises a first planet row planet carrier (29), a second planet row planet carrier (26), a second planet row sun gear (27), a first planet row sun gear (28), a first planet row gear ring (9) and a second planet row gear ring (10);
the clutch section changing mechanism comprises a forward running clutch (4), a reverse gear clutch (2), a pure hydraulic section clutch (17), a first hydraulic mechanical section clutch (13), a second hydraulic mechanical section clutch (7), a third hydraulic mechanical section clutch (11) and a fourth hydraulic mechanical section clutch (8);
the variable pump-fixed displacement motor hydraulic system comprises a variable pump (21) and a fixed displacement motor (19) which are connected with each other, wherein the variable pump (21) is connected with a pump input shaft (24), and the fixed displacement motor (19) is connected with a motor output shaft (41);
wherein the forward section gear (30), the reverse gear (32) and the pump transmission gear (39) are fixedly connected on the input shaft (1); the PTO shaft (22) is connected with the input shaft (1); the pump input shaft gear (23) is fixedly connected to the pump input shaft (24); the motor output shaft gear (25) is fixedly connected to the motor output shaft (41);
the forward running clutch (4), the reverse gear clutch (2) and the first planet carrier (29) are arranged on the first intermediate shaft (3);
the first hydraulic mechanical section clutch (13), the second hydraulic mechanical section clutch (7), the third hydraulic mechanical section clutch (11), the fourth hydraulic mechanical section clutch (8), the second-stage pure hydraulic section gear (14) and the output gear (16) are arranged on the second intermediate shaft (5);
the pure hydraulic section clutch (17), the second planet row sun gear (27), the first planet row sun gear (28) and the motor transmission gear (40) are arranged on a third intermediate shaft (18);
the gear (42) of the variable speed output shaft is fixedly connected to the variable speed output shaft (20);
the first-stage pure hydraulic section gear (15) and the second-stage pure hydraulic section transmission gear (43) are fixedly connected to a first-stage pure hydraulic section shaft (44);
the forward section gear (30) is meshed with a gear of the forward running clutch (4); the reverse gear (32) is meshed with a gear of the reverse gear clutch (2); the pump transmission gear (39) is meshed with the pump input shaft gear (23);
the first planet carrier (29) is meshed with the first planet sun gear (28) and is fixed with the second planet gear ring (10) through a pin; the first planet row gear ring (9) is respectively meshed with gears of a second hydraulic mechanical section clutch (7) and a fourth hydraulic mechanical section clutch (8); the second planet row planet carrier (26) is respectively meshed with a second planet row sun gear (27) and gears of the first hydraulic mechanical section clutch (13) and the third hydraulic mechanical section clutch (11); the motor transmission gear (40) is meshed with the motor output shaft gear (25); the first-stage pure hydraulic section gear (15) is meshed with a gear of a pure hydraulic section clutch (17);
the second-stage pure hydraulic section transmission gear (43) is meshed with the second-stage pure hydraulic section gear (14);
the output gear (16) is meshed with a variable speed output shaft gear (42).
2. A double row planetary hydro-mechanical continuously variable transmission according to claim 1, characterised in that the first hydro-mechanical section clutch (13) and the second hydro-mechanical section clutch (7) are connected by a first clutch connection sleeve (6); the third hydraulic mechanical section clutch (11) and the fourth hydraulic mechanical section clutch (8) are connected through a second clutch connecting shaft sleeve (12).
3. The double-planetary-row hydro-mechanical continuously variable transmission of claim 1, comprising a forward direction pure hydraulic section, a forward direction first hydro-mechanical section, a forward direction second hydro-mechanical section, a forward direction third hydro-mechanical section, a forward direction fourth hydro-mechanical section, a reverse direction pure hydraulic section, a reverse direction first hydro-mechanical section, a reverse direction second hydro-mechanical section;
the forward direction pure hydraulic section: the pure hydraulic section clutch (17) is combined, and the rest clutches are separated;
the forward direction first hydro-mechanical section: the forward driving clutch (4) is combined with the first hydraulic mechanical section clutch (13), and the other clutches are separated;
the advancing direction second hydraulic mechanical section: the forward driving clutch (4) is combined with the second hydraulic mechanical section clutch (7), and the other clutches are separated;
the forward direction third hydro-mechanical section: the forward driving clutch (4) is combined with the third hydraulic mechanical section clutch (11), and the other clutches are separated;
the forward direction fourth hydro-mechanical section: the forward driving clutch (4) is combined with the fourth hydraulic mechanical section clutch (8), and the other clutches are separated;
the backward direction pure hydraulic section: the reverse gear clutch (2) is combined with the pure hydraulic section clutch (17), and the rest clutches are separated;
the backward direction first hydro-mechanical section: the reverse gear clutch (2) is combined with the first hydraulic mechanical section clutch (13), and the other clutches are separated;
the backward direction second hydraulic mechanical section: the reverse clutch (2) is combined with the second hydraulic mechanical section clutch (7), and the other clutches are separated.
4. The double-planetary-row hydro-mechanical continuously variable transmission of claim 1, wherein the hydro-mechanical section transmission efficiency of the double-planetary-row hydro-mechanical continuously variable transmission is above 86%; the maximum shift impact is 14m/s3Within.
CN202122460016.9U 2021-10-13 2021-10-13 Double-planet liquid-discharge mechanical stepless gearbox Active CN215908345U (en)

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