WO2007079694A1 - Gear type steeping stepless speed change device - Google Patents

Abstract

A gear type stepping stepless speed change device includes a planet gear system and a one-way bearing (i.e. one-way clutch). The planet gear system includes a drive sun gear and 3-6 output planet gears. The drive sun gear connects with the power input end. The output planet gears mesh with the drive sun gear along its periphery and are installed on the planet gear carrier. The planet gear carrier fixedly connects with the power outlet end. All the output planet gears mesh with the first teeth ring, and a one-way bearing is mounted on the first teeth ring. The output planet gears and the planet gear carrier are the output end, and the teeth ring serves as the input end when the speed changes. The revolution speed of the planet gear carrier is the output speed, and the drive sun gear serves as the input end. The power for driving the teeth ring can be got from the input shaft. The rotation direction of the teeth ring is the same as that of the drive sun gear. The one-way bearing is installed on the teeth ring or the member which fixedly connects with the teeth ring, therefore the teeth ring can only rotate in one direction. The structure is simple, and the range of speed transmission is wide.

Description

 Gear stepless continuously variable transmission device

 The present invention relates to a shifting device, and more particularly to a gear stepless continuously variable transmission having a simple structure and a large shift range.

Background technique

 With the further deepening of the industrialization process, the transmission is widely used in various occasions and fields, and the most common is used in various vehicles and other mechanical equipment. The transmission is available in both stepped and stepless versions, and most of today's automotive applications use step-variable transmissions. Since the efficiency of the step-variable transmission is not as efficient as that of the continuously variable transmission, a reliable and durable continuously variable transmission has been researched and developed in the automobile manufacturing industry to replace the existing stepped transmission. Nowadays, the continuously variable transmission used in automobiles, only the steel belt type continuously variable transmission is known to be used in a small amount, and its superior performance is unparalleled in the step-variable transmission, but there are also some problems such as easy slippage, Large wear, short life, difficult to apply in large displacement vehicles. Therefore, people have been researching and developing all the time, and strive to develop a continuously variable transmission that can make up for the above shortcomings.

Summary of the invention

 SUMMARY OF THE INVENTION An object of the present invention is to provide a gear stepless continuously variable transmission having a simple structure and a large shift range.

 In order to achieve the above object, the present invention is achieved by the following scheme:

 A gear stepless continuously variable transmission device mainly comprises a planetary gear train and a one-way bearing, that is, a one-way clutch, the gear train includes an active sun gear connected to a power input end, and has 3 to 6 outputs engaged along the periphery of the active sun gear The planetary gear, the output planetary gear is mounted on the planetary carrier, the planetary carrier is fixedly connected with the power output end, the output planetary gears are cooperating in a ring gear, and the one-way bearing is a one-way clutch disposed on the ring gear.

 As an improvement to the above solution, an input shaft is fixedly connected to the axis of the active sun gear, and the planetary carrier is fixedly connected to an output shaft, and a speed regulating sun gear is further arranged on the input shaft, and the outer gear of the speed regulating sun wheel has 3 Up to 6 speed-adjusting planetary gears, the speed-adjusting planetary gears are mounted on the planetary carrier, the planetary carrier is fixedly connected with the input shaft, and the speed-adjusting planetary gears are meshed together in the ring gear. The one-way bearing is a one-way clutch and a ring gear. The speed control sun gear, the active sun gear, the planetary carrier, and the output shaft and input shaft are set to the same axis.

At the same time, the above scheme can also be improved as follows: an input is fixedly connected at the center of the active sun gear. The shaft, the planetary wheel frame is fixedly connected to an output shaft, and the speed regulating sun wheel is further arranged on the input shaft, and the speed regulating sun gear is externally meshed with 3 to 6 speed regulating planetary wheels, and the speed regulating planetary wheels are mounted on the planetary wheel carrier. The revolutionary planetary wheel has a revolution diameter larger than the revolution diameter of the planetary gear, and each of the output planetary gears meshes with the ring gear, and an output sun gear is fixed on the output shaft, and the output sun gear is externally meshed with 3 to 6 planetary gears, and the planetary gear The planetary carrier is fixed in the ring gear, and the speed regulating planetary gear and the planetary gear are internally meshed in a ring gear. The first ring gear, the second ring gear, the one-way bearing, that is, the one-way clutch, the speed regulating sun gear, the active sun gear, the output sun gear, the planetary carrier, and the output shaft and the input shaft are arranged in the same axis.

 For the same inventive concept, the present invention provides another improvement. The input shaft is fixedly connected to the active sun gear axis, the planetary carrier is fixedly connected to an output shaft, and the second speed regulating sun is further disposed on the output shaft. The second speed-regulating sun gear has 3 to 6 speed-adjusting planetary gears, and each speed-adjusting planetary wheel is mounted on the planetary carrier, and each output planetary gear meshes with the first ring gear, and the first input ring has a first A speed regulating sun gear, the first speed regulating sun gear is externally meshed with 3 to 6 planetary gears, the planetary wheel carrier of the planetary gear is fixed on the first ring gear, and the speed regulating planetary wheel and the planetary gear are internally meshed with a second In the ring gear. The second ring gear, the first ring gear, the one-way bearing, that is, the one-way clutch, the first speed regulating sun gear, the active sun gear, the second speed regulating sun gear, the planetary carrier, and the output shaft and the input shaft are set to the same axis .

 Also in the premise of the same inventive concept, the present invention can also be improved as follows: an input shaft is fixedly coupled to the center axis of the active sun gear, the planetary carrier is fixedly coupled to an output shaft, and a first speed regulating sun gear is further disposed on the input shaft. The first speed regulating sun gear has 3 to 6 speed-adjusting planetary gears, and each speed-adjusting planetary wheel is mounted on the planetary carrier. The revolution diameter of the speed-regulating planetary gear is larger than the revolution diameter of the planetary gear, and each output planetary gear Engaging with the first ring gear, a second speed regulating sun wheel that is rotatable relative to the output shaft is mounted coaxially on the output shaft, and the second speed regulating sun gear is externally engaged with 3 to 6 planet wheels, and the planet carrier of the planet gear Fixed in the first ring gear, the speed governing planet and the planet gear are internally meshed in a second ring gear. The second ring gear, the first ring gear, the one-way bearing, that is, the one-way clutch, the first speed regulating sun gear, the active sun gear, the second speed regulating sun gear, the planetary carrier, and the output shaft and the input shaft are set to the same axis .

Similarly, under the premise that the same invention can be conceived, an input shaft is fixedly connected to the axis of the active sun gear, the planetary carrier is fixedly connected with an output shaft, and the first speed regulating sun wheel is arranged on the input shaft, and the first speed regulating sun The outer circumference of the wheel is engaged with 3 to 6 speed-adjusting planetary gears, the speed-adjusting planetary gears are fixed on the planetary carrier, and the output planetary gears mesh with the first ring gear, and a planetary carrier is fixed on the first ring gear, the wheel carrier There are 3 to 6 planetary gears on the outer side; a second ring gear is also meshed on the outer periphery of the speed-adjusting planetary gear, the planet The wheel meshes with the outer circumference of the second ring gear, and a third ring gear is also engaged on the outer circumference of the planetary wheel. The first ring gear, the second ring gear, the third ring gear, the one-way bearing, that is, the one-way clutch and the first speed regulating sun gear , active sun gear, planetary carrier and output shaft, input shaft set for the same axis

 The progressive stepless speed change device of the present invention, by the combination of the one-way bearing and the ring gear, produces a stepping effect in the fast and slow alternate driving, thereby realizing the stepless shifting form of the gear stage. This device can change the output speed and torque in time, and can continuously and continuously change the output so that the output can run to the best condition and the shift range is wide (should be designed). The engine's power output can be achieved at the best and high efficiency at any time, improving efficiency, reducing fuel consumption, reducing engine load, reducing exhaust emissions, and solving the problem of diesel smoke caused by the load of black smoke. Play an environmentally friendly role. The utility model has the advantages of simple structure, low manufacturing cost, less control components, convenient stepping and shifting operation, good inertia, high power transmission, wide range shifting, high precision adjustment, high transmission efficiency, wide application range, reliable operation and service life. long.

DRAWINGS

 1 is a schematic structural view of a basic stepping principle of the present invention; FIG. 2 is a schematic diagram of a basic structure of the present invention; FIG. 3 is a schematic diagram of another basic structure of the present invention; Figure 5 is a schematic structural view of a second embodiment of the present invention; Figure 6 is a schematic structural view of a third embodiment of the present invention; and Figure 7 is a schematic structural view of a fourth embodiment of the present invention; Five structural diagrams.

detailed description

 For ease of understanding, the structural principle of the present invention will be further described in detail below with reference to specific embodiments and the accompanying drawings:

 Firstly, the stepping principle and the basic structure are described. As shown in FIG. 1, FIG. 2 and FIG. 3, the present invention is a relatively simple structural form, which mainly comprises a planetary gear train and a one-way bearing, that is, a one-way clutch. The basic device structure. The gear train includes an active sun gear 31 connected to the power input end, and three to six output planetary gears 41 are meshed along the periphery of the active sun gear 31. The output planetary gears 41 are mounted on the planetary carrier 51, the planetary carrier 51 and the power output end. In connection, each of the output planet gears 41 is internally meshed in a first ring gear 101. The first ring gear 101 is further provided with a one-way bearing 111, which is a one-way bearing that realizes one-way rotation of the first ring gear 101.

The invention relates to a gear stepless stepless speed change device, which has good inertia and mechanical form stepping speed increasing effect. The output planetary gear 41 and the planetary carrier 51 are output ends, the revolution speed of the planetary carrier 51 is the output rotational speed, the active sun gear 31 is the input end, and the first ring gear 101 is used as the shifting speed. For the input end, the power for driving the first ring gear 101 can be taken from the input shaft or the output shaft, and the first ring gear 101 rotates in the same direction as the active sun gear 31. The one-way bearing, that is, the one-way clutch 111, is a member that is fitted over the first ring gear 101 or fixed to the first ring gear 101, so that the first ring gear 101 can only rotate in one direction. The ratio of the rotational speed of the first ring gear 101 to the revolution of the output planetary gear 41 is 1:0.7. The speed ratio of the rotational speed of the active sun gear 31 and the output planetary gear 41 is set to 3. 5:1. If the rotational speed of the active sun gear 31 is constant at a certain value, such as 1000 rpm, the first ring gear 101 is not added to the operation, at this time, the rotational speed of the output planetary gear 41 is 286 rpm, and the rotational speed of the output end is the most. Slow, the most torque. When the rotational speed of the output end is to be increased, only the first ring gear 101 has a certain rotational speed, and the rotational speed of the first ring gear 101 is applied to the output end by the speed ratio of the planetary gear 41, such as the first ring gear. When the rotational speed of 101 is 200 rpm, the revolution of the output planetary gear 41 is increased by 200 rpm / θ θ. 7 = 140 rpm, plus the original output planetary gear 41 revolution 286 rpm, The revolution of the output planetary gear 41 is increased to 286 rpm / 140 rpm / 426 rpm, and the overall output speed is increased. If the first ring gear 101 is added at 1400 rpm, the revolution of the output planet 41 reaches 1266 rpm, and the output speed reaches a high speed.

 During the entire step-shifting process from low speed to high speed (except for the lowest and highest speeds), the operation of the first ring gear 101 is constantly alternated and changed between rotation and pause. The specific situation is as follows: When the speed is increased or stabilized at a certain speed, and because the resistance of the output end is overcome, the torque of the first ring gear 101 cannot overcome the resistance, and the one-way bearing, that is, the one-way clutch 111 is automatically The first ring gear 101 is locked so that it cannot be reversed (resistance bounce), so that the active sun gear 31 has a short and stable borrowing point to drive the rotation of the output planet gear 41 and drive the output planet carrier 51. In the revolution, until the resistance of the output carrier 51 decreases, the rotation of the first ring gear 101 is advanced. When the first ring gear 101 cannot overcome the resistance of the output end, the one-way bearing, that is, the one-way clutch 111 automatically locks the first. A ring gear 101 makes it impossible to reverse (resistance bounce), and the resistance at the output end is overcome by the active sun gear and the output planet gear 41. The resistance to the output is reduced, and the first ring gear 101 is again advanced. In the process, when the resistance is large, the span of the advance is small, and the span of the resistance hour is large, which produces the consistency of the speed ratio from the low speed to the high speed. In this step-by-step stepping operation, in the stepping operation, the first ring gear 101 can be supported by the torsion of the main sun gear 31 at different rotation speeds, and the first sun gear 31 can obtain the first ring gear 101 again. The support of the speed, the fusion and complementation of the two speeds produces the effect of stepless speed change.

Embodiment 1 As shown in FIG. 4, the embodiment mainly includes a support frame 11 . The support frame 11 is equipped with a planetary gear train. The gear train includes: an active sun gear 31 and a fixed sun gear 31 fixed connection. The input shaft 21 has three to six output planetary gears 41 meshed around the active sun gear 31. The output planetary gears 41 are mounted on the planetary carrier 51, and the planetary carrier 51 is connected to the output shaft 61 for input in front of the active sun gear 31. A first speed regulating sun gear 71 is further disposed on the shaft 21, and the first speed regulating sun gear 71 is externally engaged with 3 to 6 speed regulating planetary wheels 91. The speed regulating planetary wheel 91 is mounted on the planetary carrier 81, and the planetary carrier 81 is fixed on the input shaft 21, the speed control planetary gear 91, the output planetary gear 41 meshes with the first ring gear 101, and the one-way bearing 111 is mounted on the first ring gear 101, and the one-way bearing is one-way. The clutch 111 is fixed in the support frame, the first speed regulating sun gear 71, the active sun gear 31, the planetary carrier 81, 51 and the output shaft 61, the input shaft 21, the first ring gear 101, and the one-way bearing, that is, the one-way clutch 111 Set for the same axis. ' ·

The working process and principle are as follows: The input shaft 21, the carrier 81, and the active sun gear 31 rotate in a clockwise direction, and the active sun gear 31 drives each of the output planetary gears 41 to rotate counterclockwise while outputting the planetary gear 41 as a whole. The inner ring of one ring gear 101 revolves clockwise, and the overall revolution of the output planet gear 41 drives the planetary carrier 51 and the output shaft 61 to rotate. At this time, the reverse rotation of the first ring gear 101 is locked by the one-way bearing, that is, the one-way clutch 111. The output shaft 61 has a power output. If the first ring gear 101 is not rotated in the clockwise direction, there is no power for speeding up (ie, the first ring gear 101 is not rotating), we can set the output shaft 61 to have the slowest speed and the maximum torque at this time. , that is, as the speed output of a gear. The rotation of the input shaft 21 simultaneously drives the planetary carrier 81 to rotate in the same direction, and then drives the speed-regulating planetary gears 91 to rotate counterclockwise and the speed-adjusting planetary gear 91 as a whole rotates clockwise along the inner ring of the first ring gear 101. The speed planetary gear 91 further drives the first speed control sun gear 71 to rotate at a high speed clockwise direction. When the output shaft 61 needs to overcome a large resistance, the reverse rotation of the first ring gear 101 is locked by the one-way bearing, that is, the one-way clutch 111, so that a temporarily fixed borrowing point can be provided, and the output planet rotating counterclockwise The wheel 41 pushes the planetary carrier 51 and the output shaft 61 to rotate in a clockwise direction at a low speed and a large torque. If the resistance of the output shaft 61 is not required to increase the rotational speed of the output, a braking mechanism can be used to adjust the rotational speed of the first adjustable sun gear 71 according to the demand of the rotational speed of the output shaft 61. The first regulating sun gear 71 The braking speed is transmitted to the first ring gear 101 via the speed regulating planetary gear 91, and the first ring gear 101 drives the output planet 41 again, and the rotation speed is transmitted to the output shaft 61 at a set speed 3⁄4 in the clockwise direction. And accumulating with the original rotational speed of the output shaft 61, the rotational speed of the output shaft 61 is increased. The more the rotational speed of the first speed regulating sun gear 71 is controlled, the more the rotational speed is applied to the output shaft 61. On the contrary, the faster the rotational speed of the first speed regulating sun gear 71, the slower the rotational speed of the output shaft 61. This makes it very effective and can continuously change the output speed and torque to achieve the goal of stepless speed change. Embodiment 2; as shown in FIG. The stepless speed change device mainly comprises a support frame 11 , a planetary gear train is mounted in the support frame 11 , the gear train includes an active sun gear 31 , and the active sun gear 31 is fixedly connected to the input shaft 21 , and is meshed along the periphery of the active sun gear 31 to 3 6 output planetary gears 41, the output planetary gears 41 are mounted on the planetary carrier 51, the planetary carrier 51 is connected to the output shaft 61, and a first speed regulating sun gear 71 is further disposed on the input shaft 21 in front of the active sun gear 31. The first speed regulating sun gear 71 is externally engaged with 3 to 6 speed regulating planetary gears 92. The speed regulating planetary gears 92 are mounted on the planetary carrier 51, and the revolution diameter of the speed regulating planetary gear 92 is larger than the revolution diameter of the planetary gear 41. Each of the output planet gears 41 meshes with the first ring gear 101, and an output sun gear 122 is fixed to the output shaft 61. The output sun gear 122 is externally meshed with 3 to 6 planet gears 131. The planet carrier of the planetary gears 131 is fixed at the In the ring gear 101, the first ring gear 101 is mounted with a one-way bearing, that is, a one-way clutch 111. The one-way bearing, that is, the one-way clutch 111 is fixed in the support frame, and the speed control planetary gear 92 meshes with the planet 131 at the same time. In the circle 141, the first speed regulating sun gear 71, The active sun gear 31, the output sun gear 122, the planetary carrier 51, the output shaft 61, the input shaft 21, the second ring gears 141, 101, and the one-way bearing, that is, the one-way clutch 111, are disposed on the same axis.

The working process and principle are as follows: the input shaft 21, the active sun gear 31, rotates clockwise, the active sun gear 31 drives the output planetary gears 41 to rotate counterclockwise while the output planetary gears 41 are integrally along the inner ring of the first ring gear 101 In the clockwise direction, the overall revolution of the output planet gear 41 drives the planet carrier 51 and the output sun gear 122 and the output shaft 61 to rotate. At this time, the reverse direction of the first ring gear 101 is locked by the one-way bearing, that is, the one-way clutch 111, and the output shaft 61 is 61. There is power output. If the first ring gear 101 is not rotated in the clockwise direction, there is no power for speed increase. At this time, the rotation speed of the output shaft 61 is the slowest and the torque is the largest, and the rotation of the planetary carrier 51 drives the output sun gear 122 to rotate in the same direction. The speed regulating planetary gears 92 rotate in the counterclockwise direction and revolve in the clockwise direction along the inner ring of the second ring gear 141, and the speed regulating planetary gear 92 drives the first speed regulating sun gear 71 to rotate in a high speed clockwise direction, and outputs the sun gear 122. The clockwise rotation causes the planetary wheel 131 to rotate counterclockwise, and the counterclockwise rotation of the planetary gear 131 pushes the second ring gear 141 to also rotate counterclockwise, and the power is transmitted to the first tone through the speed regulating planetary gear 92. On the speed sun gear 71, the turning speed of the first speed regulating sun gear 71 is further accelerated. If the output shaft 61 needs to overcome a large resistance, the first speed regulating sun gear 71 is arbitrarily freely rotated without control, and the reverse rotation of the first ring gear 101 is locked by the one-way bearing, that is, the one-way clutch 111, thus A temporarily stable borrowing point can be provided to the counterclockwise output planetary gear 41 to push the carrier 51 and the output shaft 61 to rotate clockwise at a low speed and a large torque. If the resistance of the output shaft 61 is not large and the output rotation speed needs to be increased, the brake mechanism can be utilized. The rotation speed of the first speed regulating sun gear 71 is controlled according to the requirement of the rotation speed of the output shaft 61. The controlled speed of the first speed regulating sun gear 71 drives the second ring gear 141, the planetary gear 131, and the first tooth through the speed regulating planetary gear 92. The ring 101, and then the output planetary gear 41, applies the rotation speed controlled to the first speed regulating sun gear 71 to the output shaft 61 clockwise according to the set speed ratio (cycle attenuation), and the original output shaft 61 As the speed increases, the output speed increases. The more the rotational speed of the first speed regulating sun gear 71 is controlled, the faster the rotational speed is applied to the output shaft 61. On the contrary, the faster the rotational speed of the first speed regulating sun gear 71, the slower the rotational speed of the output shaft 61, thus It is very effective and can continuously change the output speed and torque to achieve the goal of light level shifting. ·

 Embodiment 3: As shown in FIG. The embodiment includes an input shaft 21, an output shaft 61, an output planetary gear 41, a speed control planetary gear 92, a planetary gear 131, a first ring gear 101, a second ring gear 141, a first speed regulating sun gear 71, and a second tone. The first sun gear 71 and the second sun gear 123 are respectively controlled by a brake mechanism, and the first sun gear 71 is rotatable around the input shaft 21 and input The rotation of the shaft 21 is phase-separated, and the second speed regulating sun gear 123 is rotatable about the output shaft 61 and separated from the rotation of the output shaft 61. The input shaft 21 rotates in synchronism with the active sun gear 31. They may be of a unitary structure or may be fixedly coupled, or may be of a separate structure and intermeshing by internal and external teeth to achieve synchronization of rotation.

 The output planetary gear 41 and the speed control planetary gear 92 have an integrated planetary carrier 51 fixed to the output shaft 61; the carrier of the planetary gear 131 is fixed to the first ring gear 101; the output planetary gear 41 is engaged Between the first ring gear 101 and the active sun gear 31, the speed regulating planetary gear 92 meshes between the second ring gear 141 and the second speed regulating sun gear 123, and the planetary gear 131 meshes with the second ring gear 141 and the first Between the speed regulating sun gears 71; the first ring gear 101 is supported on the one-way clutch 111 which can restrict the direction of rotation thereof, and functions to prevent the first ring gear 101 from rotating in the counterclockwise direction. (The counterclockwise direction mentioned here is in the direction of the power input, that is, the counterclockwise direction from the input shaft to the output shaft, and the clockwise or counterclockwise directions mentioned below are also the same.)

Since the first ring gear 101 is fixed to the wheel carrier of the third planetary gear 5, the wheel frame is locked by the one-way clutch 111 to rotate counterclockwise, so that when the input shaft 21 rotates clockwise at a constant rotation speed, The output planetary gear 41 rotates counterclockwise, and also pushes the planetary carrier 51 of the output planetary gear 41 and the speed regulating planetary gear 92 and the output shaft 61 to rotate clockwise. If it is necessary to increase or decrease the output rotational speed, the first Any one of the speed regulating sun gear 71 or the second speed regulating sun gear 123 is fixed, and the other is adjusted by a brake mechanism, which may be liquid flow stagnation, magnetic braking, rolling braking or friction system. Any of the moving devices. The working principle and process are as follows: When the input sun gear 21 rotates clockwise and stabilizes at a speed, the output planetary gear 41 is rotated counterclockwise (ie, reversed), and the planetary carrier 51 is pushed to revolve clockwise (output The shaft is fixed to the planetary carrier for power output). When the output shaft 61 is loaded, the first ring gear 101 rotates counterclockwise under the driving of the output planetary gear 41. Due to the reverse rotation of the first ring gear 101, the output planetary gear 41 loses contact with the first ring gear 101. At the point of focus, the output planet gear 41 cannot push the planet carrier 51 to rotate clockwise, and the output shaft 61 has no power output. At this time, a one-way clutch 111 is added to the first ring gear 101, and the one-way clutch 111 locks the first ring gear 101 so that it cannot be reversed, so that the output planetary gear 41 has a support for the clockwise rotation of the planetary carrier 51. The output shaft 61 generates a power output, and the output at this time is set to be the slowest and the maximum torque (ie, the first gear). In order to increase the output speed, it is only necessary to add a clockwise and a proportional rotation speed to the first ring gear 101, so that the output speed will be proportionally increased, if it is added to the first ring gear during the speed increase process. The torque of 101 is insufficient to overcome the thrust of the output planetary gear 41 (the first ring gear 101 is reversed), and the locking of the one-way clutch 111 prevents the first ring gear 141 from being reversed, thereby ensuring the output is the slowest and the largest. The rotational speed of the torsion force can increase the output rotational speed when the torque applied to the first ring gear 101 can overcome the thrust of the output planetary gear 41, that is, the first ring gear 101 is rotated. The opposite is deceleration. At the same time, by adjusting the rotational speeds of the first speed regulating sun gear 71 and the second speed regulating sun gear 123, the purpose of adjusting the rotation speed of the planetary carrier 51 can also be assisted.

 The following is a brief description of the working principle of the above-mentioned brake mechanism. The brake mechanism can adopt the gear pump mode, that is, the gear seal is installed in the pump body, and the pump body has an oil inlet passage and a drain passage, and the oil inlet passage is connected. To hydraulic oil, flow control is provided on the side of the drain. When the engine inputs a constant speed through the input shaft, the flow control valve is fully opened at this time, and the active sun gear drives the speed regulating sun gear through the first ring gear and the planetary gears to rotate at a corresponding speed ratio, and the sun is regulated. After the wheel rotates, the hydraulic oil is driven to be sucked into the pump body from the oil inlet (or actively supplied to the pump body) and discharged from the oil drain; if the flow control valve does not work, the hydraulic oil will act as a gear pump. Under the fast cycle. Since the first ring gear is supported on the one-way clutch that can restrict its rotation direction, it cannot rotate and is in a stationary state. At this time, the output shaft has a relatively low rotational speed and the maximum torque.

 If the flow control valve is gradually closed at this time, the discharge resistance of the hydraulic oil will gradually increase. When the discharge resistance of the hydraulic oil is so large that the speed of each speed regulating sun wheel is lowered, since the input shaft speed does not change, the first tooth The ring is rotated by the active sun gear on the input shaft through each of the planetary gear sets.

If the control valve is completely closed, the hydraulic oil can not be completely discharged, and the resistance of the liquid flow will make the speed control sun wheel completely unable to rotate. At this time, the first ring gear reaches the highest speed driven by the speed regulating planetary wheel of the input shaft. The speed, while the output shaft speed is also reached at the same time, the torque is the smallest.

 The brake mechanism utilizes the pressure change of the hydraulic oil to alleviate the impact change of the input shaft speed, thereby realizing the shifting. It utilizes the hydraulic fluid flow stagnation differential and adjusts the internal power ratio with the circulating liquid flow, so that the input shaft power is adjusted and collected on the output shaft. The valve can continuously control the flow of the circulating liquid flow, so continuous use can be used The means for controlling the flow valve opening is adjusted to achieve shifting.

 For the above-mentioned magnetic brake mechanism, it can be realized by using a coiled coil. In the specific implementation, it should be noted that the magnetic force generated by it is opposite to (or locked) to the direction of rotation of each speed regulating sun gear, that is, when When each of the speed control sun wheels rotates clockwise, the energized coil generates a magnetic field force in a counterclockwise direction. In order to realize the control of the speed of the adjustable sun wheel, an iron core is arranged in the coil, and the iron core is moved by the hydraulic mechanism to change the magnetic flux of the coil, thereby changing the magnitude of the magnetic field force, thereby realizing the speed regulating sun. The rotational speed of the wheel changes steplessly between the two states of maximum speed and complete stop.

 For the above rolling brake mechanism, a stator and a rotor rotating relative to the stator may be included, and the stator and the rotor are disposed to be relatively axially movable, and a flange is integrally provided on the stator and the rotor, respectively. The flanges are respectively recessed on the opposite faces in the circumferential direction with arc-shaped ring rails, so that a circumferential raceway is formed between the stator flange and the rotor flange, and a plurality of balls are evenly arranged in the circumferential roll in a rollable manner In the road, a line contact is formed between the ball and the circumferential raceway. The rotor sleeve is placed on a mandrel integrally extended on the stator, and the needle and the mandrel have needle rollers arranged in the axial direction and uniformly arranged in the circumferential direction. The working principle is briefly described as follows. The stator is fixed on the non-rotating component of the device, and the rotor is fixed to the rotating component of the device. When the rotor is not applied with axial force, it is freely rotated by the needle and the ball around the mandrel of the stator. Each ball rotates along the circumferential raceway while revolving. When an axial force directed to the stator is applied to the rotor, or an axial force directed to the rotor is applied to the stator, the friction between the balls and the circumferential raceway is increased, so that the rolling revolution speed is reduced, thereby also reducing Rotor speed; When the axial force increases to a certain set value, the rotor speed drops to zero, thereby achieving the purpose of braking.

Embodiment 4: As shown in FIG. The embodiment includes an input shaft 21, an output shaft 61, an output planetary gear 41, a speed control planetary gear 92, a planetary gear 131, a first ring gear 101, a second ring gear 141, and a first speed regulating sun controlled by a brake mechanism. The wheel 71, the second speed regulating sun gear 123, the active sun gear 31, the first speed regulating sun gear 71 rotate about the input shaft 21, and the rotation thereof is separated from the rotation of the input shaft; the carrier of the planetary wheel 131 and the first ring gear 101 phase fixing; wherein, the output planetary gear 41 and the speed regulating planetary gear 92 have an integrated planetary carrier 51, the wheel carrier 51 is fixed to the output shaft 61; 41 is engaged between the first ring gear 101 and the active sun gear 31, the speed regulating planetary gear 92 is meshed between the second ring gear 141 and the speed regulating sun gear 28, and the planetary gears 131 are meshed with the second ring gear 141 and the second Between the speed regulating sun gears 123; the first ring gear 101 is supported on a one-way clutch 111 that can restrict its direction of rotation.

 The working principle and process are similar to the third embodiment described above. When the input shaft 21 rotates clockwise, the output planetary gear 41 rotates counterclockwise. Since the first ring gear 101 is locked by the one-way clutch 111, it cannot rotate counterclockwise, so The output planetary wheel 41 rotates counterclockwise while driving the planetary carrier 51 and the output shaft 61 for clockwise rotation output, and the speed regulating planetary gear 92 rotates counterclockwise, because the resistance of the second ring gear 141 is greater than that of the first speed regulating sun gear 28 Resistance, so the first speed sun gear 28 is driven to rotate clockwise. If the load needs to be increased, the speed of the first speed regulating sun gear 28 is limited by the braking mechanism. When the resistance of the first speed regulating sun gear 28 is greater than the resistance of the second ring gear 141, the first speed is adjusted. The planet gears 92 transmit power through the second ring gear 141 to the planet gears 131, causing the first ring gear 101 to rotate clockwise and increase the output speed. Conversely, if the rotation speed of the first speed regulating sun gear 28 is completely released or the rotation speed is increased, the output rotation speed can be lowered to achieve the purpose of shifting.

 Embodiment 5: As shown in FIG. The embodiment includes an input shaft 21, an output shaft 61, an output planetary gear 41, a speed control planetary gear 92, a planetary gear 131, a first ring gear 101, a second ring gear 141, and a third ring gear 143, which are controlled by a brake mechanism. The speed regulating sun gear 71, the active sun gear 31, etc., the speed regulating sun gear 71 rotates about the input shaft 21, and the rotation thereof is separated from the rotation of the input shaft 21; the wheel carrier of the planetary gear 131 is fixed to the first ring gear 101; The second ring gear 141 is integrally provided with a sun gear portion 142 with external teeth; the third ring gear 143 is fixed by a fixing device; wherein the output planet gear 41 and the speed regulating planet gear 92 have an integrated planet carrier 51 The planetary carrier 51 is fixedly coupled to the output shaft 61; the output planetary gear 41 is meshed between the first ring gear 101 and the active sun gear 31, and the speed regulating planetary gear 92 is meshed with the second ring gear 141 and the speed regulating sun gear 71. Between the planetary gears 131 is engaged between the third ring gear 143 and the sun gear portion 142 of the second ring gear; the first ring gear 101 is supported on the one-way clutch 111 that can restrict its direction of rotation.

 The working principle and process are similar to the third embodiment described above. When the input shaft 21 rotates clockwise, the output planetary gear 41 rotates counterclockwise. Since the first ring gear 101 is locked by the single clutch 111, it cannot be rotated counterclockwise. Therefore, when the output planetary gear 41 rotates counterclockwise, the planetary carrier 51 and the output shaft 6.1 are also driven to rotate clockwise. At this time, the first ring gear 101, the second ring gear 141, and the planetary gears 131 are all in a stationary state. Then the speed governing planetary gear 92 only drives the speed regulating sun gear

71 clockwise operation, since the output shaft 61 changes its load when it rotates, if the load is reduced When the rotational speed is increased, it is only necessary to limit the rotational speed of the sun gear 71. At this time, the speed regulating planetary gear 92 passes the power through the second ring gear 141, the sun gear portion 142 on the second ring gear 141, and the planetary gear 131. The first ring gear 101 then converges on the output shaft 61, and the rotational speed of the output shaft 61 is increased; otherwise, it is decelerated.

 Also, the brake mechanism described above may be a flow stagnation, a magnetic brake, a rolling brake or a friction brake device. The above-mentioned shifting device has a good sliding inertia, which can reduce energy consumption more effectively.

 The scope of the present invention is not limited to the specific embodiments described above, and any obvious transitions without departing from the structural principle of the present invention are within the scope of the present invention.

Claims

Rights request A gear stepless continuously variable transmission comprising mainly a planetary gear train and a one-way bearing, a one-way clutch (111), characterized in that: the gear train comprises an active sun gear (31) connected to a power input end, 3 to 6 output planets (41) are meshed along the periphery of the active sun gear (31), and the output planetary gears (41) are mounted on the planetary carrier (51), and the planetary carrier (51) is fixedly connected to the power output end. Each of the output planet gears (41) is co-engaged in the first ring gear (101), and the one-way bearing, that is, the one-way clutch (111), is disposed on the first ring gear (101). 2. The gear stepless continuously variable transmission according to claim 1, wherein: an input shaft (21) is fixedly coupled to an axial center of the active sun gear (31), and the planetary carrier (51) is fixedly connected to an output. Axis (61); a first speed regulating sun gear (71) is also arranged on the input shaft (21), and the first speed regulating sun wheel (71) is externally meshed with 3 to 6 speed regulating planet wheels (91), The speed control planetary gear (91) is mounted on the planetary carrier (81), the planetary carrier (81) is fixedly connected with the input shaft (21), and the speed regulating planetary wheels (91) are jointly meshed in the ring gear (101); One-way bearing is one-way clutch (111), ring gear (101), first speed control sun gear (71), active sun gear (31), planetary carrier (81, 51), and output shaft (61), input The shaft (21) is set for the same axis.  3. The gear stepless continuously variable transmission according to claim 1, wherein: an input shaft (21) is fixedly connected to an axial center of the active sun gear (31), and the planetary carrier (51) is fixedly connected to an output. Axis (61); a first speed regulating sun gear (71) is further disposed on the input shaft (21), and the first speed regulating sun gear (71) is externally meshed with 3 to 6 speed regulating planet wheels (92), each of which The speed control planetary gear (92) is mounted on the planetary carrier (51), the revolution diameter of the speed regulating planetary gear (92) is larger than the revolution diameter of the output planetary gear (41), and each output planetary gear (41) and the first ring gear (101) meshing; an output sun gear (122) is fixed on the output shaft (61), and the output sun gear (122) is externally meshed with 3 to 6 planet wheels (131), and the planet carrier of the planetary gear (131) Fixed in the first ring gear (101), the speed regulating planetary gear (92) and the planetary gear (131) are internally engaged in a second ring gear (141); the second ring gear (141), the first ring gear (101) One-way bearing is a one-way clutch (111), a first speed regulating sun gear (71), an active sun gear (31), an output sun gear (122), a planetary carrier (5) 1) The output shaft (61) and the input shaft (21) are set to the same axis. 4. The gear stepless continuously variable transmission according to claim 1, characterized in that: an input shaft (21) is fixedly connected to the axial center of the active sun gear (31), and the planetary carrier (51) is fixedly connected. An output shaft (61); a second speed control sun gear (123) is further disposed on the output shaft (61), the second The speed regulating sun gear (123) is externally engaged with 3 to 6 speed regulating planetary wheels (92), and each speed regulating planetary gear (92) is mounted on the planetary carrier (51), and each output planetary gear (41) and the first The ring gear (101) is meshed; a first speed regulating sun gear (71) is arranged on the input shaft (21), and the first speed regulating sun wheel (71) is externally meshed with 3 to 6 planet wheels (131), a planetary gear The planetary carrier of (131) is fixed on the first ring gear (101), and the speed regulating planetary gear (92) and the planetary gear (131) are internally engaged in a second ring gear (141); the second ring gear ( 141), the first ring gear (101), the one-way bearing is the one-way clutch (111), the first speed regulating sun gear (71), the active sun gear (31), the second speed regulating sun gear (123), the planet The wheel carrier (51), the output shaft (61), and the input shaft (21) are disposed on the same axis.  5. The gear stepless continuously variable transmission according to claim 1, characterized in that: an input shaft (21) is fixedly connected to an axial center of the active sun gear (31), and the planetary carrier (51) is fixedly connected An output shaft (61); a first speed regulating sun gear (71) is further disposed on the input shaft (21), and the first speed regulating sun gear (71) is externally meshed with 3 to 6 speed regulating planet wheels (92), Each speed regulating planetary gear (92) is mounted on the planetary carrier (51), the revolution diameter of the speed regulating planetary gear (92) is larger than the revolution diameter of the planetary gear (41), and each output planetary gear (41) and the first ring gear (101) meshing; a second speed regulating sun gear (122) rotatable relative to the output shaft (61) is mounted coaxially on the output shaft (61), and the second speed regulating sun gear (122) is externally engaged with 3 to 6 The planetary gears of the planetary gears (131) and the planetary gears (131) are fixed in the first ring gear (101), and the speed regulating planetary gears (92) and the planetary gears (131) are internally meshed with a second ring gear ( 141) middle; second ring gear (141), first ring gear (101), one-way bearing, one-way clutch (111), first speed regulating sun gear (71), active sun gear (31), Speed of the sun gear (122), a planet wheel carrier (51) and an output shaft (61), the input shaft (21) is set to the same axis.  6. The gear stepless continuously variable transmission according to claim 5, characterized in that: an input shaft (21) is fixedly connected to the axial center of the active sun gear (31), and the planetary carrier (51) is fixed. Connecting an output shaft (61); providing a first speed control sun gear (71) on the input shaft (21), the first speed control sun gear ' (71) There are 3 to 6 speed-adjusting planetary gears (92) engaged in the outer circumference, the speed-adjusting planetary gears (92) are fixed on the planetary carrier (51), and each output planetary gear (41) and the first ring gear ( 101) Engagement, a planetary carrier is fixed on the first ring gear (101), three to six planetary wheels (131) are arranged on the wheel frame, and a second ring gear is also engaged on the outer circumference of the speed regulating planetary gear (92). (141), the planetary gear (131) is engaged with the outer circumference of the second ring gear (141), and a third ring gear (143) is also engaged on the outer circumference of the planetary gear (131); the first ring gear (101) and the second ring gear (141), the third ring gear (143), the one-way bearing, that is, the one-way clutch (111), the first speed regulating sun gear (71), the active sun gear (31), the planetary carrier (51), and the output shaft ( 61), the input shaft (21) is set for the same axis.