CN119042293A - Power split continuously variable transmission - Google Patents
Power split continuously variable transmission Download PDFInfo
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- CN119042293A CN119042293A CN202411546820.0A CN202411546820A CN119042293A CN 119042293 A CN119042293 A CN 119042293A CN 202411546820 A CN202411546820 A CN 202411546820A CN 119042293 A CN119042293 A CN 119042293A
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
-
- 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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0412—Cooling or heating; Control of temperature
- F16H57/0415—Air cooling or ventilation; Heat exchangers; Thermal insulations
- F16H57/0417—Heat exchangers adapted or integrated in the gearing
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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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
- F16H57/0424—Lubricant guiding means in the wall of or integrated with the casing, e.g. grooves, channels, holes
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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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps; Pressure control
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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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/045—Lubricant storage reservoirs, e.g. reservoirs in addition to a gear sump for collecting lubricant in the upper part of a gear case
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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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0482—Gearings with gears having orbital motion
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
本发明公开了一种功率分流无级变速器，属于车辆传动系统技术领域，该变速器包括：传动系统、离合器系统以及调速系统，传动系统包括传动轴组、轴齿轮组和行星齿轮组，传动轴组能输入机械动力流，轴齿轮组能通过调速系统将机械动力流转变为可调动力流，两股动力流能在行星齿轮组内累加和输出。本发明能根据作业需求全域自动无级调节发动机转速，具有提高作业效率，降低劳动强度，降低能耗及排放的优点。
The present invention discloses a power split continuously variable transmission, which belongs to the technical field of vehicle transmission system. The transmission includes: a transmission system, a clutch system and a speed regulating system. The transmission system includes a transmission shaft group, a shaft gear group and a planetary gear group. The transmission shaft group can input a mechanical power flow, and the shaft gear group can convert the mechanical power flow into an adjustable power flow through the speed regulating system. The two power flows can be accumulated and output in the planetary gear group. The present invention can automatically and steplessly adjust the engine speed in the whole range according to the operation requirements, and has the advantages of improving operation efficiency, reducing labor intensity, and reducing energy consumption and emissions.
Description
Technical Field
The invention relates to the technical field of vehicle power systems, in particular to a power split continuously variable transmission.
Background
The power split continuously variable transmission technology is used in the fields of high-horsepower vehicles, such as tractors, and the like, and almost all of the current European and American developed countries adopt the power split continuously variable transmission, but the manual transmission is mainly used at present in China due to the reasons of technology and industry foundation, so that the whole machine carrying the manual transmission has low operation efficiency and high labor intensity, and cannot meet the development requirements of automation and intellectualization of related industries.
Aiming at the current situation, in recent years, in China, such as the tractor industry, the development of the technology of the continuously variable transmission is advanced under high force, the existing power split type continuously variable transmission system generally realizes the continuously variable transmission through a parallel gear system, a planetary gear system, a hydraulic system, a clutch and a synchronizer system, in the transmission system, mechanical and hydraulic power are coupled at an output end, and the torque transmitted by a hydraulic part is very large because the torque of the output end is amplified by a plurality of times compared with that of an input end, so that the loss of the hydraulic power is increased, and a plurality of sets of hydraulic systems are needed to bear torque transmission at the same time, so that the adaptability, the working efficiency and the energy consumption efficiency of working conditions are all deficient.
To solve the above-mentioned technical problem, the U.S. patent application No. US18353916 discloses a continuously variable power split transmission having a shaft which can be coupled to a drive motor, wherein the drive motor is connected to at least one shaft, and wherein the drive motor is coupled to a drive output by means of a spur gear pair which can be engaged with a clutch depending on the direction of travel in order to achieve forward and reverse travel. The clutches are arranged in spaced apart relation. The invention realizes the combination of the mechanical transmission device and the hydraulic clutch or the fluid transmission device, and relatively reduces the loss of hydraulic power.
The prior art transmission generally has the following technical improvement space that the planetary gear train and the power of the input end are greatly deviated in the axial direction, larger power loss exists, a plurality of hydraulic motors are adopted in the hydraulic power output part, the input cost is larger, and the load of the transmission is increased.
Disclosure of Invention
The invention aims to provide a power split continuously variable transmission which can improve transmission efficiency and is low in system cost.
In order to solve the technical problems, the invention specifically provides the following technical scheme:
A power split stepless speed changer comprises a transmission system, a clutch system and a speed regulating system, wherein the transmission system comprises a transmission shaft group, a shaft gear set and a planetary gear set, the transmission shaft group can input mechanical power flow, the shaft gear set can convert the mechanical power flow into adjustable power flow through the speed regulating system, and the two power flows can be accumulated and output in the planetary gear set.
Preferably, the transmission shaft group comprises a first shaft and a eighth shaft which are matched, the planetary gear set comprises a first planetary gear train, the first planetary gear train is provided with a gear ring Z5 and a planet carrier P1 which are matched, the gear ring Z5 is fixedly connected with the first shaft, the planet carrier P1 is in transmission connection with the eighth shaft, the shaft gear set comprises a gear Z20 and a gear Z1, the gear Z20 is fixedly connected with the first shaft, the gear Z1 is in transmission connection with the planet carrier P1, and the gear Z20 is in transmission connection with the gear Z1 through a speed regulation system. The power is input through a first shaft, one part of the power is directly input to the first planetary gear train through the gear ring Z5, the other part of the power is sequentially input to the first planetary gear train through the gear Z20, the speed regulating system and the gear Z1, the two parts of the power are coupled through the first planetary gear train, the power is output to the rear-end planetary and gear transmission system through the planet carrier P1, and finally the power is output through a shaft eight.
Preferably, the speed regulation system includes a variable displacement hydraulic pump and a hydraulic motor which are disposed in sequence in the power transmission direction between the gear Z20 and the gear Z1. The variable hydraulic pump can continuously change the discharge capacity of the pump to change the output of the pump flow, so that the output rotating speed of the hydraulic motor is continuously and steplessly changed, and the output rotating speed can be continuously changed in a wide vehicle speed area of the whole vehicle by combining the planetary gear set and the shaft gear set to form different section transmission ratios.
Preferably, the planetary gear set further comprises a second planetary gear set and a third planetary gear set, the second planetary gear set is provided with a sun gear Z6, a gear ring Z8 and a planet carrier P2 which are arranged in a matched mode, the gear ring Z8 is fixedly connected with the planet carrier P1, the planet carrier P2 is fixedly connected with a first shaft, the third planetary gear set is provided with a sun gear Z9, a gear ring Z11 and a planet carrier P3 which are arranged in a matched mode, the sun gear Z6 is fixedly connected with the sun gear Z9, the planet carrier P1 is fixedly connected with the planet carrier P3, and the gear ring Z11, the sun gear Z9 and the planet carrier P1 can be in transmission connection with an eighth shaft through the shaft gear set.
Preferably, the clutch system includes a first system for outputting the first power and a second system for outputting the second power.
Preferably, the shaft gear set further comprises a gear Z12 and a gear Z14 which are fixedly connected with the planet carrier P1, the sun gear Z9, the gear ring Z11 and the gear Z12 can be in transmission connection with the shaft eight through a first system, and the gear Z14 can be in transmission connection with the shaft eight through a second system. The first planetary gear system transmits the coupled power to the second planetary gear system and the third planetary gear system through the planet carrier P1, and the power output of a plurality of gears is realized by matching the shaft gear set and the clutch system, namely the planet carrier P2 and the planet carrier P3 are matched and connected with the planet carrier P1 and are arranged in a similar way, so that the power transmission path is shortened, the power loss is reduced, the integral size of the planetary gear set is reduced, and the integral structure of the transmission is simple and compact by optimizing the structural design of the planetary gear set;
in the technical scheme, the planetary gear set for power coupling is arranged on the power input side of the transmission, so that the system efficiency is improved, and meanwhile, the system cost is reduced.
Preferably, the shaft gear set further comprises a gear Z13, an idler Z15, a gear Z16, a gear Z17 and a gear Z18, the first system comprises a clutch I, a clutch II and a clutch III, the second system comprises a clutch IV, the gear Z12 is in transmission connection with the gear Z13, the gear Z13 is in transmission connection with the shaft eight through the clutch III, the idler Z15 is in transmission connection with the gear Z14, the idler Z15 is in transmission connection with the gear Z16, the gear Z16 is in transmission connection with the shaft eight through the clutch IV, the gear Z18 is fixedly connected with the shaft eight, the gear Z17 is in transmission connection with the gear Z18, the gear Z17 is in transmission connection with the gear Z11 through the clutch I, and the gear Z17 is in transmission connection with the sun gear Z9 through the clutch II.
When the first clutch is combined, after the power output by the engine is coupled through the variable hydraulic pump, the hydraulic motor and the first planetary gear system, a part of the power is transmitted to the gear ring Z8 through the planet carrier P1 and is input to the second planetary gear system, a part of the power of the engine is input to the second planetary gear system through the planet carrier P2, the two parts of the power are converged through the sun gear Z6 of the first planetary gear system and are output to the sun gear Z9 of the third planetary gear system, the other part of the power on the planet carrier P1 is input to the planet carrier P3 of the third planetary gear system, and the two parts of the power are sequentially output to the first clutch gear Z17, the gear Z18 and the shaft eight through the gear ring Z11 of the third planetary gear system, and finally the power is output, so that the first section stepless speed change power output is realized;
When the clutch II is combined, after the power output by the engine is coupled through the variable hydraulic pump, the hydraulic motor and the first planetary gear system, one part of the power is transmitted to the gear ring Z8 through the planet carrier P1 and is input to the second planetary gear system, one part of the power of the engine is input to the second planetary gear system through the planet carrier P2, the two parts of the power are converged through the sun gear Z6 of the second planetary gear system and output to the clutch II, and are sequentially transmitted to the gear Z17, the gear Z18 and finally output power through the shaft eight, so that the stepless speed change power output of the second section is realized;
when the clutch III is combined, the power output by the engine is coupled through the variable hydraulic pump, the hydraulic motor and the first planetary gear system, and then sequentially passes through the planet carrier P1, the gear Z12, the gear Z13, the clutch III and finally the shaft eight to output power, so that the stepless speed change power output of the third section is realized;
When the clutch IV is combined, the power output by the engine is coupled through the variable hydraulic pump, the hydraulic motor and the first planetary gear system, and then sequentially passes through the planet carrier P1, the gear Z14, the idler Z15, the gear Z16, the clutch IV and finally the power output through the shaft eight, so that the reverse gear stepless speed change power output is realized;
In vehicle operation, the mechanism realizes continuous variable speed ratio in each driving vehicle speed, thereby realizing continuous stepless speed ratio adjustment in the whole working vehicle speed area, enabling the engine to work in the optimal rotating speed and power area so as to adapt to the requirement of load real-time change, improving fuel economy, and simultaneously improving the safety of vehicle load operation by enhancing the stability degree of the driving process.
Preferably, the shaft gear set further comprises a gear Z19 and a gear Z2, the transmission shaft set further comprises a shaft seven and a shaft three which are coaxially arranged at one side of the shaft, the gear Z19 is in transmission connection with the gear Z20, the gear Z19 is fixedly connected with the shaft seven, the shaft seven is connected with the variable hydraulic pump, the gear Z2 is in transmission connection with the gear Z1, the gear Z2 is fixedly connected with the shaft three, and the shaft three is connected with the hydraulic motor. The power of the first shaft sequentially passes through a gear Z20, a gear Z19, a seventh shaft, a variable hydraulic pump, a hydraulic motor, a third shaft, a gear Z2 and a gear Z1, and finally is input into the planetary gear set.
Preferably, the transmission further comprises a housing, the transmission shaft group comprises a main shaft penetrating through the housing and rotationally connected with the main shaft, the housing is provided with a lubricating piece at the joint of the main shaft, the lubricating piece comprises a base body, the base body is sleeved outside the main shaft, a first ring fixedly arranged and a second ring slidingly arranged are arranged outside the base body, a corrugated pipe is connected between the first ring and the second ring, through holes are formed in the base body at intervals, and an oil way communicated to the inner side of the corrugated pipe is formed in the outer end of the first ring. In the operation process of the vehicle, the main shaft rotates at a high speed to generate heat, the first ring and the second ring form an annular cavity at the outer side of the main shaft through the corrugated pipe and the matrix, the oil way is connected with the container through the pipeline, the container stores lubricating oil, the heat generated by the rotation of the main shaft can be transferred to the annular cavity, the air in the annular cavity is heated and then the air pressure is increased, so that the corrugated pipe expands and stretches, the second ring is driven to slide on the matrix, the space of the annular cavity is enlarged after the corrugated pipe stretches, the lubricating oil in the container can be pumped into the annular cavity through the pipeline, in a conventional state, the second ring is positioned at the position of the through hole to form a blockage, and the through hole is communicated with the inner side of the collective body, namely the lubricating oil stored in the annular cavity can be released to the main shaft through the through hole;
Because the shell is fixed relative to the vehicle, and the main shaft needs to transmit engine power and rotate at a high speed, the main shaft is provided with a bearing at the assembly position of the main shaft and the shell, and the outwards extending base body can form a supporting effect on the main shaft, so that the load on the bearing is reduced, the power transmission stability is further improved, interference of the shell can be transmitted to the corrugated pipe through the base body, the first ring and the second ring, and the interference transmission of the shell to the main shaft can be reduced through small-amplitude telescopic deformation of the corrugated pipe, so that the interference to the main shaft and the engine is reduced.
Compared with the prior art, the invention has the advantages that the full-speed area is realized through the combination of the planetary gear set and the shaft gear set, the planetary gear set realizes the stepless speed change function under the high-power transmission through the cooperation of a plurality of planetary gear trains, the planetary gear set is arranged on the power input side of the transmission in a concentrated way, the system efficiency is improved, the system cost is reduced, the engine power is input into the power split stepless transmission, then the power is output through the stepless speed change, the stepless speed change gear shifting of the vehicle is realized according to the working condition changes such as the load in the operation, the running requirements of the whole vehicle under different working conditions are met, the economical fuel property is improved, the main shaft of the transmission power can be lubricated and cooled when no external power exists, the transmission stability is improved, the transmission ratio is stabilized, and the service life of parts is also prolonged.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below. It will be apparent to those of ordinary skill in the art that the drawings in the following description are exemplary only and that other implementations can be obtained from the extensions of the drawings provided without inventive effort.
Fig. 1 is a schematic diagram of the transmission principle of embodiment 1 of the present invention;
fig. 2 is a schematic diagram of the transmission principle of embodiment 2 of the present invention;
FIG. 3 is a schematic diagram of the transmission principle of embodiment 3 of the present invention;
fig. 4 is a schematic cross-sectional view of a lubricant.
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 concept of the present application will be described with reference to the accompanying drawings. It should be noted that the following descriptions of the various concepts are only for making the content of the present application easier to understand, and are not meant to limit the scope of the present application, and at the same time, the embodiments of the present application and the features in the embodiments may be combined with each other without conflict. The application will be described in detail below with reference to the drawings in connection with embodiments.
Embodiment 1a power split continuously variable transmission includes a drive train including a drive shaft set capable of inputting a mechanical power flow, a shaft gearset capable of converting the mechanical power flow into an adjustable power flow through the speed regulating system, and a planetary gearset capable of accumulating and outputting both power flows in the planetary gearset, a clutch system, and a speed regulating system.
Referring to fig. 1, the transmission shaft group comprises a first shaft S1 and a eighth shaft S8 which are arranged in a matched manner, the planetary gear set comprises a first planetary gear train, the first planetary gear train is provided with a gear ring Z5 and a planet carrier P1 which are arranged in a matched manner, the gear ring Z5 is fixedly connected with the first shaft S1, the planet carrier P1 is in transmission connection with the eighth shaft S8, the shaft gear set comprises a gear Z20 and a gear Z1, the gear Z20 is fixedly connected with the first shaft S1, the gear Z1 is in transmission connection with the planet carrier P1, and the gear Z20 is in transmission connection with the gear Z1 through a speed regulation system.
The power is input through a first shaft S1, one part of the power is directly input to the first planetary gear train through a gear ring Z5, the other part of the power is sequentially input to the first planetary gear train through a gear Z20, a speed regulating system and a gear Z1, the two parts of power are coupled through the first planetary gear train, the power is output to a rear-end planetary and gear transmission system through a planet carrier P1, and the power is output through a eighth shaft S8.
The speed regulation system comprises a variable hydraulic pump HP and a hydraulic motor HM which are arranged in sequence along the power transmission direction and are arranged between a gear Z20 and a gear Z1. The variable hydraulic pump HP can continuously change the discharge capacity of the pump to change the output of the pump flow, so that the output rotating speed of the hydraulic motor HM continuously and steplessly changes, and the output rotating speed can continuously change in a wide vehicle speed area of the whole vehicle by combining different section transmission ratios formed by the planetary gear set and the shaft gear set, and the stepless speed change of the output rotating speed is realized.
The planetary gear set further comprises a second planetary gear set and a third planetary gear set, wherein the second planetary gear set is provided with a sun gear Z6, a gear ring Z8 and a planet carrier P2 which are arranged in a matched mode, the gear ring Z8 is fixedly connected with the planet carrier P1, the planet carrier P2 is fixedly connected with a first shaft S1, the third planetary gear set is provided with a sun gear Z9, a gear ring Z11 and a planet carrier P3 which are arranged in a matched mode, the sun gear Z6 is fixedly connected with the sun gear Z9, the planet carrier P1 is fixedly connected with the planet carrier P3, and the gear ring Z11, the sun gear Z9 and the planet carrier P1 can be in transmission connection with a second shaft S8 through the shaft gear set.
The clutch system includes a first system for outputting a first power and a second system for outputting a second power.
The shaft gear set further comprises a gear Z12 and a gear Z14 which are fixedly connected with the planet carrier P1, the sun gear Z9, the gear ring Z11 and the gear Z12 can be in transmission connection with the shaft eight S8 through a first system, and the gear Z14 can be in transmission connection with the shaft eight S8 through a second system. The first planetary gear system transmits the coupled power to the second planetary gear system and the third planetary gear system through the planet carrier P1, and the power output of a plurality of gears is realized by matching the shaft gear set and the clutch system, namely the planet carrier P2 and the planet carrier P3 are matched and connected with the planet carrier P1 and are arranged in a similar way, so that the power transmission path is shortened, the power loss is reduced, the integral size of the planetary gear set is reduced, and the integral structure of the transmission is simple and compact by optimizing the structural design of the planetary gear set;
in the technical scheme, the planetary gear set for power coupling is arranged on the power input side of the transmission, so that the system efficiency is improved, and meanwhile, the system cost is reduced.
The shaft gear set further comprises a gear Z13, an idler Z15, a gear Z16, a gear Z17 and a gear Z18, the first system comprises a first clutch K1, a second clutch K2 and a third clutch K3, the second system comprises a fourth clutch K4, the gear Z12 is in transmission connection with the gear Z13, the gear Z13 is in transmission connection with an eight-shaft S8 through the third clutch K3, the idler Z15 is in transmission connection with the gear Z14, the idler Z15 is in transmission connection with the gear Z16, the gear Z16 is in transmission connection with the eight-shaft S8 through the fourth clutch K4, the gear Z18 is fixedly connected with the eight-shaft S8, the gear Z17 is in transmission connection with the gear Z18, the gear Z17 is in transmission connection with the gear Z11 through the first clutch K1, and the gear Z17 is in transmission connection with the sun gear Z9 through the second clutch K2.
When the first clutch K1 is combined, after the power output by the engine is coupled through the variable hydraulic pump HP, the hydraulic motor HM and the first planetary gear system, a part of the power is transmitted to the gear ring Z8 through the planet carrier P1 and is input to the second planetary gear system, a part of the power of the engine is input to the second planetary gear system through the planet carrier P2, the two parts of power are converged through the sun gear Z6 of the first planetary gear system and output to the sun gear Z9 of the third planetary gear system, the other part of power on the planet carrier P1 is input to the planet carrier P3 of the third planetary gear system, and the two parts of power are sequentially output to the first clutch K1, the gear Z17, the gear Z18 and the shaft eighth S8 through the gear ring Z11 of the third planetary gear system, and finally the power is output, so that the first section stepless speed change power output is realized;
When the clutch II K2 is combined, after the power output by the engine is coupled through the variable hydraulic pump HP, the hydraulic motor HM and the first planetary gear system, one part of the power is transmitted to the gear ring Z8 through the planet carrier P1 and is input to the second planetary gear system, one part of the power of the engine is input to the second planetary gear system through the planet carrier P2, the two parts of power are converged through the sun gear Z6 of the second planetary gear system and output to the clutch II K2, and are sequentially transmitted to the gear Z17 and the gear Z18, and finally output power through the shaft eight S8, so that the stepless speed change power output of the second section is realized;
When the clutch three K3 is combined, the power output by the engine is coupled through the variable hydraulic pump HP, the hydraulic motor HM and the first planetary gear system, and then sequentially passes through the planet carrier P1, the gear Z12, the gear Z13, the clutch three K3 and finally the shaft eight S8 to output power, so that the stepless speed change power output of the third section is realized;
When the clutch IV K4 is combined, the power output by the engine is coupled through the variable hydraulic pump HP, the hydraulic motor HM and the first planetary gear system, and then sequentially passes through the planet carrier P1, the gear Z14, the idler Z15, the gear Z16, the clutch IV K4 and finally the shaft eight S8 to output power, so that reverse gear stepless speed change power output is realized;
In vehicle operation, the mechanism realizes continuous variable speed ratio in each driving vehicle speed, thereby realizing continuous stepless speed ratio adjustment in the whole working vehicle speed area, enabling the engine to work in the optimal rotating speed and power area so as to adapt to the requirement of load real-time change, improving fuel economy, and simultaneously improving the safety of vehicle load operation by enhancing the stability degree of the driving process.
The shaft gear set further comprises a gear Z19 and a gear Z2, the transmission shaft set further comprises a shaft seven S7 and a shaft three S3 which are coaxially arranged on the side of the shaft one S1, the gear Z19 is in transmission connection with the gear Z20, the gear Z19 is fixedly connected with the shaft seven S7, the shaft seven S7 is connected with the variable hydraulic pump HP, the gear Z2 is in transmission connection with the gear Z1, the gear Z2 is fixedly connected with the shaft three S3, and the shaft three S3 is connected with the hydraulic motor HM. The power of the first shaft S1 sequentially passes through a gear Z20, a gear Z19, a seventh shaft S7, a variable hydraulic pump HP, a hydraulic motor HM, a third shaft S3, a gear Z2 and a gear Z1, and finally is input into the planetary gear set.
It should be noted that the transmission shaft group further comprises a second shaft S2, a fourth shaft S4, a fifth shaft S5 and a sixth shaft S6 which are coaxially arranged with the first shaft S1, the second shaft S2, the fourth shaft S4 and the sixth shaft S6 are sleeved on the first shaft S1 in an empty mode, the fifth shaft S5 is sleeved on the sixth shaft S6 in an empty mode, and the third shaft S3, the seventh shaft S7 and the eighth shaft S8 are respectively arranged with the first shaft S1 in a fixed center distance mode;
The first planetary gear system also comprises a sun gear Z3 and a planetary gear Z4 which are matched and arranged between the gear ring Z5 and the planet carrier P1, wherein the sun gear Z3 is fixedly connected with the second shaft S2, the second planetary gear system also comprises a planetary gear Z7 which is matched and arranged with the sun gear Z6, the gear ring Z8 and the planet carrier P2, and the third planetary gear system also comprises a planetary gear Z10 which is matched and arranged with the sun gear Z9, the gear ring Z11 and the planet carrier P3;
The gear Z1 is fixedly connected with the second shaft S2, the gear Z2 is fixedly connected with the third shaft S3, the gear Z12 is fixedly connected with the fifth shaft S5, the gear Z13 is sleeved on the eighth shaft S8, the gear Z14 is fixedly connected with the fifth shaft S5, the gear Z16 is sleeved on the eighth shaft S8, and the gear Z17 is fixedly connected with the sixth shaft S6.
It should be noted that the number of the substrates, the clutch system has a wet clutch;
the driving clutch plate of the clutch I K1 is fixed on the gear ring Z11, and the driven clutch plate of the clutch I K1 is fixed on the shaft six S6;
the driving clutch plate set of the clutch II K2 is fixed on the shaft IV S4, and the driven clutch plate set of the clutch II K2 is fixed on the shaft six S6;
The driving clutch plate group of the clutch III K3 is fixed on the gear Z13, and the driven clutch plate group of the clutch II K2 is fixed on the shaft eight S8;
The driving clutch plate group of the clutch four K4 is fixed to the gear Z16, and the driven clutch plate group of the clutch two K2 is fixed to the shaft eight S8.
Referring to fig. 4, the transmission further includes a housing 1, the transmission shaft group includes a main shaft passing through the housing 1 and rotationally connected, the housing 1 is provided with a lubrication element 2 at a joint with the main shaft, the lubrication element 2 includes a base 20, the base 20 is sleeved outside the main shaft, a first ring 21 fixedly arranged and a second ring 22 slidingly arranged are arranged outside the base 20, a bellows 23 is connected between the first ring 21 and the second ring 22, through holes 201 are arranged at intervals of the base 20, and an oil path 202 communicated to the inner side of the bellows 23 is arranged at the outer end of the first ring 21.
The spindle includes, but is not limited to, axis one S1 and axis eight S8.
In the operation process of the vehicle, the main shaft rotates at a high speed to generate heat, the first ring 21 and the second ring 22 form an annular cavity at the outer side of the main shaft through the corrugated pipe 23 and the matrix 20, the oil way 202 is connected with the container through a pipeline, the container stores lubricating oil, the heat generated by the rotation of the main shaft can be transferred to the annular cavity, the air in the annular cavity is heated and then the air pressure is increased, so that the corrugated pipe 23 expands and stretches to drive the second ring 22 to slide on the matrix 20, the space of the annular cavity is enlarged after the corrugated pipe 23 stretches, the lubricating oil in the container can be pumped into the annular cavity through the pipeline, in a conventional state, the second ring 22 is positioned at the position of the through hole 201 to form a blockage, and the through hole 201 is communicated with the inner side of the collective through hole, namely the oil stored in the annular cavity can be released to the main shaft through the through hole 201;
Since the housing 1 is fixed relative to the vehicle and the main shaft is required to rotate at a high speed by transmitting engine power, the main shaft has a bearing at the position assembled with the housing 1, the outwardly extending base 20 can form a supporting effect on the main shaft, which is beneficial to reducing the load on the bearing, further improving the power transmission stability, the interference of the housing 1 can be transmitted to the bellows 23 through the base 20, the first ring 21 and the second ring 22, and the interference transmission of the housing 1 to the main shaft can be reduced through small-amplitude telescopic deformation of the bellows 23, thereby reducing the interference to the main shaft and the engine.
A retainer ring 24 for limiting the sliding of the second ring 22 is fixed on the outer side of the base body 20, a diaphragm 25 is arranged between the retainer ring 24 and the second ring 22, a space exists between the diaphragm 25 and the base body 20, and a gas path 203 for communicating the space is arranged on the inner side of the base body 20.
When heat of the main shaft and the shell 1 is transferred to the annular cavity through the base body 20, the second ring 22 is close to the baffle plate while being far away from the first ring 21, so that the diaphragm 25 is pressed, a space between the diaphragm 25 and the base body 20 is pressed and exhausted from the air path 203, the exhausted air assists in cooling the main shaft on one hand, on the other hand, flowing air flow can promote lubricating oil to flow on the main shaft, other parts connected with the main shaft are helped to be lubricated and cooled by the lubricating oil, the coverage range of the lubricating oil is improved, and the transmission stability is further improved. The provision of the diaphragm 25 also assists in the elastic return of the bellows 23 to ensure that the bellows 23 is capable of applying lubricant to the spindle multiple times during operation of the vehicle, improving durability and stability of operation of the vehicle.
Embodiment 2 referring to fig. 2, on the basis of the above embodiment 1, the variable hydraulic pump HP is replaced with a generator GM, the hydraulic motor HM is replaced with a drive motor EM, the generator GM is connected to a shaft seven S7, and the drive motor EM is connected to a shaft three S3. The stepless speed change is realized by continuously changing the rotation speed of the generator GM so as to continuously change the rotation speed of the engine connected with the first connecting shaft S1.
Embodiment 3 referring to fig. 3, on the basis of embodiment 2, a third K3 and a fourth K4 clutch are arranged on a fifth S5 shaft, a gear Z12 and a gear Z14 corresponding to the third K3 and the fourth K4 are sleeved on the fifth S5 shaft, a gear Z13 and a gear Z16 are fixed on a shaft 8, a driving clutch plate group of the third K3 and a driving clutch plate group of the fourth K4 clutch are respectively fixed with the fifth S5 shaft, a driven clutch plate group of the third K3 is connected with the gear Z12, and a driven clutch plate group of the fourth K4 is connected with the gear Z14.
Through the implementation scheme, the requirements of the whole vehicle or the agricultural machinery on the stepless speed change device with different power sections can be met, the stepless speed change is realized during operation, the power system can automatically adapt to the requirements of different working conditions, the efficiency is improved, the energy consumption is reduced, the labor intensity is reduced, and the technical foundation is provided for intellectualization and unmanned.
The above examples and/or embodiments are merely for illustrating the preferred embodiments and/or implementations of the present technology, and are not intended to limit the embodiments and implementations of the present technology in any way, and any person skilled in the art should be able to make some changes or modifications to the embodiments and/or implementations without departing from the scope of the technical means disclosed in the present disclosure, and it should be considered that the embodiments and implementations are substantially the same as the present technology.
The principles and embodiments of the present application have been described herein with reference to specific examples, the description of which is intended only to facilitate an understanding of the method of the present application and its core ideas. The foregoing is merely illustrative of the preferred embodiments of the application, and it will be appreciated that numerous modifications, adaptations and variations of the application can be made by those skilled in the art without departing from the principles of the application, and that other features and advantages of the application can be combined in any suitable manner, and that no improvement in the design or design of the application is intended to be applied directly to other applications.
Claims (9)
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| CN202411546820.0A CN119042293A (en) | 2024-11-01 | 2024-11-01 | Power split continuously variable transmission |
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| CN202411546820.0A CN119042293A (en) | 2024-11-01 | 2024-11-01 | Power split continuously variable transmission |
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| CN119042293A true CN119042293A (en) | 2024-11-29 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN119308981A (en) * | 2024-12-18 | 2025-01-14 | 浙江万里扬股份有限公司杭州分公司 | A continuously variable transmission for tractors |
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