CN119123024A - Dual-motor hydraulic mechanical continuously variable transmission system and method - Google Patents
Dual-motor hydraulic mechanical continuously variable transmission system and method Download PDFInfo
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- CN119123024A CN119123024A CN202411527719.0A CN202411527719A CN119123024A CN 119123024 A CN119123024 A CN 119123024A CN 202411527719 A CN202411527719 A CN 202411527719A CN 119123024 A CN119123024 A CN 119123024A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
- F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
- F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
- F16H2047/045—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion the fluid gearing comprising a plurality of pumps or motors
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Abstract
本发明公开了一种双马达液压机械无级变速传动系统及方法，涉及无级变速传动技术领域，输入轴模块的输出端连接动力输出轴模块的输入端和液压泵轴模块的输入端，马达轴被动齿轮与输入轴模块的输出端啮合，马达轴被动齿轮和两个液压马达同轴连接，液压泵轴模块的输出端分别连接两个液压马达，两个液压马达均与马达轴太阳轮的输入端连接，马达轴太阳轮分别啮合前进行星组件和后退行星组件，马达轴主动齿轮分别连接前进行星组件和后退行星组件，前进离合器连接前进行星组件，后退离合器连接后退行星组件，马达轴主动齿轮还与输出轴模块啮合，输出轴模块的输出端用于连接前后驱动桥。本发明能够提高传动效率、操控性能以及工作效率。
The invention discloses a dual-motor hydraulic mechanical continuously variable transmission system and method, and relates to the technical field of continuously variable transmission, wherein the output end of the input shaft module is connected to the input end of the power output shaft module and the input end of the hydraulic pump shaft module, the motor shaft driven gear is meshed with the output end of the input shaft module, the motor shaft driven gear is coaxially connected with two hydraulic motors, the output end of the hydraulic pump shaft module is respectively connected to two hydraulic motors, both of which are connected to the input end of the motor shaft sun gear, the motor shaft sun gear is respectively meshed with the forward planetary assembly and the backward planetary assembly, the motor shaft driving gear is respectively connected to the forward planetary assembly and the backward planetary assembly, the forward clutch is connected to the forward planetary assembly, the backward clutch is connected to the backward planetary assembly, the motor shaft driving gear is also meshed with the output shaft module, and the output end of the output shaft module is used to connect the front and rear drive axles. The invention can improve transmission efficiency, control performance and work efficiency.
Description
Technical Field
The invention relates to the technical field of stepless speed change transmission, in particular to a double-motor hydraulic mechanical stepless speed change transmission system and a method.
Background
At present, the domestic wheel type engineering vehicle commonly adopts a hydraulic transmission and power shift transmission, which has the problems of low transmission efficiency, low working efficiency, high energy consumption and difficult emission reaching standards, and part of engineering vehicles are provided with schemes adopting electric transmission, but have high cost, limited use prospects and difficult market popularization. Because the engineering vehicle often needs forward and backward reversing when working, the hydraulic mechanical stepless speed change transmission system without a clutch needs a pump reversing variable, and the motor is reversed to realize forward and backward switching, so that the problems of power circulation loss and low backward transmission efficiency exist.
Disclosure of Invention
The invention aims to provide a double-motor hydraulic mechanical stepless speed change transmission system and a method thereof, which are used for solving the problems of the prior art and improving transmission efficiency, control performance and working efficiency.
In order to achieve the above object, the present invention provides the following solutions:
The invention provides a double-motor hydraulic mechanical stepless speed change transmission system which comprises an input shaft module, a power output shaft module, a hydraulic pump shaft module, a hydraulic motor shaft module and an output shaft module, wherein the input end of the input shaft module is used for being connected with an engine, the output end of the input shaft module is connected with the input end of the power output shaft module and the input end of the hydraulic pump shaft module, the output end of the power output shaft module is used for power output, the hydraulic motor shaft module comprises a motor shaft sun gear, a motor shaft driving gear, a motor shaft driven gear, a forward clutch, a backward clutch, a forward planetary assembly, a backward planetary assembly and two hydraulic motors, the motor shaft driven gear is meshed with the output end of the input shaft module, the motor shaft driven gear is coaxially connected with the two hydraulic motors, the output ends of the hydraulic pump shaft module are respectively connected with the input ends of the motor shaft sun gear, the motor shaft sun gear is respectively meshed with the forward planetary assembly and the backward planetary assembly, the forward planetary assembly is respectively connected with the backward planetary assembly, and the backward planetary assembly is further meshed with the forward planetary assembly.
Preferably, the input shaft module includes an input driving gear, an input ring gear, an input planet carrier, an input planetary gear and an input sun gear, wherein the input driving gear is used for being connected with an output shaft of the engine, the input driving gear is meshed with the power output shaft module, the input driving gear is further coaxially connected with the input planet carrier, the input planetary gear is mounted on the input planet carrier, and the input planetary gear is meshed with the input sun gear and the input ring gear.
Preferably, the power take-off module includes a power take-off driven gear meshed with the input drive gear and mounted on a shaft of the power take-off module.
Preferably, the hydraulic pump shaft module comprises a hydraulic pump driven gear and a hydraulic pump, the hydraulic pump driven gear is meshed with the input annular gear, the hydraulic pump driven gear is coaxially connected with the hydraulic pump, and an oil port of the hydraulic pump is connected with the two hydraulic motors through pipelines.
Preferably, the two hydraulic motors are a first hydraulic motor and a second hydraulic motor respectively, two oil ports of the first hydraulic motor are connected with two oil ports of the hydraulic pump respectively, two oil ports of the second hydraulic motor are connected with two oil ports of the hydraulic pump respectively, and the first hydraulic motor, the second hydraulic motor and the motor shaft sun gear are all coaxially connected.
Preferably, the hydraulic pump is a closed variable displacement pump.
Preferably, the preceding star subassembly includes preceding planet carrier, preceding star gear and preceding ring gear, preceding star gear install in preceding on the planet carrier, the back star subassembly includes back star carrier, back star gear and back ring gear, back star gear install in on the back star carrier, the motor axle sun gear with preceding star gear with back star gear meshing, the motor axle driving gear with preceding planet carrier with back ring gear is connected, advance clutch with preceding ring gear is connected, back clutch with back star carrier is connected.
Preferably, the output shaft module includes an output shaft driven gear that meshes with the motor shaft drive gear.
Preferably, the hydraulic motor is a tilt-axis variable displacement plunger motor.
The invention also provides a double-motor hydraulic mechanical stepless speed change transmission method, which adopts the double-motor hydraulic mechanical stepless speed change transmission system according to any one of the technical schemes, and comprises the following conditions:
when the forward clutch and the backward clutch are both separated, the clutch is in neutral gear;
When the forward clutch is engaged and the reverse clutch is disengaged, the forward gear is selected, wherein:
When the hydraulic pump has positive displacement and the first hydraulic motor and the second hydraulic motor rotate positively and reach the maximum displacement, the hydraulic pump is suitable for heavy-load low-speed running at the moment, and the power output is realized to be low-speed heavy-load forward;
When the positive displacement and the displacement of the hydraulic pump are gradually increased, the displacement of the first hydraulic motor is gradually reduced until the displacement of the first hydraulic motor becomes zero, and the displacement of the second hydraulic motor is gradually reduced, or when the positive displacement and the displacement of the hydraulic pump are gradually increased, the displacement of the second hydraulic motor is gradually reduced until the displacement of the second hydraulic motor becomes zero, and the displacement of the first hydraulic motor is gradually reduced, the speed of the vehicle is gradually increased, and the power output is realized to be high-speed forward;
When the hydraulic pump has positive displacement and maximum displacement, and the first hydraulic motor box and the second hydraulic motor have zero displacement, the vehicle speed reaches the maximum, and the hydraulic transmission power is zero at the moment, so that the power output is realized to be purely mechanical transmission and advance;
When the reverse clutch is engaged and the forward clutch is disengaged, the gear is a reverse gear, wherein;
When the hydraulic pump is in positive displacement, the first hydraulic motor and the second hydraulic motor are in positive rotation, and the displacement reaches the maximum displacement, the hydraulic pump is suitable for heavy-load low-speed running, and the power output is realized to be in low-speed heavy-load backward;
When the hydraulic pump is positive in displacement and the displacement is gradually increased, the displacement of the second hydraulic motor is gradually reduced until the displacement becomes zero, or the displacement of the first hydraulic motor is gradually reduced until the displacement becomes zero, and when the displacement of the second hydraulic motor is gradually reduced, the speed of the vehicle is gradually increased, so that the power output is realized to be high-speed retreating.
Compared with the prior art, the invention has the following technical effects:
According to the double-motor hydraulic mechanical stepless speed change transmission system and the method, the output end of the input shaft module is connected with the input end of the power output shaft module and the input end of the hydraulic pump shaft module, the motor shaft driven gear is meshed with the output end of the input shaft module, the motor shaft driven gear is coaxially connected with the two hydraulic motors, the output end of the hydraulic pump shaft module is respectively connected with the two hydraulic motors, the two hydraulic motors are both connected with the input end of the motor shaft sun gear, when the forward speed and the backward speed are high, a certain hydraulic motor can be alternately used for prolonging the service life of the gearbox, the motor shaft sun gear is meshed with the forward star component and the backward star component respectively, the motor shaft driving gear is connected with the forward star component and the backward star component respectively, the forward clutch is connected with the forward star component, the backward clutch is connected with the backward star component, when the forward clutch and the backward clutch are both separated, the forward of the vehicle can be realized, and when the backward clutch is combined, the forward of the vehicle can be realized, and the motor shaft driving gear is meshed with the output shaft module. Through the design, stepless speed regulation and parking reversing can be realized according to driving requirements, gear shifting impact is avoided, power circulation is avoided, operability is good, operation efficiency is high, an engine can be controlled to work at an optimal power point or an optimal oil consumption point according to resistance change in real time, power performance or fuel economy of the whole vehicle is improved, meanwhile, the hydraulic transmission and mechanical transmission advantages are achieved, on one hand, larger torque output can be realized when the rotation speed of the engine is low, and the power performance is good.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are needed in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic diagram of a two-motor hydromechanical continuously variable transmission system according to the first embodiment;
In the figure: 1-input shaft module, 101-input driving gear, 102-input ring gear, 103-input planet carrier, 104-input planet gear, 105-input sun gear, 2-power output shaft module, 201-power output driven gear, 3-hydraulic pump shaft module, 301-hydraulic pump driven gear, 302-hydraulic pump, 4-hydraulic motor shaft module, 401-first hydraulic motor, 402-motor shaft driven gear, 403-motor shaft driving gear, 404-second hydraulic motor, 405-motor shaft sun gear, 406-back star, 407-back star, 408-back ring gear, 409-forward planet carrier, 410-forward star, 411-forward ring gear, 412-forward clutch, 413-back clutch, 5-output shaft module, 501-output shaft driven gear.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
The invention aims to provide a double-motor hydraulic mechanical stepless speed change transmission system and a method, which are used for solving the problems existing in the prior art and improving transmission efficiency, control performance and working efficiency.
In order that the above-recited objects, features and advantages of the present invention will become more readily apparent, a more particular description of the invention will be rendered by reference to the appended drawings and appended detailed description.
Example 1
As shown in fig. 1, the present embodiment provides a dual-motor hydromechanical continuously variable transmission system capable of being used for a non-road work vehicle, particularly, a work vehicle hydromechanical power split continuously variable transmission suitable for a frequent forward/reverse switching, comprising an input shaft module 1, a power output shaft module 2, a hydraulic pump shaft module 3, a hydraulic motor shaft module 4 and an output shaft module 5, an input end of the input shaft module 1 being connected to an engine for power input, an output end of the input shaft module 1 being connected to an input end of the power output shaft module 2 and an input end of the hydraulic pump shaft module 3, an output end of the power output shaft module 2 being used for power output, the hydraulic motor shaft module 4 comprising a motor shaft sun gear 405, a motor shaft driving gear 403, a motor shaft driven gear 402, a forward clutch 412, a reverse clutch 413, a forward planetary assembly, a reverse planetary assembly and two hydraulic motors, the motor shaft driven gear 402 is meshed with the output end of the input shaft module 1, the motor shaft driven gear 402 is coaxially connected with two hydraulic motors, the output end of the hydraulic pump shaft module 3 is respectively connected with two hydraulic motors, the two hydraulic motors are connected with the input end of the motor shaft sun gear 405, when the forward and backward vehicle speeds are high, a certain hydraulic motor can be alternatively used for prolonging the service life of the gearbox, the motor shaft sun gear 405 is meshed with a front proceeding star component and a backward proceeding star component respectively, the motor shaft driving gear 403 is connected with the front proceeding star component and the backward proceeding star component respectively, the front proceeding star component is connected with the front proceeding clutch 412, the backward proceeding star component is connected with the backward proceeding clutch 413, the front proceeding clutch 412 and the backward proceeding clutch 413 are both separated to be neutral gear, the forward movement of the vehicle can be realized when the forward clutch 412 is combined, the backward movement of the vehicle can be realized when the backward clutch 413 is combined, the motor shaft driving gear 403 is also meshed with the output shaft module 5, the output end of the output shaft module 5 is used for connecting a front driving axle and a rear driving axle, the existing hydrodynamic power gear shifting transmission system is replaced, the stepless speed change is realized through the hydraulic pump 302 and the hydraulic motor, the power split is realized through the planetary mechanism, and the hydraulic and mechanical power coupling is performed on the hydraulic motor shaft module 4. Through the design, the embodiment can realize stepless speed regulation and parking reversing according to driving requirements, has no gear shifting impact, no power circulation, good operability and high operation efficiency, can control an engine to work at an optimal power point or an optimal oil consumption point according to resistance change in real time, improves the power performance or the fuel economy of the whole vehicle, has the advantages of hydraulic transmission and mechanical transmission, can still realize larger torque output when the rotating speed of the engine is low, and has good power performance, high transmission efficiency and even pure mechanical transmission under certain working conditions, and is good in energy conservation. The motor does not need to reverse during reversing, no power circulation is generated, and the overall efficiency is high.
Specifically, the input shaft module 1 includes an input driving gear 101, an input ring gear 102, an input planet carrier 103, an input planet gear 104 and an input sun gear 105, where the input driving gear 101 is used to connect with an output shaft of an engine to realize backward output of power provided by the engine, the input driving gear 101 is meshed with the power output shaft module 2, so as to facilitate the power input value power shaft module to realize power output, the input driving gear 101 is further coaxially connected with the input planet carrier 103 to realize power input, the input planet gear 104 is mounted on the input planet carrier 103, the input planet gear 104 is meshed with the input sun gear 105 and the input ring gear 102, and when the engine drives the input driving gear 101 to rotate, the input planet carrier 103 drives the input ring gear 102 and the input sun gear 105 to rotate, and meanwhile, the input planet gear 104 also rotates to realize power transmission.
The power output shaft module 2 includes a power output driven gear 201, the power output driven gear 201 is meshed with the input driving gear 101, and the power output driven gear 201 is mounted on a shaft of the power output shaft module 2 so as to achieve output of power.
The hydraulic pump shaft module 3 comprises a hydraulic pump driven gear 301 and a hydraulic pump 302, wherein the hydraulic pump driven gear 301 is meshed with the input annular gear 102, so that the hydraulic pump driven gear 301 rotates under the drive of the input annular gear 102 to realize power output, the hydraulic pump driven gear 301 is coaxially connected with the hydraulic pump 302, and an oil port of the hydraulic pump 302 is connected with two hydraulic motors through a pipeline.
The two hydraulic motors are a first hydraulic motor 401 and a second hydraulic motor 404 respectively, two oil ports of the first hydraulic motor 401 are connected with two oil ports of the hydraulic pump 302 respectively, two oil ports of the second hydraulic motor 404 are connected with two oil ports of the hydraulic pump 302 respectively, and the first hydraulic motor 401, the second hydraulic motor 404 and a motor shaft sun gear 405 are all coaxially connected, so that power output and power confluence are achieved.
The hydraulic pump 302 is a closed variable displacement plunger pump.
The forward planetary assembly comprises a forward planetary frame 409, a forward planetary gear 410 and a forward inner gear 411, the forward planetary gear 410 is mounted on the forward planetary frame 409, the backward planetary assembly comprises a backward planetary frame 406, a backward planetary gear 407 and a backward inner gear 408, the backward planetary gear 407 is mounted on the backward planetary frame 406, a motor shaft sun gear 405 is meshed with the forward planetary gear 410 and the backward planetary gear 407, a motor shaft driving gear 403 is connected with the forward planetary frame 409 and the backward inner gear 408, a forward clutch 412 is connected with the forward inner gear 411, a backward clutch 413 is connected with the backward planetary frame 406, so that a large torque can be provided when the vehicle runs at a low speed, a single hydraulic motor can be used for meeting the requirements of vehicle speed and traction force, the forward of the vehicle can be realized when each clutch is separated, the backward of the vehicle can be realized when the backward clutch 413 is combined, the vehicle runs at a highest speed, the displacement of the hydraulic pump 302 and the hydraulic motor can be regulated, the transmission efficiency of the transmission can be greatly improved, and the energy saving performance can be realized.
The output shaft module 5 includes an output shaft driven gear 501, the output shaft driven gear 501 meshing with the motor shaft drive gear 403.
The hydraulic motor is a variable displacement plunger motor of a diagonal shaft type.
Example two
The invention also provides a double-motor hydraulic mechanical stepless speed change transmission method, which uses the double-motor hydraulic mechanical stepless speed change transmission system of any one of the first embodiment, and comprises the following conditions:
neutral when both forward clutch 412 and reverse clutch 413 are disengaged;
when forward clutch 412 is engaged and reverse clutch 413 is disengaged, a forward gear is established, wherein:
when the hydraulic pump 302 has positive displacement and the first hydraulic motor 401 and the second hydraulic motor 404 both have positive rotation and reach the maximum displacement, the hydraulic pump is suitable for heavy-load low-speed running at the moment, and the power output is realized to be in forward motion of low-speed heavy load;
When the hydraulic pump 302 is positive in displacement and the displacement is gradually increased, the displacement of the first hydraulic motor 401 is gradually reduced until the displacement becomes zero, and the displacement of the second hydraulic motor 404 is gradually reduced, or when the hydraulic pump 302 is positive in displacement and the displacement is gradually increased, the displacement of the second hydraulic motor 404 is gradually reduced until the displacement becomes zero, and the displacement of the first hydraulic motor 401 is gradually reduced, the vehicle speed is gradually increased, and the power output is realized to be high-speed forward;
When the hydraulic pump 302 has positive displacement and maximum displacement, and the first hydraulic motor 401 and the second hydraulic motor 404 have zero displacement, the vehicle speed reaches the maximum, and the hydraulic transmission power is zero at the moment, so that the power output is realized to be purely mechanical transmission for advancing;
when the reverse clutch 413 is engaged, the forward clutch 412 is disengaged, which is a reverse gear, wherein;
when the hydraulic pump 302 is in positive displacement, the first hydraulic motor 401 and the second hydraulic motor 404 are in positive rotation, and the displacement reaches the maximum displacement, the hydraulic pump is suitable for heavy-load low-speed running, and the power output is realized to be in a low-speed heavy-load backward;
When the hydraulic pump 302 is positive in displacement and gradually increases in displacement, the displacement of the second hydraulic motor 404 is gradually reduced until becoming zero, and the displacement of the first hydraulic motor 401 is gradually reduced, or the displacement of the first hydraulic motor 401 is gradually reduced until becoming zero, and the displacement of the second hydraulic motor 404 is gradually reduced, the vehicle speed is gradually increased, and the power output is realized to be high-speed backward.
The principles and embodiments of the present invention have been described in detail with reference to specific examples, which are provided herein to facilitate understanding of the principles and embodiments of the present invention and to provide further advantages and practical applications for those of ordinary skill in the art in light of the present teachings. In view of the foregoing, this description should not be construed as limiting the invention.
Claims (10)
1. The hydraulic mechanical stepless speed change transmission system with the double motors is characterized by comprising an input shaft module, a power output shaft module, a hydraulic pump shaft module, a hydraulic motor shaft module and an output shaft module, wherein the input end of the input shaft module is used for being connected with an engine, the output end of the input shaft module is connected with the input end of the power output shaft module and the input end of the hydraulic pump shaft module, the output end of the power output shaft module is used for power output, the hydraulic motor shaft module comprises a motor shaft sun gear, a motor shaft driving gear, a motor shaft driven gear, a forward clutch, a backward clutch, a forward planetary assembly, a backward planetary assembly and two hydraulic motors, the motor shaft driven gear is meshed with the output end of the input shaft module, the motor shaft driven gear is coaxially connected with the two hydraulic motors, the two hydraulic motors are respectively connected with the input end of the motor shaft sun gear, the motor shaft sun gear is respectively meshed with the forward planetary assembly and the backward planetary assembly, the forward clutch is respectively connected with the forward planetary assembly and the backward planetary assembly, and the backward clutch is further connected with the forward planetary assembly and the forward planetary assembly.
2. The hydromechanical continuously variable transmission system according to claim 1, wherein the input shaft module includes an input driving gear, an input ring gear, an input carrier, an input planetary gear and an input sun gear, the input driving gear is used for connecting an output shaft of the engine, the input driving gear is meshed with the power output shaft module, the input driving gear is further coaxially connected with the input carrier, the input planetary gear is mounted on the input carrier, and the input planetary gear is meshed with the input sun gear and the input ring gear.
3. The hydromechanical continuously variable transmission system according to claim 2, wherein the power take-off module comprises a power take-off driven gear, the power take-off driven gear is meshed with the input drive gear, and the power take-off driven gear is mounted on a shaft of the power take-off module.
4. The hydraulic mechanical stepless speed change transmission system with two motors according to claim 2, wherein the hydraulic pump shaft module comprises a hydraulic pump driven gear and a hydraulic pump, the hydraulic pump driven gear is meshed with the input annular gear, the hydraulic pump driven gear is coaxially connected with the hydraulic pump, and an oil port of the hydraulic pump is connected with the two hydraulic motors through a pipeline.
5. The hydraulic mechanical stepless speed change transmission system with two motors according to claim 4, wherein the two hydraulic motors are a first hydraulic motor and a second hydraulic motor respectively, two oil ports of the first hydraulic motor are connected with two oil ports of the hydraulic pump respectively, two oil ports of the second hydraulic motor are connected with two oil ports of the hydraulic pump respectively, and the first hydraulic motor, the second hydraulic motor and the motor shaft sun gear are all coaxially connected.
6. The hydraulic mechanical stepless speed change transmission system with double motors according to claim 4, wherein the hydraulic pump is a closed variable plunger pump.
7. The hydraulic mechanical stepless speed change transmission system with double motors according to claim 1, wherein the forward planetary assembly comprises a forward planetary frame, a forward planetary gear and a forward internal gear ring, the forward planetary gear is mounted on the forward planetary frame, the backward planetary assembly comprises a backward planetary frame, a backward planetary gear and a backward internal gear ring, the backward planetary gear is mounted on the backward planetary frame, the motor shaft sun gear is meshed with the forward planetary gear and the backward planetary gear, the motor shaft driving gear is connected with the forward planetary frame and the backward internal gear ring, the forward clutch is connected with the forward internal gear ring, and the backward clutch is connected with the backward planetary frame.
8. The hydromechanical continuously variable transmission system according to claim 1, wherein the output shaft module includes an output shaft driven gear, the output shaft driven gear being meshed with the motor shaft driving gear.
9. The hydromechanical continuously variable transmission system with dual motors according to claim 1, wherein the hydraulic motor is a variable displacement plunger motor with a tilt shaft.
10. A double-motor hydraulic mechanical stepless speed change transmission method, which is characterized in that the double-motor hydraulic mechanical stepless speed change transmission system according to any one of claims 1-9 is used, comprising the following conditions:
when the forward clutch and the backward clutch are both separated, the clutch is in neutral gear;
When the forward clutch is engaged and the reverse clutch is disengaged, the forward gear is selected, wherein:
When the hydraulic pump has positive displacement and the first hydraulic motor and the second hydraulic motor rotate positively and reach the maximum displacement, the hydraulic pump is suitable for heavy-load low-speed running at the moment, and the power output is realized to be low-speed heavy-load forward;
When the positive displacement and the displacement of the hydraulic pump are gradually increased, the displacement of the first hydraulic motor is gradually reduced until the displacement of the first hydraulic motor becomes zero, and the displacement of the second hydraulic motor is gradually reduced, or when the positive displacement and the displacement of the hydraulic pump are gradually increased, the displacement of the second hydraulic motor is gradually reduced until the displacement of the second hydraulic motor becomes zero, and the displacement of the first hydraulic motor is gradually reduced, the speed of the vehicle is gradually increased, and the power output is realized to be high-speed forward;
When the hydraulic pump has positive displacement and maximum displacement, and the first hydraulic motor box and the second hydraulic motor have zero displacement, the vehicle speed reaches the maximum, and the hydraulic transmission power is zero at the moment, so that the power output is realized to be purely mechanical transmission and advance;
When the reverse clutch is engaged and the forward clutch is disengaged, the gear is a reverse gear, wherein;
When the hydraulic pump is in positive displacement, the first hydraulic motor and the second hydraulic motor are in positive rotation, and the displacement reaches the maximum displacement, the hydraulic pump is suitable for heavy-load low-speed running, and the power output is realized to be in low-speed heavy-load backward;
when the hydraulic pump is positive in displacement and the displacement is gradually increased, the displacement of the second hydraulic motor is gradually reduced until the displacement becomes zero,
When the first hydraulic motor displacement is gradually reduced, or the first hydraulic motor displacement is gradually reduced until becoming zero,
When the displacement of the second hydraulic motor is gradually reduced, the speed of the vehicle is gradually increased, and the power output is realized to be high-speed backward.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202411527719.0A CN119123024A (en) | 2024-10-30 | 2024-10-30 | Dual-motor hydraulic mechanical continuously variable transmission system and method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202411527719.0A CN119123024A (en) | 2024-10-30 | 2024-10-30 | Dual-motor hydraulic mechanical continuously variable transmission system and method |
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| CN119123024A true CN119123024A (en) | 2024-12-13 |
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| CN202411527719.0A Pending CN119123024A (en) | 2024-10-30 | 2024-10-30 | Dual-motor hydraulic mechanical continuously variable transmission system and method |
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| CN (1) | CN119123024A (en) |
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2024
- 2024-10-30 CN CN202411527719.0A patent/CN119123024A/en active Pending
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