CN117780888A - HMT mechanical hydraulic stepless speed changing box for tractor - Google Patents
HMT mechanical hydraulic stepless speed changing box for tractor Download PDFInfo
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Abstract
The invention relates to the technical field of power transmission, in particular to an HMT mechanical hydraulic stepless speed-changing box of a tractor. The hydraulic power transmission system is used for providing stepless hydraulic power of the speed-crossing box, and the stepless hydraulic power is input into the engine part power through the gear set I and is transmitted to the planetary reduction mechanism through the gear set II; the wet mechanical power transmission system is used for providing mechanical power for switching forward and backward directions, inputting partial power of the engine through the gear set I and transmitting the partial power to the planetary reduction mechanism through the gear set II; the planetary reduction mechanism is used for converging the power of the hydraulic power transmission system and the mechanical system; the gearbox system is used for controlling gear shifting of the gearbox in a linkage manner with the mechanical power transmission system, and stepless control of four gears in the forward and backward directions is achieved. The invention has simple and compact structure by optimizing the power transmission system; the planetary reduction mechanism utilizes hydraulic and mechanical power to meet the requirements of frequent forward and backward movement and speed adjustment of the tractor.
Description
Technical Field
The invention relates to the technical field of power transmission, in particular to a tractor HMT mechanical hydraulic stepless speed changing box.
Background
The tractor needs to cope with various working conditions, including heavy-load plowing and ridging operation, medium-load plant protection operation and the like. To meet these diverse demands, continuously variable transmission is an ideal choice, providing more work gears for the tractor. In order to ensure that the tractor can obtain stable and continuous power output under various terrains and working conditions, the working efficiency and performance are further improved, and a series of improvements are made by the person skilled in the art. For example, chinese patent CN115750717a discloses a three-stage Continuously Variable Transmission (CVT) for a tractor, in which the working stages can be continuously variable, the speed of the hydraulic pump motor element is continuously variable, the clutch has no speed difference, the operation of shifting the stages is simple, the transmission efficiency is high, and the required power of the hydraulic pump motor element is small, the volume is small, and the cost is controllable. However, the scheme is complex in structure and not compact enough, and the manufacturing cost and the maintenance difficulty are increased; only a fixed gear shifting mode is supported, and automatic or manual mode switching cannot be performed according to actual requirements; speed adjustment and directional control may not be smooth enough, resulting in reduced operating efficiency.
Disclosure of Invention
The invention aims to solve the technical problems that: overcomes the defects of the prior art and provides the HMT mechanical hydraulic stepless speed changing box of the tractor.
The technical scheme of the invention is as follows:
a tractor HMT mechanical hydraulic continuously variable transmission comprising the following components:
the hydraulic power transmission system is used for providing stepless hydraulic power of the speed-crossing box, inputting partial power of the engine through the gear set I and transmitting the partial power to the planetary reduction mechanism through the gear set II;
the mechanical power transmission system is used for providing mechanical power for switching forward and backward directions, adopts a wet clutch, inputs partial power of the engine through a gear set I and transmits the partial power to the planetary reduction mechanism through a gear set II;
the planetary speed reducing mechanism is used for converging the power of the hydraulic power transmission system and the mechanical power transmission system and transmitting the power to the gearbox system through the gear set III;
the gearbox system is used for controlling gear shifting of the gearbox in a linkage manner with the mechanical power transmission system, and four-section gear shifting is adopted to realize stepless control of four gears in the forward direction and the backward direction.
According to the technical scheme, through improving the connection structure of the hydraulic power transmission system, the mechanical power transmission system, the planetary reduction mechanism and the gearbox system, continuous speed change in the speed change process is realized by utilizing hydraulic and mechanical power, and the requirements of frequent forward and backward movement and speed adjustment of the tractor are met. The improved technical scheme can provide continuous speed change and accurate direction switching, so that the tractor is excellent in farmland operation. Wherein: the hydraulic power transmission system inputs part of power of the engine into the hydraulic power transmission system through a precise gear set I; the stepless hydraulic power is further processed and converted by a motor and is transmitted to a planetary reduction mechanism through a gear set II; in practice, this allows the tractor to achieve a smooth, continuous power output over a wide variety of complex terrain and operating conditions. The mechanical power transmission system is responsible for providing mechanical power for switching forward and backward directions, the switching function is realized through a wet clutch, and the wet clutch can bear larger torque, so that the situation of slipping or power interruption in the switching process is avoided; the mechanical power transmission system also obtains partial power of the engine through the gear set I, and then transmits the mechanical power to the planetary reduction mechanism through the gear set II. The planetary reduction mechanism plays a role of a transmission mechanism, gathers all power of the hydraulic power transmission system and the mechanical power transmission system, and transmits the power to the gearbox system through the gear set III through the transmission effect of the planetary reduction mechanism; in practice, this allows the tractor to flexibly distribute and adjust the power output of each section according to the work requirements. The gearbox system is linked with the mechanical power transmission system to jointly control gear shifting of the gearbox; during shifting in running, the electric control system adjusts the optimal speed of hydraulic output according to the input speed and the output speed, so that the shifting process is smoother, and the impact and vibration caused by shifting are reduced. The gearbox system adopts a four-section gear shifting design, so that the stepless control of four gears in the forward and backward directions can be realized; in practical application, the operation convenience and the operation efficiency of the tractor are greatly improved. No matter whether cultivation, sowing or harvesting is carried out, the four-section mechanical hydraulic hybrid power stepless speed-crossing box can enable the tractor to exert the maximum efficiency under various working conditions.
In some of these embodiments, the engine transmits power to gear set I through a torsional vibration damper; the gear set I comprises an idler wheel connected with the engine, a gear I connected with the hydraulic power transmission system and a gear II connected with the mechanical power transmission system.
In the technical scheme, the torsional damper is used for reducing vibration and noise generated by an engine, ensuring stability of power transmission and preventing unnecessary damage to the gear set I. The gear set I is directly connected with the engine, is meshed with the hydraulic power transmission system and the mechanical power transmission system, and realizes the transmission of the engine power and the hydraulic power and the mechanical power through the gear set I.
In some of these embodiments, the hydraulic power transfer system includes an electric proportioning pump and a motor, the electric proportioning pump converting mechanical power to hydraulic pressure and transferring to the motor; the motor transmits the stepless hydraulic power to the gear ring of the planetary reduction mechanism through the gear set II.
In the technical scheme, the electric proportional pump converts the input mechanical power into hydraulic power, and adjusts the output hydraulic flow according to the control signal, so that the stepless regulation of the power is realized, and the electric proportional pump has the characteristics of quick response, high precision and continuous adjustability. The motor is used as an executive component of the hydraulic power transmission system, converts the hydraulic power output by the electric proportional pump into mechanical power, and transmits the mechanical power to the gear ring of the planetary reduction mechanism through the gear set II, and the motor ensures that the gearbox can obtain stable output torque and speed in different working environments. The planetary reduction mechanism plays a role in collecting and transmitting power, and is tightly matched with the motor, the planetary reduction mechanism transmits stepless hydraulic power to the gear ring, and high-strength torque and traction force are effectively dispersed and transmitted through interaction with the sun gear and the planet gear, so that stable operation under complex working conditions is ensured, and mechanical faults and abrasion caused by high-strength operation are reduced.
In some of these embodiments, the wet clutch of the mechanical power transmission system includes a forward clutch that switches the forward direction, a reverse clutch that switches the reverse direction; the forward clutch/reverse clutch transfers mechanical power through gear set ii to the sun gear of the planetary reduction mechanism.
In the technical scheme, the forward clutch and the backward clutch are two parts in the wet clutch, so that the requirement of frequently switching forward and backward is met; by using the wet clutch, an operator can more easily and stably control the speed and the direction of the tractor, so that the working efficiency is improved; the forward clutch/backward clutch transmits the mechanical power of the engine to the sun gear of the planetary reduction mechanism through a gear set II; the output torque and speed can be adjusted according to actual needs through the sun gear of the planetary reduction mechanism, so that stable and efficient operation under various conditions is ensured. When the gear shifting action is carried out by matching with the electric control gear shifting, the wet clutch is opened, and the wet clutch is slowly combined after the gear is shifted, so that the smooth speed transition of the whole machine is realized.
In some embodiments, the planetary reduction mechanism is a three-element transmission mechanism and comprises a gear ring, a sun gear and a planetary carrier, wherein the gear ring transmits the stepless hydraulic power and the mechanical power to the planetary carrier after converging; the planet carrier transmits the hydraulic hybrid power to the gearbox through a gear set III.
In the technical scheme, the gear ring is used for receiving stepless hydraulic power from the hydraulic power transmission system; the sun gear is used for receiving mechanical power of the mechanical power transmission system; the planetary carrier is a junction point, and two kinds of power, namely stepless hydraulic power and mechanical power, are collected and transmitted in a coordinated and consistent manner; the planetary reduction mechanism combines the advantages of hydraulic pressure, machinery and planetary gears, and realizes the combination and efficient transmission of power; the planetary reduction mechanism can accurately adjust the output speed and power according to actual demands, ensures that the tractor can accurately reach a designated position in the operation process, and maintains stable speed. The mechanical and hydraulic transmission is a parallel transmission route, so that the transmission efficiency is high, stepless speed change can be realized, the operation comfort is improved, and the oil consumption is reduced.
In some of these embodiments, the gearbox system comprises the following gears:
the neutral gear, the first gear and the second gear are respectively connected with a synchronizer I driven by an oil cylinder I, wherein the oil cylinder I pushes the synchronizer I to be neutral in center, to be left in the first gear and to be right in the second gear;
the neutral gear, the III gear and the IV gear are respectively connected with a synchronizer II driven by an oil cylinder II, wherein the oil cylinder II pushes the synchronizer II to be neutral in center, to be the III gear on the left and to be the IV gear on the right.
According to the technical scheme, the oil cylinder pushes the synchronizer to move leftwards or rightwards through the cooperation of the oil cylinder and the synchronizer so as to select the corresponding gear, and the adjustment of the power transmission direction and speed is realized. The oil cylinder I is matched with the synchronizer I to realize the switching among neutral gear, I gear and II gear; the oil cylinder II is matched with the synchronizer II to realize the switching of neutral gear, III gear and IV gear. It should be noted that; the four gears exist in both the forward direction and the backward direction, and the four-stage structure is also realized. For example, a lower gear is selected to obtain greater traction during work and hill climbing, and a higher gear is selected to control speed during transition.
In some embodiments, the transmission system is controlled in linkage with the mechanical power transmission system, and the mechanical power transmission system is in a separated state when the gear of the transmission system is switched; when the gear of the transmission system is switched, the mechanical power transmission system is in a closed state.
In the technical scheme, as the gearbox system is provided with a plurality of groups of gears, the gearbox is cut off firstly in the process of gear switching every time, and then the gears can be switched; and closing the clutch after the switching is finished. The whole linkage process time is very short, and an operator can quickly and stably switch gears and simultaneously ensure the stable transmission of power in the switching process. The linkage control is realized by adopting hardware such as keys, buttons, handles and the like arranged in a cab.
The gearbox system may implement a split shift: the multifunctional handle is integrated with a gear selecting button, and the wet clutch and the gear shifting mechanism are electrically controlled to be matched, so that the gear shifting between the static state and the driving state is realized;
the gearbox system can realize full-course automatic gear shifting: the corresponding mechanical gear and hydraulic power will be given according to the set speed; simultaneously controlling corresponding mechanical gear and hydraulic pump displacement according to the load size;
the gearbox system may implement manual mode shifting: the manual gear selection can be performed according to the requirement of an operator to perform gear shifting;
the gearbox system can realize manual-automatic mode shifting: the manual button shift can be performed and the automatic shift can be performed.
The speed control of the multifunctional handle can be realized by the gearbox system: the size of the pushing handle is used for controlling the acceleration (deceleration) of the vehicle speed, the residence time is used for controlling the final vehicle speed, the middle position is the position where the acceleration is zero, and the vehicle speed is kept; otherwise, the speed is reduced, and the device is kept or stopped.
In some of these embodiments, the transmission system is further coupled to the following components:
the PTO clutch is used for providing mechanical power for switching high and low gears, inputting partial power of the planetary reduction mechanism through the gear set III, and performing high and low gears through the high and low gear transmission so as to drive different loads;
the differential mechanism is used for adjusting the rotating speeds of the tires at two sides during turning, inputting partial power through a gearbox system and decelerating through a planetary mechanism so as to drive the tires to turn;
and the driving gearbox is used for providing mechanical power for switching four-wheel drive sources, inputting partial power of the planetary reduction mechanism through the gear set IV and selecting and mounting different drive sources.
In the technical scheme, when the load driving force of the tractor is insufficient, the PTO clutch receives mechanical power from the gearbox system, so that the device can select proper gears according to different load demands, and the optimal power output can be obtained under various operation conditions; when the tractor turns, the differential mechanism receives part of power from the gearbox system and decelerates through the planetary mechanism, so that tires on two sides can rotate at proper speed during turning, and the stability and safety of turning are improved. The gearbox is driven, different driving sources can be selected and mounted, a rear-drive mode is selected under normal conditions, and a lower four-drive mode can be selected under special conditions, for example, on a muddy or wet road surface so as to improve traction; on a flat road surface, a higher four-wheel drive mode can be selected to increase the working speed.
Compared with the prior art, the invention has the following beneficial effects:
(1) The hydraulic power transmission system and the mechanical power transmission system are optimized, so that the structure is simple and compact; the planetary reduction mechanism utilizes hydraulic and mechanical power to realize continuous speed change of the gearbox system, and meets the requirements of frequent forward and backward movement and speed adjustment of the tractor;
(2) The wet clutch utilizes the forward clutch and the backward clutch to meet the requirement of frequently switching forward and backward, so that the speed and the direction of the tractor are controlled more easily and stably, and the working efficiency is improved;
(3) The gearbox system adopts a four-section structure and is matched with a mechanical power transmission system controlled in a linkage manner, so that four gears are arranged in the forward direction or the backward direction; therefore, various modes such as full-course automatic shifting, sectional shifting, manual mode shifting, manual-automatic mode shifting and multifunctional handle speed control are realized.
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 required to be used in the description of the embodiments or the prior art will be briefly described below, and it will be obvious to those skilled in the art that other drawings can be obtained from these drawings without inventive effort.
Fig. 1 is an electrical diagram of the entire present invention.
Fig. 2 is an electrical diagram of a hybrid continuously variable transmission.
Fig. 3 is a power transmission line diagram of the entire present invention.
Fig. 4 is one of the power transmission line diagrams of the hybrid continuously variable transmission.
Fig. 5 is a second power transmission line diagram of the hybrid continuously variable transmission.
Fig. 6 is a shift position switching state diagram of the present invention.
In the figure: 1. an engine; 2. a torsional damper; 3. a gear set I; 4. a hydraulic power transmission system; 41. an electric proportional pump; 42. a motor; 5. a gear set II; 6. a mechanical power transmission system; 61. a forward clutch; 62. retracting the clutch; 7. a planetary reduction mechanism; 71. a gear ring; 72. a sun gear; 73. a planet carrier; 8. a gear set III; 9. a transmission system; 91. an oil cylinder I; 92. an oil cylinder II; 93. a synchronizer I; 94. a synchronizer II; 95. a gear I; 96. gear II; 97. III gear; 98. IV gear; 10. a PTO clutch; 11. a differential; 12. a planetary mechanism; 13. a tire; 14. a high-low gear gearbox; 15. the gearbox is driven.
Detailed Description
In order to make the technical solution of the present invention better understood by those skilled in the art, the technical solution of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention, and it is apparent that the described embodiments are only some embodiments of the present invention, not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the present invention without making any inventive effort, shall fall within the scope of the present invention.
Example 1
As shown in fig. 1 to 5, the present embodiment provides a tractor HMT mechanical hydraulic continuously variable transmission, including the following components:
a hydraulic power transmission system 4 for providing a stepless hydraulic power of the speed-changing box, which inputs part of the power of the engine 1 through a gear set I3 and transmits the part of the power to a planetary reduction mechanism 7 through a gear set II 5;
a mechanical power transmission system 6 for providing mechanical power for switching forward and backward directions, wherein a wet clutch is adopted, part of power of the engine 1 is input through a gear set I3, and the power is transmitted to a planetary reduction mechanism 7 through a gear set II 5;
a planetary reduction mechanism 7 for collecting the power of the hydraulic power transmission system 4 and the mechanical power transmission system 6 and transmitting the power to a gearbox system 9 through a gear set III 8;
the gearbox system 9 is used for controlling gear shifting of the gearbox in a linkage manner with the mechanical power transmission system 6, and four-stage gear shifting is adopted to realize stepless control of four gears in the forward and backward directions.
As shown in fig. 1 to 5, the present technical solution realizes continuous speed change in the speed change process by improving the connection structures of the hydraulic power transmission system 4, the mechanical power transmission system 6, the planetary reduction mechanism 7 and the gearbox system 9, and simultaneously utilizing hydraulic and mechanical power, thereby meeting the requirements of frequent forward and backward movement and speed adjustment of the tractor. The improved technical scheme can provide continuous speed change and accurate direction switching, so that the tractor is excellent in farmland operation. Wherein: the hydraulic power transmission system 4 inputs part of power of the engine 1 into the hydraulic power transmission system 4 through a precise gear set I3; the stepless hydraulic power is further processed and converted by a motor 42 and is transmitted to the planetary reduction mechanism 7 through a gear set II 5; in practice, this allows the tractor to achieve a smooth, continuous power output over a wide variety of complex terrain and operating conditions. The mechanical power transmission system 6 is responsible for providing mechanical power for switching forward and backward directions, the switching function is realized by a wet clutch, and the wet clutch can bear larger torque, so that the situation of slipping or power interruption in the switching process is avoided; the mechanical power transmission system 6 also obtains part of the power of the engine 1 through the gear set I3, and then transmits the mechanical power to the planetary reduction mechanism 7 through the gear set II 5. The planetary reduction mechanism 7 plays a role of a transmission mechanism, gathers all power of the hydraulic power transmission system 4 and the mechanical power transmission system 6, and transmits the power to the gearbox system 9 through the gear set III 8 through the transmission function of the planetary reduction mechanism 7; in practice, this allows the tractor to flexibly distribute and adjust the power output of each section according to the work requirements. The gearbox system 9 is linked with the mechanical power transmission system 6 and jointly controls gear shifting of the gearbox; the linkage control mode enables the gear shifting process to be smoother, and impact and vibration caused by gear shifting are reduced. The gearbox system 9 adopts a four-section gear shifting design, so that the stepless control of four gears in the forward and backward directions can be realized; in practical application, the operation convenience and the operation efficiency of the tractor are greatly improved. No matter whether cultivation, sowing or harvesting is carried out, the four-section mechanical hydraulic hybrid power stepless speed-crossing box can enable the tractor to exert the maximum efficiency under various working conditions.
In some of these embodiments, the engine 1 transmits power to the gear set I3 through the torsional vibration damper 2; the gear set I3 includes an idler gear coupled to the engine 1, a gear I coupled to the hydraulic power transfer system 4, and a gear II coupled to the mechanical power transfer system 6.
In this technical scheme, torsional damper 2 is used for reducing vibration and noise that engine 1 produced, ensures the stationarity of power transmission, prevents to cause unnecessary harm to gear train I3. The gear set I3 is directly connected with the engine 1, is meshed with the hydraulic power transmission system 4 and the mechanical power transmission system 6, and realizes the transmission of the power, the hydraulic power and the mechanical power of the engine 1 through the gear set I3.
In some of these embodiments, the hydraulic power transmission system 4 includes an electric proportioning pump 41 and a motor 42, the electric proportioning pump 41 converting mechanical power into hydraulic pressure and transmitting to the motor 42; the motor 42 transmits stepless hydraulic power to the ring gear 71 of the planetary reduction mechanism 7 through the gear set ii 5.
In the present solution, the electric proportional pump 41 converts the input mechanical power into hydraulic power, and adjusts the output hydraulic flow according to the control signal, so as to realize stepless adjustment of the power, and has the characteristics of quick response, high precision and continuous adjustability. The motor 42 is used as an actuator of the hydraulic power transmission system 4, converts the hydraulic power output by the electric proportional pump 41 into mechanical power, and transmits the mechanical power to the gear ring 71 of the planetary reduction mechanism 7 through the gear set II 5, and the motor 42 ensures that the gearbox can obtain stable output torque and speed in different working environments. The planetary reduction mechanism 7 plays a role in collecting and transmitting power, the planetary reduction mechanism 7 transmits stepless hydraulic power to the gear ring 71 through close fit with the motor 42, high-strength torque and traction force are effectively dispersed and transmitted through interaction with the sun gear 72 and the planet gears, stable operation under complex working conditions is ensured, and mechanical faults and abrasion caused by high-strength operation are reduced.
As shown in fig. 4 and 5, the wet clutch of the mechanical power transmission system 6 includes a forward clutch 61 for switching the forward direction and a reverse clutch 62 for switching the reverse direction; the forward clutch 61/reverse clutch 62 transmits mechanical power to the sun gear 72 of the planetary reduction mechanism 7 through the gear set ii 5.
In the present solution, the forward clutch 61 and the reverse clutch 62 are two parts of the wet clutch, and meet the need of frequently switching between forward and reverse; by using the wet clutch, an operator can more easily and stably control the speed and the direction of the tractor, so that the working efficiency is improved; the forward clutch 61/reverse clutch 62 transmits the mechanical power of the engine 1 to the sun gear 72 of the planetary reduction mechanism 7 through the gear set ii 5; the sun gear 72 of the planetary reduction mechanism 7 can adjust the output torque and speed according to actual needs, and ensure stable and efficient operation under various conditions. When the gear shifting action is carried out by matching with the electric control gear shifting, the wet clutch is opened, and the wet clutch is slowly combined after the gear is shifted, so that the smooth speed transition of the whole machine is realized.
In some embodiments, the planetary reduction mechanism 7 is a three-element transmission mechanism, and comprises a gear ring 71, a sun gear 72 and a planetary carrier 73, wherein the gear ring 71 combines stepless hydraulic power and the sun gear 72 to transmit mechanical power to the planetary carrier 73; the planet carrier 73 transfers hydraulic hybrid power to the gearbox through the gear set iii 8.
In the present embodiment, the ring gear 71 is configured to receive stepless hydraulic power from the hydraulic power transmission system 4; sun gear 72 is configured to receive mechanical power from mechanical power transmission system 6; the planet carrier 73 is a junction point, and gathers the two kinds of power of stepless hydraulic power and mechanical power and transmits out in a coordinated and consistent way; the planetary reduction mechanism 7 combines the advantages of hydraulic pressure, machinery and planetary gears, and realizes the combination and efficient transmission of power; the planetary reduction mechanism 7 can accurately adjust the output speed and power according to actual demands, ensure that the tractor can accurately reach a designated position in the operation process, and maintain a stable speed. The mechanical and hydraulic transmission is a parallel transmission route, so that the transmission efficiency is high, stepless speed change can be realized, the operation comfort is improved, and the oil consumption is reduced.
As shown in fig. 6, the gearbox system 9 comprises the following gears:
the neutral gear, the I gear 95 and the II gear 96 are respectively connected with a synchronizer I93 driven by an oil cylinder I91, wherein the oil cylinder I91 pushes the synchronizer I93 to be neutral in center, to be left as the I gear 95 and to be right as the II gear 96;
the neutral gear, the III gear 97 and the IV gear 98 are respectively connected with a synchronizer II 94 driven by an oil cylinder II 92, wherein the oil cylinder II 92 pushes the synchronizer II 94 to be neutral, left-located in the neutral gear 97 and right-located in the IV gear 98.
According to the technical scheme, the oil cylinder pushes the synchronizer to move leftwards or rightwards through the cooperation of the oil cylinder and the synchronizer so as to select the corresponding gear, and the adjustment of the power transmission direction and speed is realized. The oil cylinder I91 is matched with the synchronizer I93 to realize the switching among neutral gear, I gear 95 and II gear 96; the oil cylinder II 92 is matched with the synchronizer II 94 to realize the switching of neutral gear, III gear 97 and IV gear 98. It should be noted that; the four gears exist in both the forward direction and the backward direction, and the four-stage structure is also realized. For example, a lower gear is selected to obtain greater traction during work and hill climbing, and a higher gear is selected to control speed during transition.
In some embodiments, the transmission system 9 is controlled in linkage with the mechanical power transmission system 6, and when the gear of the transmission system 9 is switched, the mechanical power transmission system 6 is in a separated state; when the gear of the gearbox system 9 is switched, the mechanical power transmission system 6 is in a closed state.
In the technical scheme, as the gearbox system 9 is provided with a plurality of groups of gears, the gearbox is cut off firstly in the process of each gear switching, and then the gears can be switched; and closing the clutch after the switching is finished. The whole linkage process time is very short, and an operator can quickly and stably switch gears and simultaneously ensure the stable transmission of power in the switching process. The linkage control is realized by adopting software and hardware such as keys, buttons, handles, controllers and the like which are arranged in a cab.
The gearbox system 9 may implement a step shift: the multifunctional handle is integrated with a gear selecting button, and the wet clutch and the gear shifting mechanism are electrically controlled to be matched, so that the gear shifting between the static state and the driving state is realized;
the gearbox system 9 can realize full automatic gear shifting: the corresponding mechanical gear and hydraulic power will be given according to the set speed; simultaneously controlling corresponding mechanical gear and hydraulic pump displacement according to the load size;
the gearbox system 9 may implement manual mode shifting: the manual gear selection can be performed according to the requirement of an operator to perform gear shifting;
the transmission system 9 may implement manual-automatic mode shifting: the manual button shift can be performed and the automatic shift can be performed.
The gearbox system 9 can realize the speed control of the multifunctional handle: the size of the pushing handle is used for controlling the acceleration (deceleration) of the vehicle speed, the residence time is used for controlling the final vehicle speed, the middle position is the position where the acceleration is zero, and the vehicle speed is kept; otherwise, the speed is reduced, and the device is kept or stopped.
In some of these embodiments, the gearbox system 9 is also connected to the following components:
a PTO clutch 10 for providing mechanical power for shifting up and down, inputting partial power of the planetary reduction mechanism 7 through the gear set iii 8, and performing up and down shift through the high and low shift gearbox 14 to drive different loads;
a differential 11 for adjusting the rotational speed of the tires 13 on both sides when turning, inputting part of power through the transmission system 9, and decelerating through the planetary mechanism 12 to drive the tires 13 to turn;
the driving gearbox 15 is used for providing mechanical power for switching four-wheel drive sources, inputting partial power of the planetary reduction mechanism 7 through the gear set IV, and selecting and mounting different driving sources.
In the technical scheme, when the load driving force of the tractor is insufficient, the PTO clutch 10 receives mechanical power from the gearbox system 9, so that the device can select proper gears according to different load demands, and the optimal power output can be obtained under various working conditions; when the tractor is in a turning operation, the differential 11 receives part of the power from the gearbox system 9 and decelerates through the planetary mechanism 12, ensuring that the tires 13 on both sides can rotate at a proper speed during the turning, thereby improving the stability and safety of the turning. The gearbox 15 is driven and can choose to mount different driving sources, a rear drive mode is usually chosen, and in special cases, for example, on a muddy or slippery road surface, a lower four-drive mode can be chosen to improve traction; on a flat road surface, a higher two-drive mode can be selected to increase the working speed.
The use process of the above embodiment is as follows:
as shown in fig. 1 to 6, after the transmitter is started, and power is transmitted to the gear set i 3 through the torsional damper 2, the power is divided into two paths in parallel:
one path of the mechanical power is converted into hydraulic power by the electric proportional pump 41 through the hydraulic power transmission system 4 and is transmitted to the motor 42; the motor 42 receives the stepless hydraulic power and transmits it to the ring gear 71 of the planetary reduction mechanism 7 through the gear set ii 5;
the other path is transmitted to a sun gear 72 of the planetary reduction mechanism 7 through a mechanical power transmission system 6, and the forward clutch 61/backward clutch 62 is transmitted to the planetary reduction mechanism through a gear set II 5;
the two paths are connected in parallel and are converged to a planetary carrier 73, and the planetary carrier 73 receives stepless hydraulic power transmitted by a gear ring 71 and mechanical power transmitted by a sun gear 72 respectively; the carrier 73 transmits the combined power to the mechanical power transmission system 6;
when gear shifting is realized through keys, buttons and handles, the gearbox system 9 and the mechanical power transmission system 6 are controlled in a linkage mode, so that the mechanical power transmission system 6 is in a separated state when gear shifting is achieved, and is in a closed state after the gear shifting is completed.
For example, the cylinder I91 is actuated to shift the synchronizer I93 between neutral, I gear 95, and II gear 96. The mechanical power transmission system 6 is separated, and the oil cylinder I91 pushes the synchronizer I93 to be switched from neutral to the I gear 95; the mechanical power transmission system 6 is closed and the power of the planet carrier 73 is transmitted to the gear shifting mechanism through the gear set iii 8 and drives the PTO clutch 10, the differential 11 and the drive gearbox 15 in motion.
Although the present invention has been described in detail by way of preferred embodiments with reference to the accompanying drawings, the present invention is not limited thereto. Various equivalent modifications and substitutions may be made in the embodiments of the present invention by those skilled in the art without departing from the spirit and scope of the present invention, and it is intended that all such modifications and substitutions be within the scope of the present invention/be within the scope of the present invention as defined by the appended claims. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.
Claims (8)
1. A tractor HMT mechanical hydraulic continuously variable transmission comprising the following components:
the hydraulic power transmission system (4) is used for providing stepless hydraulic power of the speed-changing box, inputting partial power of the engine (1) through the gear set I (3) and transmitting the partial power to the planetary reduction mechanism (7) through the gear set II (5);
a mechanical power transmission system (6) for providing mechanical power for switching forward and backward directions, wherein a wet clutch is adopted, partial power of the engine (1) is input through a gear set I (3), and the partial power is transmitted to a planetary reduction mechanism (7) through a gear set II (5);
a planetary reduction mechanism (7) for collecting the power of the hydraulic power transmission system (4) and the mechanical power transmission system (6) and transmitting the power to a gearbox system (9) through a gear set III (8);
and the gearbox system (9) is used for controlling gear shifting of the gearbox in a linkage manner with the mechanical power transmission system (6), and four-stage gear shifting is adopted to realize stepless control of four gears in the forward and backward directions.
2. The tractor HMT mechanical hydraulic continuously variable transmission according to claim 1, characterized in that the engine (1) transmits power to the gear set i (3) through a torsional damper (2); the gear set I (3) comprises an idler wheel connected with the engine (1), a gear I connected with the hydraulic power transmission system (4) and a gear II connected with the mechanical power transmission system (6).
3. The tractor HMT mechanical hydraulic continuously variable transmission according to claim 2, characterized in that said hydraulic power transmission system (4) comprises an electric proportional pump (41) and a motor (42), the electric proportional pump (41) converting mechanical power into hydraulic pressure and transmitting it to the motor (42); the motor (42) transmits the stepless hydraulic power to the gear ring (71) of the planetary reduction mechanism (7) through the gear set II (5).
4. A tractor HMT mechanical hydraulic continuously variable transmission according to claim 3, characterized in that the wet clutch of the mechanical power transmission system (6) comprises a forward clutch (61) switching the forward direction, a reverse clutch (62) switching the reverse direction; the forward clutch (61)/reverse clutch (62) transmits mechanical power through gear set II (5) to the sun gear (72) of the planetary reduction mechanism (7).
5. The tractor HMT mechanical-hydraulic continuously variable transmission according to claim 4, characterized in that the planetary reduction mechanism (7) is a three-element transmission mechanism comprising a gear ring (71), a sun gear (72) and a planet carrier (73), the gear ring (71) transmitting the stepless hydraulic power, the sun gear (72) converging the mechanical power and then transmitting the mechanical power to the planet carrier (73); the planet carrier (73) transmits the hydraulic hybrid power to the gearbox through the gear set III (8).
6. The tractor HMT mechanical hydraulic continuously variable transmission according to claim 1, characterized in that the transmission system (9) comprises the following gears:
the neutral gear, the I gear (95) and the II gear (96) are respectively connected with a synchronizer I (93) driven by an oil cylinder I (91), wherein the oil cylinder I (91) pushes the synchronizer I (93) to be neutral in center, left in the neutral gear, the I gear (95) and right in the II gear (96);
the neutral gear, the III gear (97) and the IV gear (98) are respectively connected with a synchronizer II (94) driven by an oil cylinder II (92), wherein the oil cylinder II (92) pushes the synchronizer II (94) to be neutral in center, to be left in the III gear (97) and to be right in the IV gear (98).
7. The tractor HMT mechanical hydraulic continuously variable transmission according to claim 1 or 6, characterized in that the transmission system (9) is controlled in linkage with the mechanical power transmission system (6), the mechanical power transmission system (6) being in a disengaged state when the transmission system (9) is shifted in gear; when the gear of the gearbox system (9) is switched, the mechanical power transmission system (6) is in a closed state.
8. The tractor HMT mechanical hydraulic continuously variable transmission according to claim 7, characterized in that the transmission system (9) is further connected with:
a PTO clutch (10) for providing mechanical power for switching between high and low gears, inputting partial power of the planetary reduction mechanism (7) through a gear set III (8), and driving different loads by performing high and low gears through a high and low gear box (14);
a differential (11) for adjusting the rotational speed of the tires (13) at both sides when turning, inputting partial power through the gearbox system (9), and decelerating through the planetary mechanism (12) to drive the tires (13) to turn;
and the driving gearbox (15) is used for providing mechanical power for switching four-wheel drive sources, inputting partial power of the planetary reduction mechanism (7) through the gear set IV and selecting and mounting different driving sources.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202311818129.9A CN117780888B (en) | 2023-12-27 | 2023-12-27 | HMT mechanical hydraulic stepless speed changing box for tractor |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202311818129.9A CN117780888B (en) | 2023-12-27 | 2023-12-27 | HMT mechanical hydraulic stepless speed changing box for tractor |
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| CN117780888A true CN117780888A (en) | 2024-03-29 |
| CN117780888B CN117780888B (en) | 2024-07-26 |
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Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2000025041A1 (en) * | 1998-10-26 | 2000-05-04 | Yanmar Diesel Engine Co.,Ltd. | Continuously variable transmission |
| CN101133268A (en) * | 2005-03-04 | 2008-02-27 | 丰田自动车株式会社 | Control equipment for vehicle drive equipment |
| CN101173710A (en) * | 2006-10-31 | 2008-05-07 | 丰田自动车株式会社 | Control devices for vehicle drive systems |
| CN101178123A (en) * | 2006-11-09 | 2008-05-14 | 丰田自动车株式会社 | Control devices for vehicle drive systems |
| CN101260933A (en) * | 2008-04-24 | 2008-09-10 | 吉林大学 | Hydromechanical automatic shift system |
| KR20160089071A (en) * | 2015-01-19 | 2016-07-27 | 엘에스엠트론 주식회사 | Hydro mechanical transmission |
| CN109519529A (en) * | 2018-12-25 | 2019-03-26 | 北理慧动（常熟）车辆科技有限公司 | Pneumatic shift-selecting and changing actuating mechanism |
| CN111692300A (en) * | 2020-03-25 | 2020-09-22 | 中国北方车辆研究所 | Mechanical hydraulic composite transmission device suitable for heavy vehicle |
| CN218236102U (en) * | 2022-10-10 | 2023-01-06 | 潍柴雷沃智慧农业科技股份有限公司 | Hydraulic gear shifting control system and gearbox |
-
2023
- 2023-12-27 CN CN202311818129.9A patent/CN117780888B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2000025041A1 (en) * | 1998-10-26 | 2000-05-04 | Yanmar Diesel Engine Co.,Ltd. | Continuously variable transmission |
| CN101133268A (en) * | 2005-03-04 | 2008-02-27 | 丰田自动车株式会社 | Control equipment for vehicle drive equipment |
| CN101173710A (en) * | 2006-10-31 | 2008-05-07 | 丰田自动车株式会社 | Control devices for vehicle drive systems |
| CN101178123A (en) * | 2006-11-09 | 2008-05-14 | 丰田自动车株式会社 | Control devices for vehicle drive systems |
| CN101260933A (en) * | 2008-04-24 | 2008-09-10 | 吉林大学 | Hydromechanical automatic shift system |
| KR20160089071A (en) * | 2015-01-19 | 2016-07-27 | 엘에스엠트론 주식회사 | Hydro mechanical transmission |
| CN109519529A (en) * | 2018-12-25 | 2019-03-26 | 北理慧动（常熟）车辆科技有限公司 | Pneumatic shift-selecting and changing actuating mechanism |
| CN111692300A (en) * | 2020-03-25 | 2020-09-22 | 中国北方车辆研究所 | Mechanical hydraulic composite transmission device suitable for heavy vehicle |
| CN218236102U (en) * | 2022-10-10 | 2023-01-06 | 潍柴雷沃智慧农业科技股份有限公司 | Hydraulic gear shifting control system and gearbox |
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| CN117780888B (en) | 2024-07-26 |
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