WO2018137437A1 - 无级变速器 - Google Patents

无级变速器 Download PDF

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Publication number
WO2018137437A1
WO2018137437A1 PCT/CN2017/116593 CN2017116593W WO2018137437A1 WO 2018137437 A1 WO2018137437 A1 WO 2018137437A1 CN 2017116593 W CN2017116593 W CN 2017116593W WO 2018137437 A1 WO2018137437 A1 WO 2018137437A1
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WO
WIPO (PCT)
Prior art keywords
cavity
bucket wheel
planetary
input
wheel
Prior art date
Application number
PCT/CN2017/116593
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English (en)
French (fr)
Inventor
唐永峰
唐玉凝
Original Assignee
威海团中变速器有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 威海团中变速器有限公司 filed Critical 威海团中变速器有限公司
Priority to US16/349,930 priority Critical patent/US10677336B2/en
Publication of WO2018137437A1 publication Critical patent/WO2018137437A1/zh

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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
    • F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
    • F16H47/08—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion
    • 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
    • F16H2702/00—Combinations of two or more transmissions
    • 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
    • F16H2702/00—Combinations of two or more transmissions
    • F16H2702/02—Mechanical transmissions with planetary gearing combined with one or more other mechanical transmissions
    • 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
    • F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
    • F16H47/08—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion
    • F16H47/12—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion the members with orbital motion having vanes interacting with the fluid

Definitions

  • the present invention relates to a mechanical transmission, and more particularly to a flexibly activated continuously variable transmission.
  • the automatic transmission is divided into a hydraulic automatic transmission (AT), an electronically controlled mechanical automatic transmission (AMT) and a continuously variable transmission (CVT).
  • AT hydraulic automatic transmission
  • AMT electronically controlled mechanical automatic transmission
  • CVT continuously variable transmission
  • torque converter the most widely used and most loaded component is a torque converter, but now
  • the existing manual transmission mainly replaces the gear by adjusting different gear combinations; the existing electronically controlled mechanical automatic transmission (AMT) is installed on the basis of the conventional dry clutch and manual gear transmission.
  • the electronic control system transforms the manual shifting mechanism into an automatic shifting mechanism, thereby realizing automatic shifting of the stepped mechanical automatic transmission.
  • the disadvantage is that the flexible transmission cannot be provided, the stepless shifting cannot be realized, and the control structure is complicated.
  • the existing hydraulic transmission includes a torque converter and a transmission that increases control based on the torque converter, such as a hydraulic automatic transmission (AT), and the torque converter is connected through the housing.
  • the pump wheel and the pump wheel agitate the oil in the torque converter, and the turbine rotates through the guide wheel, and the turbine outputs the power.
  • the disadvantage is that when the speed difference between the pump wheel and the turbine of the torque converter is close to synchronization, the transmission is lost. Capacity, synchronization cannot be achieved; in order to improve the above problems of the torque converter, when the control system is added, the system is complicated and the manufacturing cost is high.
  • the existing continuously variable transmission transmits power by using a transmission belt with a transmission friction force and a variable working main and driven wheels, which can realize continuous change of the transmission ratio, thereby obtaining the power train and the engine working condition.
  • the best match, the shortcoming is that it can not provide flexible zero start, can not provide a large torque, easy to slip when the force changes frequently.
  • the liquid contained in the inner casing 2 forms an annular liquid surface in the inner casing 2 due to the centrifugal force.
  • the liquid enters each of the bucket wheels into a concave bucket wheel 22 .
  • the liquid entering the bucket wheel 22 forces the rotation speed of the bucket wheel 9 to gradually decrease until the rotation stops due to the centrifugal force.
  • the output shaft 8 gradually increases in speed, and finally the input shaft 7, the inner casing 2, the planetary gear 11,
  • the bucket wheel 9, the reverse wheel, the 12, the large ring gear 14 and the output shaft 8 are all rotated at the same speed to achieve a soft start of the load.
  • the liquid level of the liquid attached to the inner surface of the inner casing 2 determines the magnitude of the centrifugal force, and the magnitude of the centrifugal force further determines whether the output shaft 8 can rotate synchronously with the input shaft 7.
  • the current on the motor measured by the current transformer 604 reaches a set value, for example, greater than or equal to 120A (step 701) and Pt100 platinum thermal resistance 602 measured.
  • the signal is transmitted to the single chip microcomputer 601, and the single chip microcomputer 601 further controls the brake wheel through the electromagnetic brake 15.
  • step 702 the brake wheel 16 starts to mesh with the sun gear 13, thereby braking the sun gear 13, and the sun gear 13 further transmits the braking force to the reversing wheel 12, the planetary gear 11, and the large ring gear 14, Finally, the output shaft 8 is reached, and the output shaft speed is decreased to increase the torque; at the same time, the single chip microcomputer 601 transmits a signal to the electromagnetic valve 609, and the electromagnetic valve 609 is opened, and the liquid of the inner box is emptied by fixing the scoop tube 18 and the oil discharge line 17, This reduces power loss. After the electromagnetic brake 15 is braked, the complete set of gear mechanisms participating in the brake is actually a conventional planetary gear reducer structure.
  • the disadvantage of the hydraulic synchronous double speed device is that the balance force between the bucket wheel and the oil is limited, and the torque can only be changed within the maximum balance force of the oil to the bucket wheel; the output shaft needs to be larger than the maximum of the oil and the bucket wheel When the balance force can provide the torque, the oil of the inner box body needs to be emptied.
  • the gear mechanism involved in the braking is a commonly used planetary gear reducer structure, and does not have the flexible transmission function; the entire control system belongs to the electronic control system, and Control, braking and other devices are complex in structure.
  • the invention is to solve the problem that the existing manual transmission (MT) can not provide flexible transmission, and the control is complicated; the hydraulic transmission loses transmission capacity when synchronized, and cannot be synchronized; the hydraulic automatic transmission control system is complicated and high in cost; the continuously variable transmission (CVT) Can not provide flexible zero start, can not provide large torque, easy to slip when the force changes frequently; the balance between the hydraulic synchronous double-speed bucket wheel and the oil is limited, only the largest in the oil to the bucket wheel The torque in the balance force; when the output shaft needs to be greater than the maximum balance force of the oil and the bucket wheel, the oil of the inner tank needs to be emptied, and the gear mechanism involved in the brake is a commonly used planetary gear reducer.
  • the structure does not have the flexible transmission function; the whole control system belongs to the electronic control system, and the technical problems of the structure of the control and braking devices are complicated, and the torque is provided not only in the maximum balance force of the oil to the bucket wheel, but also the output shaft
  • the torque required to be greater than the maximum balance force of the oil and the bucket wheel is required, the oil of the inner tank is not required to be emptied, and the gear mechanism is not required to participate in the braking, thereby achieving continuous shifting and Range torque converter, comprising a flexible drive function, not need to add a control system, a continuously variable transmission with a simple structure.
  • the technical solution of the present invention is a continuously variable transmission including an input planetary gear set and an output planetary gear set, and a cavity carrier, a cavity between the input planetary gear set and the output planetary gear set
  • the body carrier includes a cavity input end cover, a cavity output end cover, a bucket wheel cavity housing fixed between the cavity input end cover and the cavity output end cover, and an input side planetary gear set inner side and a cavity input end
  • the cover is connected, the inner side of the output planetary gear set is connected with the cavity output end cover, and the inner side of the bucket wheel housing is provided with the bucket wheel planetary gear set.
  • the input planetary gear set includes an input sun gear and an input planetary wheel, and an input shaft is arranged in the middle of the input sun wheel, the input sun gear is meshed with the input planetary wheel, and the planetary gear connecting shaft is arranged in the middle of the input planetary gear.
  • the planetary wheel connecting shaft passes through the cavity input end cover and is rotatably connected with the cavity input end cover, the input shaft passes through the cavity input end cover, and the input shaft is rotatably connected with the cavity input end cover; the planetary wheel connecting shaft passes through the cavity The output end cover, the planetary wheel connecting shaft is rotatably connected with the cavity output end cover.
  • the output planetary gear set includes an output sun gear and an output planetary gear, and an output shaft is arranged in the middle of the output sun wheel, the output sun gear is coupled with the output planetary gear, and the output planetary wheel and the output end cover are passed through the cavity.
  • the planetary wheel connecting shaft is fixedly connected; the output shaft passes through the cavity output end cover into the interior of the bucket wheel housing, and the output shaft is rotatably connected with the cavity output end cover.
  • the bucket wheel planetary gear set includes a bucket wheel sun wheel and a bucket wheel planet wheel, the bucket wheel sun wheel and the bucket wheel planet wheel meshing connection, and the bucket wheel sun wheel is fixedly connected with an output shaft entering the interior of the bucket wheel cavity housing;
  • a bucket wheel planetary axle is arranged in the middle of the wheel, and one end of the bucket wheel planetary axle is disposed on the cavity output end cover, and the other end of the bucket wheel planetary axle is provided with a bucket wheel.
  • the other side of the bucket wheel housing is provided with a bushing, and the bushing is rotatably connected with an input shaft side passing through the cavity input end cover, the bucket wheel planetary axle passes through the bushing, the bucket wheel planetary axle and The bushing is rotatably connected.
  • the input planetary gear sets have three or more input planetary gears.
  • the output planetary gear sets have more than three planetary gears at the output end.
  • the number of the bucket wheel planetary wheels of the bucket wheel planetary gear set is three or more.
  • a bucket wheel is provided on the input shaft inside the bucket wheel housing.
  • a continuously variable transmission includes an input planetary gear set and a bucket wheel planetary gear set.
  • the input planetary gear set is provided with a cavity carrier inside, and the inner side of the planetary gear set of the bucket wheel is provided with an output planetary gear set;
  • the cavity planetary carrier The utility model comprises a cavity input end cover, a cavity output end cover, and a bucket wheel cavity housing fixedly arranged between the cavity input end cover and the cavity output end cover;
  • the input planetary gear set includes an input sun gear and an input planetary wheel, and an input shaft is arranged in the middle of the input sun wheel, the input sun gear is meshed with the input planetary wheel, and the planetary gear connecting shaft is arranged in the middle of the input planetary gear.
  • the planetary wheel connecting shaft passes through the cavity input end cover and the bucket wheel cavity housing, and the planetary wheel connecting shaft is in rotational connection with the cavity input end cover and the bucket wheel cavity housing;
  • the bucket wheel planetary gear set includes a bucket wheel sun wheel and a bucket wheel planet wheel, the bucket wheel sun wheel and the bucket wheel planet wheel meshing connection, the bucket wheel sun wheel is provided with an output shaft, the output shaft passes through the cavity output end cover, and the output shaft Rotatingly connected with the cavity output end cover, the bucket wheel planetary wheel is provided with a bucket wheel planetary axle, the bucket wheel planetary axle passes through the cavity output end cover and the bucket wheel cavity housing, the bucket wheel planetary axle and the cavity output end cover a rotary connection with the bucket wheel housing, and a bucket wheel on the bucket wheel planet axle inside the bucket wheel chamber;
  • the output planetary gear set includes an output sun gear and an output planetary gear, the output sun gear and the output planetary gear are meshed, the output planetary gear and the planetary gear passing through the cavity input end cover and the bucket wheel housing
  • the connecting shaft is fixedly connected, and the output sun wheel is fixedly connected with the output shaft passing through the output end cover of the cavity.
  • the input planetary gear sets have three or more input planetary gears.
  • the output planetary gear sets have more than three planetary gears at the output end.
  • the number of the bucket wheel planetary wheels of the bucket wheel planetary gear set is three or more.
  • the invention has the beneficial effects that since the continuously variable transmission includes an input planetary gear set and an output planetary gear set, a cavity carrier is arranged between the input planetary gear set and the output planetary gear set, and the cavity carrier includes a cavity
  • the input end cover, the cavity output end cover, the cavity input end cover and the cavity output end cover are fixedly provided with a bucket wheel cavity housing, and the inner side of the input end planetary gear set is connected with the cavity input end cover, and the output end planet
  • the inner side of the gear set is connected with the output end cover of the cavity, and the inner side of the bucket wheel housing is provided with a bucket wheel planetary gear set, which can realize zero speed start and no external resistance start at the start, the transmission process is flexible, and the torque increase can be realized. Double setting, large torque range, synchronous working conditions, no need for control devices, adaptive adjustment, automatic matching of a wide range of torque and speed, enabling high-power flexible transmission.
  • Figure 1 is a perspective view of Embodiment 1 of the present invention.
  • Figure 2 is another axial side view of Embodiment 1 of the present invention.
  • Figure 3 is a front elevational view of Embodiment 1 of the present invention.
  • Figure 4 is a rear elevational view of Embodiment 1 of the present invention.
  • Figure 5 is a side view of Embodiment 1 of the present invention.
  • Figure 6 is a schematic view of Embodiment 2 of the present invention.
  • Figure 7 is a front elevational view of Embodiment 2 of the present invention.
  • Figure 8 is a perspective view of Embodiment 2 of the present invention.
  • Figure 9 is another isometric view of Embodiment 2 of the present invention.
  • 101 the input end planetary gear set; 102, the output end planetary gear set; 103, the bucket wheel planetary gear set; 104, the cavity planet carrier; 1, the input shaft; 2, the input end sun gear; 3, the input end planetary gear; 4, planetary wheel connecting shaft; 5, bearing; 6, cavity input end cover; 7, bucket wheel; 8, bucket wheel planetary wheel; 9, bucket wheel sun wheel; 10, output sun wheel; 11, output shaft; 12, bushing; 13, cavity output end cover; 14, bucket wheel cavity housing; 15, the output end of the planet wheel; 16, the bucket wheel cavity internal oil; 17, the bucket wheel planetary axle.
  • an embodiment of a continuously variable transmission of the present invention is provided with an input planetary gear set 101 and an output planetary gear set 102, an input planetary gear set 101 and an output planetary gear.
  • a cavity carrier 104 is disposed between the groups 102.
  • the cavity carrier 104 includes a cavity input end cover 6, a cavity output end cover 13, and a cavity input end cover 6 and a cavity output end cover 13 are fixedly disposed.
  • the bucket wheel housing 14 is connected to the cavity input end cover 6 at the inner side of the input end planetary gear set 101, and the inner side of the output end planetary gear set 102 is connected to the cavity output end cover 13 and the inner side of the bucket wheel housing 14
  • a bucket wheel planetary gear set 103 is provided;
  • the input planetary gear set 101 includes an input sun gear 2 and three input planetary gears 3, and an input shaft 1 is provided between the input sun gear 2, and the input sun gear 2 and the input are provided.
  • the planetary gears 3 are meshed and connected, and the planetary gears 3 are arranged in the middle of the input planetary gears 3.
  • the planetary gear connecting shafts 4 pass through the cavity input end cover 6.
  • the planetary gear connecting shaft 4 is rotatably connected with the cavity input end cover 6.
  • the input shaft 1 passes through the cavity input end cover 6, and the input shaft 1 and the cavity input end cover 6 rotate.
  • the planetary wheel connecting shaft 4 passes through the cavity output end cover 6, and the planetary gear connecting shaft 4 is rotatably connected with the cavity output end cover 6;
  • the output end planetary gear set 102 includes an output end sun gear 10 and three output end planets
  • the wheel 15 is provided with an output shaft 11 at the output end of the sun gear 10, the output end sun gear 10 and the output end planetary gear 15 are meshed with each other, and the output end planetary gear 15 is fixed with the planetary wheel connecting shaft 4 passing through the cavity output end cover 13.
  • the bucket wheel planetary gear set 103 includes a bucket wheel sun gear 9 and The six bucket wheel planetary gears 8, the bucket wheel sun gear 9 and the bucket wheel planetary gear 8 are meshed with each other, and the bucket wheel sun gear 9 is fixedly connected with the output shaft 11 that enters the interior of the bucket wheel housing casing 14;
  • a bucket wheel planetary axle 17 is provided, and one end of the bucket wheel planetary axle 17 is rotatably connected to the cavity output end cover 13, and the other end of the bucket wheel planetary axle 17 is rotatably connected to the cavity input end cover 6, and the bucket wheel cavity shell is connected.
  • a bucket wheel 7 is fixed on the bucket wheel planetary axle 17 inside the body 14; the bucket wheel cavity
  • the other side of the casing 14 is provided with a bushing 12, and the bushing 12 is rotatably connected to the input shaft 1 side of the cavity input end cover 6, and the bucket wheel planetary axle 17 passes through the bushing 12, and the bucket wheel planetary axle 17
  • the bushing 12 is rotatably connected, and the bushing 12 and the cavity input end cover 6 contain an appropriate amount of the internal fluid of the bucket wheel chamber.
  • the input shaft 1 inside the bucket wheel housing 14 is provided with a bucket wheel 7.
  • the bucket wheel planetary wheel 8 and the bucket wheel 7 can also be formed as a unitary structure, and the other end of the bucket wheel 7 can adopt a cantilever structure or a support structure to adapt to various transmissions with different volume requirements.
  • the number of teeth of the input sun gear 2 is 35
  • the number of teeth of the input planetary gear 3 is 70
  • the number of teeth of the output planetary gear 15 is 35
  • the number of teeth of the output sun gear 10 is 70.
  • the output shaft 11 outputs torque in a range that is four times the torque provided by the input shaft 1.
  • the number of teeth of the bucket wheel planetary gear 8 is 20, the number of teeth of the bucket wheel sun gear 9 is 50, and the maximum balance torque range that the bucket wheel gear set 103 can provide to the output shaft 11 is that the bucket wheel 7 is combined with the oil inside the bucket wheel chamber. 2.5 times the resistance torque.
  • the running process is: when starting, set the power clockwise input, the power is input from the input shaft 1, the input sun gear 2 rotates clockwise, and the input sun gear 2 drives the input end planetary gear 3 to rotate counterclockwise, through the fixed connection
  • the planetary wheel connects the shaft 4, and drives the output planetary gear 15 to rotate.
  • the sun gear 10 receives the resistance from the output shaft 11, and the output planetary gear 15 revolves counterclockwise around the output sun gear 10 to drive the cavity carrier 104. Counterclockwise revolution, which in turn drives the bucket wheel planetary gear 8 to rotate counterclockwise, and then drives the bucket wheel 7 to rotate counterclockwise.
  • the counterclockwise rotation speed of the bucket wheel 7 exceeds the counterclockwise revolution number of the cavity carrier 104, and the bucket wheel 7 Counterclockwise rotation is formed in the bucket wheel housing 14 by the resistance of the oil 16 inside the bucket wheel body to form a torque, which includes the liquid gravity formed by the revolution of the bucket wheel housing 14 and the fluid injection from the bucket wheel 7 is connected to the nozzle.
  • the hydraulic power of the bucket wheel 7 and the liquid adhesion force of the oil between the bucket wheel 7 and the bucket wheel housing 14 are transmitted to the bucket wheel sun by the variable diameter of the bucket wheel planet 8 and the bucket wheel sun wheel 9
  • the output shaft 11 of the wheel 9 is fixed, and the sun wheel 9 of the bucket wheel is outputted. The shaft 11 does not move.
  • the torque is converted into a torque that prevents the cavity carrier 104 from reversing counterclockwise, thereby driving the output end planetary gear 15 to force the output sun gear 10, and the output end sun gear 10 is driven.
  • the output shaft 11 outputs power, and the resistance of the oil 16 in the bucket chamber to the bucket wheel 7 starts to be 0.
  • the revolution speed of the cavity carrier 104 increases, the resistance of the internal fluid 16 to the bucket wheel 7 in the bucket chamber
  • the multiplication is multiplied, and the output sun gear 10 drives the output shaft 11 to rotate, and the output shaft 11 outputs power.
  • the stepless transmission of the first embodiment is free from external resistance and starts at zero speed; in the middle of starting, the resistance of the combination of the bucket wheel 7 is uniformly increased, and finally the output end planetary gear 15 drives the output shaft through the output sun gear 10 11 flexible start; rated working condition, speed and torque are relatively stable, the bucket wheel 7 is not balanced by the force balance, the gears between each other do not rotate, the whole realizes the synchronous transmission of power, and approaches the 1:1 transmission; when the force is unbalanced The torque and speed balance are automatically adjusted.
  • the output torque of the continuously variable transmission output shaft 11 of the first embodiment is four times the maximum torque provided by the input shaft 1.
  • the number of teeth of the input sun gear 2 and the number of teeth of the input end planetary gear 3 and the transmission ratio of other transmissions can be changed, thereby optimizing the torque required for the adjustment and realizing various output of the rotation speed and the torque.
  • the input planetary gear set 101 is provided with a cavity carrier 104 inside, and the cavity carrier 104 includes A cavity input end cover 6, a cavity output end cover 13, a cavity input end cover 6 and a cavity output end cover 13 are fixedly provided with a bucket wheel cavity housing 14, a cavity output end cover 13 and a bucket wheel cavity
  • An output end planetary gear set 102 is disposed between the body casings 14;
  • the input end planetary gear set 101 includes an input end of a sun gear 2 and three input end planetary gears 3, and an input shaft 1 is provided between the input end sun gear 2, and the input
  • the end sun gear 2 is meshed with the input end planetary gear 3, and the planetary gear connecting shaft 4 is arranged in the middle of the input end planetary gear 3.
  • the planetary gear connecting shaft 4 passes through the cavity input end cover 6 and the bucket wheel cavity housing 14, the planet The wheel connecting shaft 4 is in rotational connection with the cavity input end cover 6 and the bucket wheel housing casing 14;
  • the bucket wheel planetary gear set 103 comprises a bucket wheel sun gear 9 and nine bucket wheel planet wheels 8, the bucket wheel sun gear 9
  • the meshing wheel 8 is meshed with the bucket wheel, and the output shaft 11 is disposed in the middle of the bucket wheel sun gear 9.
  • the output shaft 11 passes through the cavity output end cover 1 3.
  • the output shaft 11 and the cavity output end cover 13 are rotatably connected, and the bucket wheel planetary wheel 8 is provided with a bucket wheel planetary axle 17, and the bucket wheel planetary axle 17 passes through the cavity output end cover 13 and the bucket wheel housing 14
  • the bucket wheel planetary axle 17 is rotatably connected to the cavity output end cover 13 and the bucket wheel cavity housing 14.
  • the other end of the bucket wheel planetary axle 17 is rotatably connected to the cavity input end cover 6, and the bucket wheel housing 14 is connected.
  • the inner bucket wheel planetary axle 17 is fixedly provided with nine bucket wheels 7;
  • the output planetary gear set 102 includes an output sun gear 10 and three output planetary gears 15, an output sun gear 10 and an output planetary gear 15
  • the output planetary gear 15 is fixedly connected to the planetary gear connecting shaft 4 passing through the cavity input end cover 6 and the bucket wheel housing 14 , and the output sun gear 10 and the output through the cavity output end cover 13
  • the shaft 11 is fixedly connected, and the bucket wheel housing 14 contains an appropriate amount of oil 16 inside the bucket wheel chamber.
  • the second embodiment is based on the first embodiment, and the planetary wheel connecting shaft 4 is moved from the outside of the original bucket wheel housing 14 to the inside of the bucket wheel housing 14, and the center of the bucket wheel housing 14 is The bucket wheel 7 is cancelled, thereby bringing the gear diameter of the input planetary gear set 101 and the output planetary gear set 102 to be small, but the mutual diameter ratio is not affected; the bucket wheel planetary gear set 103 and the output planetary gear The group 102 is interchanged; the outer diameter of the bucket wheel planetary gear set 103 is increased, the number of the bucket wheel 7 is increased, the centrifugal acceleration of the oil 16 in the bucket wheel chamber is increased, and the bucket wheel 7 is subjected to liquid gravity, liquid viscosity, and liquid.
  • the power is increased; the bushing 12 and the bucket wheel housing 14 are combined into a bucket wheel housing 14 .
  • the number of teeth of the input sun gear 2 is 20, the number of teeth of the input planetary gear 3 is 40; the number of teeth of the output planetary gear 15 is 20, and the number of teeth of the output sun gear 10 is 40.
  • the output shaft 11 outputs torque in a range that is four times the torque provided by the input shaft 1.
  • the number of teeth of the bucket wheel planetary gear 8 is 25, the number of teeth of the bucket wheel sun gear 9 is 75, and the maximum balance torque range that the bucket wheel gear set 103 can provide to the output shaft 11 is that the bucket wheel 7 is combined with the oil inside the bucket wheel chamber. Three times the resistance torque.
  • the running process is: when starting, set the power clockwise input, the power is input from the input shaft 1, the input sun gear 2 rotates clockwise, and the input sun gear 2 drives the input end planetary gear 3 to rotate counterclockwise, through the fixed connection
  • the planetary wheel connects the shaft 4, and drives the output planetary gear 15 to rotate.
  • the sun gear 10 receives the resistance from the output shaft 11, and the output planetary gear 15 revolves counterclockwise around the output sun gear 10 to drive the cavity carrier 104. Counterclockwise revolution, which in turn drives the bucket wheel planetary gear 8 to rotate counterclockwise, and then drives the bucket wheel 7 to rotate counterclockwise.
  • the counterclockwise rotation speed of the bucket wheel 7 exceeds the counterclockwise revolution number of the cavity carrier 104, and the bucket wheel 7 Counterclockwise rotation is formed in the bucket wheel housing 14 by the resistance of the oil 16 inside the bucket wheel body to form a torque, which includes the liquid gravity formed by the revolution of the bucket wheel housing 14 and the fluid injection from the bucket wheel 7 is connected to the nozzle.
  • the hydraulic power of the bucket wheel 7 and the liquid adhesion force of the oil between the bucket wheel 7 and the bucket wheel housing 14 are transmitted to the bucket wheel sun by the variable diameter of the bucket wheel planet 8 and the bucket wheel sun wheel 9
  • the output shaft 11 of the wheel 9 is fixed, and the sun wheel 9 of the bucket wheel is outputted.
  • the stepless transmission of the second embodiment is free from external resistance and starts at zero speed; in the middle of starting, the resistance of the combination of the bucket wheel 7 is uniformly increased, and the final output planetary gear 15 drives the output shaft through the output sun gear 10 11 flexible start; rated working condition, speed and torque are relatively stable, the bucket wheel 7 is not balanced by the force balance, the gears between each other do not rotate, the whole realizes the synchronous transmission of power, and approaches the 1:1 transmission; when the force is unbalanced The torque and speed balance are automatically adjusted.
  • the output torque of the output shaft 11 of the continuously variable transmission is more than four times the torque provided by the input shaft 1.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Transmission Devices (AREA)
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Abstract

一种无级变速器，解决了液力同步双速器变矩斗轮与油液之间的平衡力有限，在增矩时，排空油液不具备柔性传动功能，且控制、制动等装置结构复杂的技术问题。该无级变速器，包括输入端行星齿轮组（101）和输出端行星齿轮组（102），输入端行星齿轮组（101）和输出端行星齿轮组（102）之间设有腔体行星架（104），腔体行星架（104）包括腔体输入端盖（6）、腔体输出端盖（13），腔体输入端盖（6）和腔体输出端盖（13）之间固定设有斗轮腔体壳体（14），输入端行星齿轮组（101）内侧与腔体输入端盖（6）连接，输出端行星齿轮组（102）内侧与腔体输出端盖（13）连接，斗轮腔体壳体（14）内部一侧设有斗轮行星齿轮组（103），该无级变速器可广泛应用于传动领域。

Description

无级变速器 技术领域
本发明涉及一种机械传动装置，特别是涉及一种柔性启动的无级变速器。
背景技术
在传动领域，变速器在汽车领域应用最为广泛。目前，汽车变速器按照操纵方式分为：手动变速器(MT)、自动变速器(AT)和手动自动一体变速器。随着汽车日新月异的快速发展，自动变速器由于其操纵简单已经逐步占领了汽车主流，而自动变速器汽车通过液力传递和齿轮组合的方式来达到变速的目的。
自动变速器又分为液力自动变速器(AT)、电控机械式自动变速器(AMT)和无级变速器(CVT)，其中应用最为广泛、装车率最多的部件是液力变矩器，但现有的变速器普遍存在以下问题：
(1)现有的手动变速器(MT)主要通过调节不同齿轮组合来更换挡位；现有的电控机械式自动变速器(AMT)在传统干式离合器和手动齿轮变速器的基础上，加装电子控制系统，将手动换档机构改造成自动换档机构，从而实现自动换档的有级式机械自动变速器，其缺点是不能提供柔性传动、无法实现无级变速、控制结构复杂。
(2)现有的液力变速器包括液力变矩器以及在液力变矩器基础上增加控制的变速器，如液力自动变速器(AT)，液力变矩器是动力通过壳体相连的泵轮，泵轮搅动变矩器中的油液，通过导轮带动涡轮转动，涡轮将动力输出，其缺点是当液力变矩器的泵轮和涡轮的转速差接近同步时，会丧失传动能力，无法实现同步；为了改善液力变矩器存在的以上问题，增加控制系统时，又带来系统复杂，制造成本高的问题。
(3)现有的无级变速器(CVT)采用传动摩擦力和工作直径可变的主、从动轮相配合的传动带来传递动力，可以实现传动比的连续改变， 从而得到传动系与发动机工况的最佳匹配，其缺点是不能提供柔性零启动，不能提供较大的扭力，受力变化频繁时，易打滑。
(4)现有国内专利授权号为CN 102606709B的专利液力同步双速器，该液力同步双速器工作时，驱动装置带动输入轴7驱动内箱体2转动，同时将存放于外箱体1内的工作液体利用工作泵输送到内箱体2中，在内箱体2刚刚开始转动时，由于输出轴8上载有负荷，使与输出轴8固定连接的大齿圈14不转动，行星轮11、换向轮12、斗轮轴10和斗轮9跟随内箱体支架19一起绕输出轴8公转；同时，斗轮9高速绕斗轮轴10自转。随着内箱体2的继续转动，容纳在内箱体2内的液体由于离心力的作用在内箱体2内形成圆环状液面。当液面达到预定高度时，液体进入各个斗轮成凹形的斗轮叶片22内。进入斗轮叶片22内的液体由于离心力的作用迫使斗轮9的自转速度逐渐下降直至自转停止，此过程中，输出轴8转速逐渐上升，最终输入轴7、内箱体2、行星轮11、斗轮9、换向轮、12、大齿圈14和输出轴8都以相同的速度转动，实现了负荷的软启动。以上可以看出，贴在内箱体2的内表面上的液体的液位决定了离心力的大小，而离心力的大小进一步决定了输出轴8能否与输入轴7同步旋转。输出轴8越趋于与输入轴7同步转动，输出轴8与输入轴7之间的滑差越小。如图7所示，液力同步双速器在工作过程中，电流互感器604测量的电机上的电流达到设定值，例如大于或等于120A时(步骤701)以及Pt100铂热电阻602测量的外箱体1或内箱体2内液体的温度达到设定的值，例如大于或等于70℃时(步骤703)，会将信号传递给单片机601，单片机601进而通过电磁制动器15控制制动轮16(步骤702)，制动轮16与太阳轮13开始啮合，从而对太阳轮13进行制动，太阳轮13进一步将制动力依次传递到换向轮12、行星轮11、大齿圈14，最后到达输出轴8，降低输出轴转速以增加扭矩；同时，单片机601将信号传递给电磁阀609，电磁阀609开启，通过固定勺管18和出油管路17将内箱体的液体排空，这样就减小了功率损失。在电磁制动器15制动后，整套参与制动的齿轮机构实际上就是一个常 用的行星齿轮减速器结构。
该液力同步双速器的缺点是，斗轮与油液之间的平衡力有限，只能在油液对斗轮的最大平衡力内变矩；输出轴需要大于油液与斗轮的最大平衡力所能提供扭矩时，需将内箱体的油液排空，参与制动的齿轮机构是一个常用的行星齿轮减速器结构，不具备柔性传动功能；整个控制系统属于电子控制系统，且控制、制动等装置结构复杂。
发明内容
本发明就是要解决现有的手动变速器(MT)不能提供柔性传动，控制复杂；液力变速器同步时丧失传动能力，不能同步；液力自动变速器控制系统复杂，成本高；无级变速器(CVT)不能提供柔性零启动，不能提供较大的扭力，受力变化频繁时，易打滑；液力同步双速器斗轮与油液之间的平衡力有限，只能在油液对斗轮的最大平衡力内变矩；输出轴需要大于油液与斗轮的最大平衡力所能提供扭矩时，需将内箱体的油液排空，参与制动的齿轮机构是一个常用的行星齿轮减速器结构，不具备柔性传动功能；整个控制系统属于电子控制系统，且控制、制动等装置结构复杂的技术问题，提供一种不仅能在油液对斗轮的最大平衡力内变矩，输出轴需要大于油液与斗轮的最大平衡力所能提供扭矩时，不需将内箱体的油液排空，不需要齿轮机构参与制动，实现连续变速和宽范围变矩，具备柔性传动功能，不需要再增加控制系统，结构简单的无级变速器。
为此，本发明的技术方案是，一种无级变速器，包括输入端行星齿轮组和输出端行星齿轮组，输入端行星齿轮组和输出端行星齿轮组之间设有腔体行星架，腔体行星架包括腔体输入端盖、腔体输出端盖，腔体输入端盖和腔体输出端盖之间固定设有斗轮腔体壳体，输入端行星齿轮组内侧与腔体输入端盖连接，输出端行星齿轮组内侧与腔体输出端盖连接，斗轮腔体壳体内部一侧设有斗轮行星齿轮组。
输入端行星齿轮组包括输入端太阳轮和输入端行星轮，输入端太阳 轮中间设有输入轴，输入端太阳轮与输入端行星轮啮合连接，输入端行星轮中间设有行星轮连接轴，行星轮连接轴穿过腔体输入端盖，与腔体输入端盖旋转连接，输入轴穿过腔体输入端盖，输入轴与腔体输入端盖旋转连接；行星轮连接轴穿过腔体输出端盖，行星轮连接轴与腔体输出端盖旋转连接。
输出端行星齿轮组包括输出端太阳轮和输出端行星轮，输出端太阳轮中间设有输出轴，输出端太阳轮和输出端行星轮啮合连接，输出端行星轮与穿过腔体输出端盖的行星轮连接轴固定连接；输出轴穿过腔体输出端盖进入斗轮腔体壳体内部，输出轴与腔体输出端盖旋转连接。
斗轮行星齿轮组包括斗轮太阳轮和斗轮行星轮，斗轮太阳轮和斗轮行星轮啮合连接，斗轮太阳轮与进入斗轮腔体壳体内部的输出轴固定连接；斗轮行星轮中间设有斗轮行星轮轴，斗轮行星轮轴一端设于腔体输出端盖上，斗轮行星轮轴另一端设有斗轮。
优选地，斗轮腔体壳体内部另一侧设有衬套，衬套与穿过腔体输入端盖的输入轴一侧旋转连接，斗轮行星轮轴穿过衬套，斗轮行星轮轴与衬套旋转连接。
优选地，输入端行星齿轮组的输入端行星轮为3个以上。
优选地，输出端行星齿轮组的输出端行星轮为3个以上。
优选地，斗轮行星齿轮组的斗轮行星轮为3个以上。
优选地，位于斗轮腔体壳体内部的输入轴上设有斗轮。
一种无级变速器，包括输入端行星齿轮组和斗轮行星齿轮组，输入端行星齿轮组内侧设有腔体行星架，斗轮行星齿轮组内侧设有输出端行星齿轮组；腔体行星架包括腔体输入端盖、腔体输出端盖，腔体输入端盖和腔体输出端盖之间固定设有斗轮腔体壳体；
输入端行星齿轮组包括输入端太阳轮和输入端行星轮，输入端太阳轮中间设有输入轴，输入端太阳轮与输入端行星轮啮合连接，输入端行星轮中间设有行星轮连接轴，行星轮连接轴穿过腔体输入端盖和斗轮腔体壳体，行星轮连接轴与腔体输入端盖和斗轮腔体壳体为旋转连接；
斗轮行星齿轮组包括斗轮太阳轮和斗轮行星轮，斗轮太阳轮和斗轮行星轮啮合连接，斗轮太阳轮中间设有输出轴，输出轴穿过腔体输出端盖，输出轴和腔体输出端盖旋转连接，斗轮行星轮中间设有斗轮行星轮轴，斗轮行星轮轴穿过腔体输出端盖和斗轮腔体壳体，斗轮行星轮轴和腔体输出端盖和斗轮腔体壳体旋转连接，位于斗轮腔体内部的斗轮行星轮轴上设有斗轮；
输出端行星齿轮组包括输出端太阳轮和输出端行星轮，输出端太阳轮和输出端行星轮啮合连接，输出端行星轮与穿过腔体输入端盖和斗轮腔体壳体的行星轮连接轴固定连接，输出端太阳轮与穿过腔体输出端盖的输出轴固定连接。
优选地，输入端行星齿轮组的输入端行星轮为3个以上。
优选地，输出端行星齿轮组的输出端行星轮为3个以上。
优选地，斗轮行星齿轮组的斗轮行星轮为3个以上。
本发明有益效果是，由于无级变速器包括输入端行星齿轮组和输出端行星齿轮组，输入端行星齿轮组和输出端行星齿轮组之间设有腔体行星架，腔体行星架包括腔体输入端盖、腔体输出端盖，腔体输入端盖和腔体输出端盖之间固定设有斗轮腔体壳体，输入端行星齿轮组内侧与腔体输入端盖连接，输出端行星齿轮组内侧与腔体输出端盖连接，斗轮腔体壳体内部一侧设有斗轮行星齿轮组，在启动时可以实现零速启动和无外阻力启动，传动过程柔性，可实现增矩成倍设定，变矩范围大，额定工况同步，不需要控制装置，自适应调节，实现大范围扭矩与速度的自动匹配，可实现大功率柔性传动场合。
附图说明
图1是本发明实施例1的轴测图；
图2是本发明实施例1的另一轴侧图；
图3是本发明实施例1的主视图；
图4是本发明实施例1的后视图；
图5是本发明实施例1的侧视图；
图6是本发明实施例2的示意图；
图7是本发明实施例2的主视图；
图8是本发明实施例2的轴测图；
图9是本发明实施例2的另一轴测图。
图中符号说明：
101、输入端行星齿轮组；102、输出端行星齿轮组；103、斗轮行星齿轮组；104、腔体行星架；1、输入轴；2、输入端太阳轮；3、输入端行星轮；4、行星轮连接轴；5、轴承；6、腔体输入端盖；7、斗轮；8、斗轮行星轮；9、斗轮太阳轮；10、输出端太阳轮；11、输出轴；12、衬套；13、腔体输出端盖；14、斗轮腔体壳体；15、输出端行星轮；16、斗轮腔体内部油液；17、斗轮行星轮轴。
具体实施方式
下面结合实施例对本发明做进一步描述。
实施例1
如图1-图5所示，是本发明一种无级变速器的一种实施例，设有输入端行星齿轮组101和输出端行星齿轮组102，输入端行星齿轮组101和输出端行星齿轮组102之间设有腔体行星架104，腔体行星架104包括腔体输入端盖6、腔体输出端盖13，腔体输入端盖6和腔体输出端盖13之间固定设有斗轮腔体壳体14，输入端行星齿轮组101内侧与腔体输入端盖6连接，输出端行星齿轮组102内侧与腔体输出端盖13连接，斗轮腔体壳体14内部一侧设有斗轮行星齿轮组103；输入端行星齿轮组101包括一个输入端太阳轮2和三个输入端行星轮3，输入端太阳轮2中间设有输入轴1，输入端太阳轮2与输入端行星轮3啮合连接，输入端行星轮3中间设有行星轮连接轴4，行星轮连接轴4穿过腔体输入端盖6，行星轮连接轴4与腔体输入端盖6旋转连接，输入轴1穿过腔体输入端盖6，输入轴1与腔体输入端盖6旋转连接；行星轮连接轴4穿过腔体输出端盖6， 行星轮连接轴4与腔体输出端盖6旋转连接；输出端行星齿轮组102包括一个输出端太阳轮10和三个输出端行星轮15，输出端太阳轮10中间设有输出轴11，输出端太阳轮10和输出端行星轮15啮合连接，输出端行星轮15与穿过腔体输出端盖13的行星轮连接轴4固定连接；输出轴11穿过腔体输出端盖13进入斗轮腔体壳体14内部，输出轴11与腔体输出端盖13旋转连接；斗轮行星齿轮组103包括一个斗轮太阳轮9和六个斗轮行星轮8，斗轮太阳轮9和斗轮行星轮8啮合连接，斗轮太阳轮9与进入斗轮腔体壳体14内部的输出轴11固定连接；斗轮行星轮8中间设有斗轮行星轮轴17，斗轮行星轮轴17一端设于腔体输出端盖13上旋转连接，斗轮行星轮轴17另一端设于腔体输入端盖6上旋转连接，斗轮腔体壳体14内部的斗轮行星轮轴17上固定设有斗轮7；斗轮腔体壳体14内部另一侧设有衬套12，衬套12与穿过腔体输入端盖6的输入轴1一侧旋转连接，斗轮行星轮轴17穿过衬套12，斗轮行星轮轴17与衬套12旋转连接，衬套12与腔体输入端盖6之间含有适量斗轮腔体内部油液16，斗轮腔体壳体14内部的输入轴1上设有斗轮7。
斗轮行星轮8和斗轮7也可以做成一体结构，斗轮7另一端可以采取悬臂结构，也可以采用支撑结构，适应各种体积要求不同的变速器。
本实施例中，输入端太阳轮2的齿数是35，输入端行星轮3的齿数是70；输出端行星轮15的齿数是35，输出端太阳轮10的齿数是70。输出轴11输出扭矩的范围是输入轴1提供扭矩的4倍。
斗轮行星轮8的齿数是20，斗轮太阳轮9的齿数是50，斗轮齿轮组103可提供给输出轴11的最大平衡扭矩范围是斗轮7组合受到斗轮腔体内部油液16阻力扭矩的2.5倍。
其运行过程是：启动时，设定动力顺时针输入，动力从输入轴1输入，带动输入端太阳轮2顺时针旋转，输入端太阳轮2带动输入端行星轮3逆时针旋转，通过固连的行星轮连接轴4，带动输出端行星轮15旋转，在输出端太阳轮10受到来自输出轴11的阻力，输出端行星轮15绕输出端太阳轮10逆时针公转，带动腔体行星架104的逆时针公转，进而 带动斗轮行星轮8逆时针自转，进而带动斗轮7逆时针自转，斗轮7逆时针自转转数超出腔体行星架104逆时针公转转数，斗轮7逆时针自转在斗轮腔体壳体14内受斗轮腔体内部油液16阻力形成扭矩，此阻力包括斗轮腔体壳体14公转形成的液重力、离开斗轮7油液喷射给相连斗轮7的液动力和斗轮7与斗轮腔体壳体14之间油液的液粘力，扭矩通过斗轮行星轮8和斗轮太阳轮9的变径成倍传输给斗轮太阳轮9固连的输出轴11，斗轮太阳轮9受输出轴11阻力不动，根据牛顿第三定律，此扭矩转化为阻止腔体行星架104逆时针公转的扭矩，进而带动输出端行星轮15对输出端太阳轮10受力，输出端太阳轮10带动输出轴11输出动力，斗轮腔体内部油液16对斗轮7的阻力开始是0，随着腔体行星架104公转速度增大，斗轮腔体内部油液16对斗轮7的阻力成倍增大，进而输出端太阳轮10带动输出轴11旋转，进而通过输出轴11输出动力。
上述过程：启动初期，本实施例1无级变速器不受外界阻力，零速启动；启动中期，斗轮7组合受到的阻力匀速提升，最终输出端行星轮15通过输出端太阳轮10驱动输出轴11柔性启动；额定工况，速度与扭矩相对稳定，斗轮7受力平衡不自转，相互间的齿轮不转动，整体实现动力的同步传输，趋近于1∶1传动；受力不平衡时，自动调节扭矩与速度平衡，本实施例1无级变速器输出轴11输出扭矩是输入轴1提供最大扭矩的4倍。
可以根据不同应用领域的需要，改变输入端太阳轮2的齿数和输入端行星轮3的齿数以及其它传动付的传动比，从而优化调整需要达到的扭矩大小，实现多种转速和扭矩的输出。
实施例2
图6-图9是本发明的实施例2，设有输入端行星齿轮组101和斗轮行星齿轮组103，输入端行星齿轮组101内侧设有腔体行星架104，腔体行星架104包括腔体输入端盖6、腔体输出端盖13，腔体输入端盖6和腔体输出端盖13之间固定设有斗轮腔体壳体14，腔体输出端盖13和斗轮腔体壳体14之间设有输出端行星齿轮组102；输入端行星齿轮组101包 括输入端一个太阳轮2和三个输入端行星轮3，输入端太阳轮2中间设有输入轴1，输入端太阳轮2与输入端行星轮3啮合连接，输入端行星轮3中间设有行星轮连接轴4，行星轮连接轴4穿过腔体输入端盖6和斗轮腔体壳体14，行星轮连接轴4与腔体输入端盖6和斗轮腔体壳体14为旋转连接；斗轮行星齿轮组103包括一个斗轮太阳轮9和九个斗轮行星轮8，斗轮太阳轮9和斗轮行星轮8啮合连接，斗轮太阳轮9中间设有输出轴11，输出轴11穿过腔体输出端盖13，输出轴11和腔体输出端盖13旋转连接，斗轮行星轮8中间设有斗轮行星轮轴17，斗轮行星轮轴17穿过腔体输出端盖13和斗轮腔体壳体14，斗轮行星轮轴17与腔体输出端盖13和斗轮腔体壳体14旋转连接，斗轮行星轮轴17另一端设于腔体输入端盖6上旋转连接，斗轮腔体壳体14内部的斗轮行星轮轴17上固定设有九个斗轮7；输出端行星齿轮组102包括一个输出端太阳轮10和三个输出端行星轮15，输出端太阳轮10和输出端行星轮15啮合连接，输出端行星轮15与穿过腔体输入端盖6和斗轮腔体壳体14的行星轮连接轴4固定连接，输出端太阳轮10与穿过腔体输出端盖13的输出轴11固定连接，斗轮腔体壳体14内含有适量斗轮腔体内部油液16。
实施例2是在实施例1的基础上，将行星轮连接轴4由原来的斗轮腔体壳体14的外部内移到斗轮腔体壳体14内部，斗轮腔体壳体14中心斗轮7取消，由此带来的是输入端行星齿轮组101、输出端行星齿轮组102的齿轮直径变小，但是相互的直径比例不受影响；斗轮行星齿轮组103与输出端行星齿轮组102位置互换；斗轮行星齿轮组103外径变大，斗轮7数量增多，斗轮腔体内部油液16离心加速度变大，斗轮7因此受到的液重力、液粘力、液动力增大；衬套12与斗轮腔体壳体14合并为斗轮腔体壳体14。
本实施例2中，输入端太阳轮2的齿数是20，输入端行星轮3的齿数是40；输出端行星轮15的齿数是20，输出端太阳轮10的齿数是40。输出轴11输出扭矩的范围是输入轴1提供扭矩的4倍。
斗轮行星轮8的齿数是25，斗轮太阳轮9的齿数是75，斗轮齿轮组 103可提供给输出轴11的最大平衡扭矩范围是斗轮7组合受到斗轮腔体内部油液16阻力扭矩的3倍。
其运行过程是：启动时，设定动力顺时针输入，动力从输入轴1输入，带动输入端太阳轮2顺时针旋转，输入端太阳轮2带动输入端行星轮3逆时针旋转，通过固连的行星轮连接轴4，带动输出端行星轮15旋转，在输出端太阳轮10受到来自输出轴11的阻力，输出端行星轮15绕输出端太阳轮10逆时针公转，带动腔体行星架104的逆时针公转，进而带动斗轮行星轮8逆时针自转，进而带动斗轮7逆时针自转，斗轮7逆时针自转转数超出腔体行星架104逆时针公转转数，斗轮7逆时针自转在斗轮腔体壳体14内受斗轮腔体内部油液16阻力形成扭矩，此阻力包括斗轮腔体壳体14公转形成的液重力、离开斗轮7油液喷射给相连斗轮7的液动力和斗轮7与斗轮腔体壳体14之间油液的液粘力，扭矩通过斗轮行星轮8和斗轮太阳轮9的变径成倍传输给斗轮太阳轮9固连的输出轴11，斗轮太阳轮9受输出轴11阻力不动，根据牛顿第三定律，此扭矩转化为阻止腔体行星架104逆时针公转的扭矩，进而带动输出端行星轮15对输出端太阳轮10受力，输出端太阳轮10带动输出轴11受力，斗轮腔体内部油液16对斗轮7的阻力开始是0，随着腔体行星架104公转速度增大，斗轮腔体内部油液16对斗轮7的阻力成倍增大，形成输出端太阳轮10带动输出轴11旋转，进而通过输出轴11输出动力。
上述过程：启动初期，本实施例2无级变速器不受外界阻力，零速启动；启动中期，斗轮7组合受到的阻力匀速提升，最终输出端行星轮15通过输出端太阳轮10驱动输出轴11柔性启动；额定工况，速度与扭矩相对稳定，斗轮7受力平衡不自转，相互间的齿轮不转动，整体实现动力的同步传输，趋近于1∶1传动；受力不平衡时，自动调节扭矩与速度平衡，本实施例2无级变速器输出轴11输出扭矩的范围是输入轴1提供扭矩的4倍以上。
惟以上所述者，仅为本发明的具体实施例而已，当不能以此限定本发明实施的范围，故其等同组件的置换，或依本发明专利保护范围所作 的等同变化与修改，皆应仍属本发明权利要求书涵盖之范畴。

Claims (10)

  1. 一种无级变速器，包括输入端行星齿轮组和输出端行星齿轮组，其特征是：所述输入端行星齿轮组和输出端行星齿轮组之间设有腔体行星架，所述腔体行星架包括腔体输入端盖、腔体输出端盖，所述腔体输入端盖和腔体输出端盖之间固定设有斗轮腔体壳体，所述输入端行星齿轮组内侧与腔体输入端盖连接，所述输出端行星齿轮组内侧与腔体输出端盖连接，所述斗轮腔体壳体内部一侧设有斗轮行星齿轮组；
    所述输入端行星齿轮组包括输入端太阳轮和输入端行星轮，所述输入端太阳轮中间设有输入轴，所述输入端太阳轮与输入端行星轮啮合连接，所述输入端行星轮中间设有行星轮连接轴，所述行星轮连接轴穿过腔体输入端盖，所述行星轮连接轴与腔体输入端盖旋转连接，所述输入轴穿过腔体输入端盖，所述输入轴与腔体输入端盖旋转连接；所述行星轮连接轴穿过腔体输出端盖，所述行星轮连接轴与腔体输出端盖旋转连接；
    所述输出端行星齿轮组包括输出端太阳轮和输出端行星轮，所述输出端太阳轮中间设有输出轴，所述输出端太阳轮和输出端行星轮啮合连接，所述输出端行星轮与穿过腔体输出端盖的行星轮连接轴固定连接；所述输出轴穿过腔体输出端盖进入斗轮腔体壳体内部，所述输出轴与腔体输出端盖旋转连接；
    所述斗轮行星齿轮组包括斗轮太阳轮和斗轮行星轮，所述斗轮太阳轮和斗轮行星轮啮合连接，所述斗轮太阳轮与进入斗轮腔体壳体内部的输出轴固定连接；所述斗轮行星轮中间设有斗轮行星轮轴，所述斗轮行星轮轴一端设于腔体输出端盖上，所述斗轮行星轮轴另一端设有斗轮。
  2. 根据权利要求1所述的无级变速器，其特征在于：所述斗轮腔体壳体内部的斗轮行星齿轮组一侧设有衬套，所述衬套与穿过腔体输入端盖的输入轴一侧旋转连接，所述斗轮行星轮轴穿过衬套，所述斗轮行星轮轴与衬套旋转连接。
  3. 根据权利要求1或2所述的无级变速器，其特征在于：所述输入端行星齿轮组的输入端行星轮为3个以上。
  4. 根据权利要求1或2所述的无级变速器，其特征在于：所述输出端行星齿轮组的输出端行星轮为3个以上。
  5. 根据权利要求1或2所述的无级变速器，其特征在于：所述斗轮行星齿轮组的斗轮行星轮为3个以上。
  6. 根据权利要求1或2所述的无级变速器，其特征在于：所述位于斗轮腔体壳体内部的输入轴上设有斗轮。
  7. 一种无级变速器，包括输入端行星齿轮组和斗轮行星齿轮组，其特征是：所述输入端行星齿轮组内侧设有腔体行星架，所述腔体行星架包括腔体输入端盖、腔体输出端盖，所述腔体输入端盖和腔体输出端盖之间固定设有斗轮腔体壳体，所述腔体输出端盖和斗轮腔体壳体之间设有输出端行星齿轮组；
    所述输入端行星齿轮组包括输入端太阳轮和输入端行星轮，所述输入端太阳轮中间设有输入轴，所述输入端太阳轮与输入端行星轮啮合连接，所述输入端行星轮中间设有行星轮连接轴，所述行星轮连接轴穿过腔体输入端盖和斗轮腔体壳体，所述行星轮连接轴与腔体输入端盖和斗轮腔体壳体为旋转连接；
    所述斗轮行星齿轮组包括斗轮太阳轮和斗轮行星轮，所述斗轮太阳轮和斗轮行星轮啮合连接，所述斗轮太阳轮中间设有输出轴，所述输出轴穿过腔体输出端盖，所述输出轴和腔体输出端盖旋转连接，所述斗轮行星轮中间设有斗轮行星轮轴，所述斗轮行星轮轴穿过腔体输出端盖和斗轮腔体壳体，所述斗轮行星轮轴和腔体输出端盖和斗轮腔体壳体旋转连接，所述位于斗轮腔体内部的斗轮行星轮轴上设有斗轮；
    所述输出端行星齿轮组包括输出端太阳轮和输出端行星轮，所述输出端太阳轮和输出端行星轮啮合连接，所述输出端行星轮与穿过腔体输入端盖和斗轮腔体壳体的行星轮连接轴固定连接，所述输出端太阳轮与穿过腔体输出端盖的输出轴固定连接。
  8. 根据权利要求7所述的无级变速器，其特征在于：所述输入端行星齿轮组的输入端行星轮为3个以上。
  9. 根据权利要求7所述的无级变速器，其特征在于：所述输出端行星齿轮组的输出端行星轮为3个以上。
  10. 根据权利要求7所述的无级变速器，其特征在于：所述斗轮行星齿轮组的斗轮行星轮为3个以上。
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