阅读说明：本技术 反向分动百向传动器 (Reverse transfer one hundred directions driver ) 是由 罗灿 于 2018-05-28 设计创作，主要内容包括：本发明反向分动百向传动器,由反向分动器与百向合动器构成,具有特定的连接方式与传动路径,是复合行星排结构,是二自由度决定系统。反向分动器行星排符合本发明所述条件一,百向合动器行星排符合本发明所述条件二。通过调节特性参数使m与k取值确定,动力可以从输入端NA1传动到输出端NX2。控制周转控制端转速NA2的值,可以实现输出端轴向指向与百向合动器轴呈一定夹角的,输出端轴向指向可以围绕百向合动器轴周转且周转可控的百向传动。本发明优先采用使m＝0.5的特性参数对应的行星排作为百向合动器。(The invention relates to a reverse transfer case-hundred-direction driver, which consists of a reverse transfer case and a hundred-direction clutch, has a specific connection mode and a specific transmission path, is a composite planet row structure, and is a two-degree-of-freedom determining system. The reverse transfer case planet row meets the first condition of the invention, and the one-way clutch planet row meets the second condition of the invention. By adjusting the characteristic parameters to determine the values of m and k, power can be transmitted from the input end NA1 to the output end NX 2. The value of the rotating speed NA2 of the turnover control end is controlled, the output end axial direction and the hundred-direction clutch shaft can form a certain included angle, the output end axial direction can be circulated around the hundred-direction clutch shaft, and the turnover is controllable in hundred-direction transmission. The present invention preferentially adopts a planetary row corresponding to a characteristic parameter of which m is 0.5 as a unidirectional clutch.)

1. The reverse transfer case hundred-direction driver is composed of a reverse transfer case and a hundred-direction clutch, has a specific connection mode and a specific transmission path, is a single-row planetary row, and is characterized in that the planetary row meets the condition one: the motion characteristic equation is in the form of NA1 (1+ k) NB1-k NC1, k >1.0 after finishing deformation, the unidirectional clutch is a single-row planetary row, the planetary row shaft of the unidirectional clutch is the shaft of the unidirectional clutch, the planetary row can be a bevel gear single-layer planetary row, a variable linear speed single-layer planetary row or a common cylindrical gear single-layer planetary row, and the motion characteristic equation is characterized in that the planetary row meets the condition two: the motion characteristic equation is in the form of NA2-m NB2- (1-m) NC2 being 0, 1> m >0 after arrangement and deformation, a planet carrier A2 corresponding to NA2 is also j2 as a turnover control end, a component A1 corresponding to NA1 is used as an input end of a reverse transfer gear in a reverse transfer gear planet row, which is also an input end of the reverse transfer gear hundred-drive transmission of the invention, the other two components of the reverse transfer gear are used as transfer ends, a transfer end B1 is connected with a sun gear B2 of the reverse transfer gear centre gear, a transfer end C1 is connected with a sun gear C2 of the reverse transfer gear hundred, a component planet carrier j2 corresponding to NA2 is also an A2 as a turnover control end in the sun gear row of the reverse transfer gear hundred-drive transmission of the invention, one or two of the sun gears are used as output ends, and the output rotating speed is NX2, this is also the output of the reverse transfer hundreds transmission of the present invention.

2. The reverse transfer-hundred-direction transmission of claim 1 is a compound planetary-row structure, is a two-degree-of-freedom determination system, when the rotating speed NA1 of the input end and the rotating speed NA2 of a turnover control end are determined, the rotating speeds of all rotating components in the system are determined, the rotation rotating speed NX2 of the planetary wheel at the output end of the hundred-direction transmission is also determined, the values of k and m are determined by adjusting the gear tooth number ratio of each component in two planetary rows of the reverse transfer gear and the hundred-direction transmission and adjusting the characteristic parameters of the two planetary rows, the power can be transmitted from the input end NA1 to the output end NX2 by adjusting the input end NA1, the required turnover rotating speed and direction of a planetary frame in the hundred-direction transmission can be controlled to surround the axle of the hundred-direction transmission by controlling the rotating speed NA2 of the turnover control end, the output end of the planetary wheel points (the output end points axially) to surround the axle, the output end of the bevel gear single-layer star planet row one-way clutch is axially directed to form a certain included angle with a one-way clutch shaft to rotate around the one-way clutch shaft, the output end of the variable linear speed single-layer star planet row one-way clutch or the output end of the common cylindrical gear single-layer star row one-way clutch is axially directed to be parallel to the one-way clutch shaft (with the included angle of 0 degree) to rotate around the one-way clutch shaft, so that the output end is axially directed to keep a certain included angle with the one-way clutch shaft, the output end is axially directed to rotate around the one-way clutch shaft and the rotation of the one-way clutch shaft can be controlled to rotate in a controllable one-way transmission mode, and the reverse transfer one-way transmission preferentially adopts a planet row corresponding to a characteristic parameter of which m is 0..

Technical Field

The invention relates to a transmission machine with a planet row composite structure, which particularly comprises a reverse transfer case and a one-hundred-direction actuator, wherein the axial direction of an output end forms a certain included angle with the axis of the one-hundred-direction actuator, and the axial direction of the output end can be circulated around the axis of the one-hundred-direction actuator and is controllable in circulation.

Background

The rotating speed transmission with the included angle between the input shaft and the output shaft is called direction-changing transmission, and the rotating speed transmission with the included angle between the output shaft and the input shaft kept unchanged and the 360-degree turnover of the output shaft is called turnover direction-changing transmission. Two types of direction-changing actuators are commonly used: a universal joint driver and a bevel gear direction changing driver. The universal joint driver has the advantages that the included angle of the rotating direction is easy to change, and the defects that the larger the transmission included angle between an output shaft and an input shaft is, the lower the transmission efficiency is, and the maximum transmission included angle is generally less than 50 degrees. The bevel gear direction-changing driver realizes direction-changing transmission by utilizing a bevel gear pair, and the maximum included angle is not limited. Both the two drivers can form large support torque, the support torque is related to the power torque of the transmission, and the larger the power torque is, the larger the support torque is; the support torque is also related to the size of the transmission included angle, the larger the included angle is, the larger the support torque is, and when the included angle is 90 degrees, the support torque is the largest. The two kinds of turning transmission can rotate the output shaft support to turn the output shaft, so that the turning transmission capable of turning is formed. When the output shaft rotates, the torque of the forward rotating support and the torque of the reverse rotating support are completely unbalanced. It is generally necessary to provide a greater epicyclic control torque to manipulate the epicyclic or to provide additional torque to counteract this imbalance by providing additional balancing means such as spring means or electromagnetic force means.

The invention provides a novel turning driver, which can enable the axial direction of an output end (output shaft) to form a certain included angle with a one-way clutch shaft, control the axial direction of the output end to rotate around the one-way clutch shaft, and has controllable rotation and high transmission efficiency. This transmission mode is called a hundred-direction transmission, and a transmission implementing the hundred-direction transmission is called a hundred-direction transmission. When the transmission direction of the hundred-direction driver is changed, the output end axially points to the torque of the forward rotating support and the torque of the reverse rotating support which are circulated around the hundred-direction transmission clutch, and the circulation can be controlled only by small torque.

Disclosure of Invention

The invention relates to a unidirectional driver, wherein the axial direction of an output end forms a certain included angle with a unidirectional actuator shaft, and the axial direction of the output end can be circulated around the unidirectional actuator shaft and the circulation can be controlled. The transfer gear comprises a reverse transfer gear and a one-hundred-direction actuator.

The planet row consists of three parts, namely two central wheels (sun wheels or inner gear rings) and a planet carrier with planet wheels, and the arrangement and meshing structural relationship of the three parts determines various motion equations (including a motion characteristic equation, a space equation and a ring star equation) and determines the type of the planet row. The existing planet row can be divided into a single-layer planet row and a double-layer planet row according to a motion characteristic equation, the three parts of the planet row are a sun gear t, a planet carrier j and an inner gear ring q, and a planet gear on the planet carrier is x. Let Zt be sun gear tooth number, Zq be inner gear ring tooth number, Nt be sun gear rotation speed, Nq be inner gear ring rotation speed, Nj be planet carrier rotation speed, Nx be planet wheel rotation speed, define ordinary cylindrical gear planet row, bevel gear planet row's characteristic parameter a ═ Zq/Zt, taixing parameter b ═ Zt/Zx, circle star parameter c ═ Zq/Zx; characteristic parameters a of the variable linear speed planet row are defined as (Zq Zxt)/(Zt Zxq), a star parameter b is defined as Zt/Zxt, and a circle star parameter c is defined as Zq/Zxq. The variable-speed planetary gear is provided with two sets of gears, one set of gears with the same linear speed as the inner gear ring q has the gear tooth number of Zxq and the rotating speed of Nxq, and the other set of gears with the same linear speed as the sun gear t has the gear tooth number of Zxt and the rotating speed of Nxt. The motion characteristic equation of all single-layer star planet rows is defined as follows: nt + a Nq- (1+ a) Nj is 0, and the motion characteristic equation of all the double-layer star planet rows is defined as: nt-a Nq- (1-a) Nj-0. The Taixing equation of a common cylindrical gear single-layer star planet row and a bevel gear single-layer star planet row is defined as follows: nxt + b Nt- (1+ b) Nj is 0, and the circled star equation is: nxq-c Nq- (1-c) Nj-0. The taixing equation of the variable linear speed double-layer planet row with the structural form six is defined as follows: nxt + b Nt- (1+ b) Nj is 0, and the circled star equation is: nxq + c Nq- (1+ c) Nj is 0. The Taixing equation of the outer planet wheel in the variable linear speed single-layer planet row in the structural form II is defined as follows: Nxt-b-Nt- (1-b) Nj-0, the circled star equation is: nxq + c Nq- (1+ c) Nj is 0. The space equation and the circus equation can be used for calculating the rotating speed of the planet wheel.

The reverse transfer case is in a single-row planet row structure, and the planet row is characterized in that the form of a motion characteristic equation after finishing deformation meets the condition I: the inverse transfer case equation of motion NA1 ═ 1+ k × NB1-k × NC1, k > 1.0. The planet row of the reverse transfer case can be a variable linear speed single-layer planet row, a variable linear speed double-layer planet row, a common cylindrical gear single-layer planet row, a common cylindrical gear double-layer planet row, a bevel gear single-layer planet row or a bevel gear double-layer planet row, and the variable linear speed double-layer planet row or the common cylindrical gear single-layer planet row is usually adopted. For each single-star planet row, the kinematic characteristic equation Nt1+ a × Nq1- (1+ a) × Nj1 ═ 0 can be modified to Nt1 ═ 1+ a) × Nj1-a × Nq1 when a is greater than or equal to 1.0, k ═ a, k > 1.0; when a <1.0, the modification may be Nq1 ═ ((1+ a)/a) × Nj1- (1/a) × Nt1, k ═ 1/a, k > 1.0. The condition one is met. For each double-layer star planet row, the motion characteristic equation Nt1-a Nq1- (1-a) Nj 1-0 can be modified to Nq 1-1/a Nt1- ((1-a)/a) Nj1 when a is less than 0.5, and k-1-a/a, k is greater than 1.0; at 0.5< a <1.0 the distortion can be arranged as Nj1 ═ (1/(1-a)). Nt1- (a/(1-a)). Nq1, k ═ a/(1-a), k > 1.0; at 1.0< a <2.0 the distortion may be arranged as Nj1 ═ (a/(a-1)). Nq1- (1/(a-1)). Nt1, k ═ 1/(a-1), k > 1.0; when a >2.0, the finished deformation may be Nt1 ═ a × Nq1- (a-1) × Nj1, k ═ a-1, k > 1.0. All meet the condition one. The variable linear speed double-layer planet row is favorable for arranging a positive modified gear and improving the transmission efficiency, the variable linear speed double-layer planet row has a structural form which can only be a single-layer planet, and the variable linear speed double-layer planet row is called as a double-layer planet row because the motion characteristic equation of the variable linear speed double-layer planet row follows the motion characteristic equation of the double-layer planet row, namely Nt-a Nq- (1-a) Nj is 0, and the structural form is called as a structural form six of the variable linear speed planet row. The structural schematic diagram of the variable linear speed double-layer planetary row with the structure form six can be seen in fig. 1, and the planetary row composed of the components 1, 2 and 3 in fig. 1 is the structure form six of the variable linear speed double-layer planetary row with only one layer of planet wheels, which is simpler. Referring to fig. 2, a schematic structural diagram of a single-layer star planet row of a common cylindrical gear is shown, and a planet row formed by components 1, 2 and 3 in fig. 2 is the single-layer star planet row of the common cylindrical gear. The three components of the reverse transfer case planetary row are A1, B1 and C1 respectively, and the rotating speeds of the three components are NA1, NB1 and NC1 respectively. The input end of the reverse transfer gear, namely the input end of the whole reverse transfer gear hundred-direction transmission, can input a positive value, a zero value or a negative value, namely the speed input value of NA1 can be determined by taking a component A1 corresponding to the turnover speed NA1 as the input end of the reverse transfer gear. The other two components are used as a transfer end, a transfer end B1 is connected with a central wheel B2 of the hundred-direction clutch, and a transfer end C1 is connected with a central wheel C2 of the hundred-direction clutch.

The unidirectional clutch is in a single-row planetary row structure, the shaft of the planetary row is the shaft of the unidirectional clutch, and the planetary row is characterized in that the form of a motion characteristic equation after finishing deformation meets the second condition: the actuator motion equation NA2 (m × NB2+ (1-m) × NC2, 1> m >0, and the carrier j2 corresponding to NA2 is also a2 as an epicyclic control end. The three parts of the planetary row of the coupling are A2, B2 and C2 respectively, and the rotating speeds of the three parts are NA2, NB2 and NC2 respectively. The planet row can be a bevel gear single-layer planet row, a variable linear speed single-layer planet row and a common cylindrical gear single-layer planet row. For the three single-star planetary rows, the kinematic characteristic equation Nt2+ a × Nq2- (1+ a) × Nj2 ═ 0 can be modified into Nj2 ═ (1/(1+ a)) × Nt2+ (a/(1+ a)) × Nq2, m ═ 1/(1+ a),1> m >0, and the planet carrier j2 corresponding to NA2 is also a2 as the epicyclic control end, which meets the condition two. The part planet carrier j2 corresponding to NA2 is used as an epicyclic control end, the epicyclic control end is also used as an epicyclic control end of the whole reverse transfer transmission, the part can be controlled to rotate forwards, stop or reversely by applying torque to the epicyclic control end, and the rotating speed NA2 value of the epicyclic control end can be determined. Two corresponding parts of NB2 and NC2 are used as two central wheels of the planetary row of the hundred-direction clutch, the central wheel B2 is connected with a transfer end B1 of the reverse transfer case, and the central wheel C2 is connected with a transfer end C1 of the reverse transfer case. One or two planetary wheels can be used as a single-path output end or a double-path output end, which is also the output end of the whole reverse transfer case hundred-direction transmission, and the output rotating speed is the planetary wheel rotation rotating speed NX 2. A group of planet wheels is taken as an output end, called a one-way output end, and is marked by 7 in fig. 2. Two groups of planet wheels which are coaxially and reversely rotated are taken as output ends, are called double-path output ends and are marked by 7 in figure 1. In the two figures, the axial direction of the output end is controlled by the revolving control end 6, and a component planet carrier j2 corresponding to the rotating speed NA2 also has a2 revolving around the shaft of the universal joint, and the planet carrier can have a self-rotating speed NX2 while revolving. The components 4, 5, 6 and 7 in fig. 1 and 2 form a bevel gear single-layer star planetary row adopted by the unidirectional clutch. In fig. 1 and 2, an outer ring gear is provided on the epicyclic control end 6, and the pinion 8 with which the outer ring gear meshes can be supplied with NA2 to the epicyclic control end. The components shown in 4, 5, 6 and 7 in fig. 3 form a variable linear speed single-layer planet row adopted by the unidirectional clutch, a planet carrier j2 is also A2, an outer gear ring is arranged on the planet carrier, and the epicyclic speed NA2 of the planet carrier serving as an epicyclic control end is determined by input of an input paraxial gear 8 meshed with the planet carrier. The purpose of the input of the side gear is to avoid the contradiction of nesting with other parts. The variable linear speed single-layer planet row obeys the motion characteristic equation of the single-layer planet row, but the planet wheels of the variable linear speed single-layer planet row actually have double-layer planet wheels, and the structure is called as a second structure of the variable linear speed planet row. In fig. 3, the outer planet wheel is also a variable speed planet wheel as an output end, the output end is axially directed parallel to the clutch shaft (at an angle of 0 degrees) and rotates around the clutch shaft, and the rotating speed of the output end is the planet carrier rotating speed NA 2. FIG. 4 is a schematic structural diagram of the invention in which a universal cylindrical gear single-star planetary row is adopted in the unidirectional clutch. The components shown in the figures 4, 5, 6 and 7 form a single-layer star planetary row of a common cylindrical gear.

The reverse transfer-hundred-direction transmission comprises a reverse transfer case and a hundred-direction clutch, is a planet row composite structure, is a two-degree-of-freedom determining system, and when the rotating speeds NA1 and NA2 of two rotating members, namely an input end A1 of the reverse transfer case and an epicyclic control end A2 of the hundred-direction clutch, the rotating speeds of all the rotating members in the system are determined, and the self-rotation rotating speed NX2 of a planet wheel at an output end is also determined. The motion equations of the reverse transfer case planet row and the motion equations of the hundred-direction clutch planet row can form an equation set, and the rotation speed of each rotating member in the reverse transfer case hundred-direction transmission can be obtained by solving the equation set under the conditions of the determined values of the rotation speed NA1 and the rotation speed NA2 and the connection conditions.

With a smaller value of the torque adjustment control NA2, the planet carrier of the planetary row of the coupling can be controlled to rotate around the coupling shaft at the desired speed and direction, i.e. the orientation of the planet wheel outputs of the coupling (output axial orientation) can be controlled to rotate around the coupling shaft as desired. The output end of the single-layer planet row one-way clutch adopting the bevel gear axially points to form a certain included angle with the shaft of the one-way clutch to rotate around the shaft of the one-way clutch, and the output end of the single-layer planet row one-way clutch adopting the variable linear speed or the common cylindrical gear axially points to be parallel to the shaft (forming an included angle of 0 degree) of the one-way clutch to rotate around the shaft of the one-way clutch. Therefore, the output end axial direction keeps a certain included angle with the shaft of the unidirectional clutch, and the output end axial direction can be circulated around the shaft of the unidirectional clutch and has controllable unidirectional transmission.

The reverse transfer case adopts a variable linear speed double-layer star planet row, has a simple structure, high transmission efficiency and is more convenient to obtain a larger k value. When the characteristic parameter of the variable linear speed double-layer star planet row is close to 1.0, the k value in the motion equation of the reverse transfer case can be larger. The reverse transfer case with the large k value is a high-efficiency speed reducer with a large transmission ratio while transferring transmission, the transmission ratio from NA1 to NB1 is large, the transmission ratio from NA1 to NC1 is large, and the rotating speed of NA1 is larger than that of NB1 and larger than that of NC 1.

When the gear ratio of each component in the planetary row structure of the unidirectional clutch is adjusted, the characteristic parameter is adjusted to enable m to be 0.5, the epicyclic torque difference is small, and the transmission efficiency of the reverse transfer unidirectional transmission is high. The invention preferably uses a planetary row with characteristic parameters of m equal to 0.5 as a universal joint. In the one-way clutch, m is set to 0.5, and the planet carrier j2 corresponding to NA2 is also a planetary row with a2 as an epicyclic control end, and the planetary rows are bevel gear single-layer planetary rows and variable linear speed single-layer planetary rows. When the characteristic parameter of the single-layer planetary row of the bevel gear and the single-layer planetary row with the variable linear speed is 1.0, the motion characteristic equation can be arranged and deformed into 1 × Nt +1 × Nq- (1+1) × Nj equal to 0, namely NA2-0.5 × NB2- (1-0.5) × NC2 equal to 0, m equal to 0.5, and j2 is A2 which is an epicyclic control end. The motion characteristic equation of the variable linear speed single-layer star planet row obeys the motion characteristic equation of the single-layer star planet row, so the variable linear speed single-layer star planet row is called as a single-layer star planet row, but the variable linear speed single-layer planet row has two layers of planet wheels, is a structural form II of the variable linear speed single-layer planet row, can take the planet carrier as a turnover control end, can take an outer layer planet wheel as an output end, and can turn around a hundred directions clutch shaft in an axial direction of the output end, which is parallel to the hundred directions clutch shaft (which has an included angle of. For the unidirectional clutch, a bevel gear single-layer star planetary row is adopted, when m is 0.5, NB2 is-NC 2, and the number of teeth of two central gears of the unidirectional clutch is equal. At the moment, the axial direction of the output end forms an included angle of 90 degrees with the shaft of the unidirectional clutch, and the output end rotates around the shaft of the unidirectional clutch and is controllable in rotation. When m is not equal to 0.5, m NB2 ═ - (1-m) NC2, the two center gear teeth of the unidirectional clutch are not equal. At the moment, the axial direction of the output end forms an actually required included angle of not 90 degrees with the shaft of the unidirectional clutch, and the output end rotates around the shaft of the unidirectional clutch and can rotate and control.

The cylindrical gear can be straight gear, helical gear, herringbone gear and the like, and the bevel gear can be straight gear, curved gear and the like. The gears may be of various tooth forms.

The invention can be used for the transmission of the tiltable rotor of an aircraft, the output end of a helicopter axially points to a steerable tail rotor, the output end of a steamship axially points to a steerable propeller, and the like. The multi-rotor type axial-flow propeller can be used as a hundred-direction driver of a single rotor, a coaxial reverse rotation double rotor, a single propeller and a coaxial reverse rotation double propeller. Can be used for the transmission of machine tools and robots.

The present invention may be used in combination with other machines. Referring to fig. 5, two sets of reverse transfer hundred-direction transmissions are taken, wherein a hundred-direction actuator m is 0.5, and are arranged behind a differential and transmission device 9 in parallel, the two sets of reverse transfer hundred-direction transmissions respectively obtain two input rotating speeds from the differential and transmission device 9, the two output ends 7 can be connected with a left steerable driving wheel and a right steerable driving wheel to output two output rotating speeds to the left steerable driving wheel and the right steerable driving wheel, and the two epicyclic control ends 6 are connected with a rack and pinion through a side shaft gear 8 and are controlled by a steering device, so that the steerable driving wheel transmission device of the motor vehicle can be formed. The epicyclic torque difference of the control revolution of the left steerable driving wheel and the right steerable driving wheel can be compensated in the steering device. The device can replace a universal transmission steering device to be used for the transmission of a steerable driving wheel of a motor vehicle, the transmission efficiency is higher, the steerable angle range is larger, and the influence of steering control on the transmission of the driving wheel is small.

The reverse transfer-hundred-direction transmission has the advantage that a planet row composite structure of a two-degree-of-freedom determination system consisting of a reverse transfer case and a hundred-direction clutch is provided as the structure of the invention. The reverse transfer case is characterized in that the planet row of the reverse transfer case meets the first condition of the invention, and the one-way clutch is characterized in that the planet row of the reverse transfer case meets the second condition. A connection mode between the reverse transfer case and the hundred-direction clutch is provided. The method is characterized in that in the transmission process of power transmitted from an input end rotating speed NA1 to an output end autorotation rotating speed NX2, the output end is controlled to axially point to rotate by controlling the rotating speed NA2 of the rotating control end, the output end axially points to form a certain included angle with the shaft of the unidirectional clutch, and the output end axially points to the unidirectional transmission which can rotate around the shaft of the unidirectional clutch and can be controlled in rotating.

The invention provides that as long as a structure consisting of a reverse transfer case and a hundred-direction actuator is adopted in a transmission machine, the characteristics of the reverse transfer case and the hundred-direction actuator accord with the characteristics of the invention, in the transmission process of power from an input end rotating speed NA1 to an output end autorotation rotating speed NX2, the output end is controlled to axially point to the turnover by controlling the turnover rotating speed NA2 of a turnover control end, the axial pointing of the output end and the axle of the hundred-direction actuator form a certain included angle, and the axial pointing of the output end can be turned around the axle of the hundred-direction actuator and is a transmission with controllable turnover, which all belong to the protection range of the invention.

Drawings

Fig. 1 is a schematic diagram of a reverse transfer hundreds-directional transmission of the invention, and is a schematic diagram of an embodiment 1 of the invention. The input end 1, one of the split ends 2, the other of the split ends 3, one of the central wheels 4, the other of the central wheels 5 and the turnover control end 6 are provided with an external gear ring, and the double-path output end 7 and a paraxial gear 8 meshed with the external gear ring can input NA2 to the turnover control end. Wherein the reverse transfer case composed of the components 1, 2 and 3 adopts a variable linear speed double-layer star planet row. The central wheels 4 and 5 of the single-layer star planet row of the bevel gear of the unidirectional clutch have the same tooth number, two rotating speeds output by the two-way output end are coaxial, and the rotating directions of the rotating speeds are opposite when the rotating speeds have the same absolute value.

Fig. 2 is another schematic view of the reverse transfer hundreds transmission of the invention. The input end 1, one of the split ends 2, the other of the split ends 3, one of the central wheels 4, the other of the central wheels 5 and the turnover control end 6 are provided with an external gear ring, the one-way output end 7, and a paraxial gear 8 meshed with the external gear ring can input NA2 to the turnover control end. The reverse transfer case composed of the components shown in 1, 2 and 3 adopts a common cylindrical gear single-layer star planet row, and the one-hundred-direction combination case composed of the components shown in 4, 5, 6 and 7 adopts a bevel gear single-layer star planet row.

Fig. 3 is a schematic view of another reverse transfer hundreds transmission of the invention. The input end 1, one of the split ends 2, the other of the split ends 3, one of the central wheels 4, the other of the central wheels 5 and the turnover control end 6 are provided with an external gear ring, the one-way output end 7, and a paraxial gear 8 meshed with the external gear ring can input NA2 to the turnover control end. The reverse transfer case composed of the components shown in 1, 2 and 3 adopts a common cylindrical gear single-layer star planet row, and the one-way clutch composed of the components shown in 4, 5, 6 and 7 adopts a variable linear speed single-layer star planet row.

Fig. 4 is a further schematic view of the reverse transfer hundred-way transmission of the present invention. The device comprises an input end 1, a shunt end 2, another shunt end 3, a central wheel 4, another central wheel 5, a turnover control end 6 and a one-way output end 7. The reverse transfer case composed of the components 1, 2 and 3 adopts a variable linear speed double-layer star planet row, and the unidirectional clutch composed of the components 4, 5, 6 and 7 adopts a common cylindrical gear single-layer star planet row.

Fig. 5 is a schematic diagram of a motor vehicle steerable drive wheel transmission device formed by two sets of reverse transfer hundred-direction transmissions. The input end 1, one of the split ends 2, the other of the split ends 3, one of the central wheels 4, the other of the central wheels 5 and the turnover control end 6 are provided with an outer gear ring, the one-way output end 7 is connected with a driving wheel, a side shaft gear 8 meshed with the outer gear ring is connected with a gear rack to be controlled by a steering device, and NA2, a differential and a transmission device 9 can be input to the turnover control end. Wherein the reverse transfer case composed of the components 1, 2 and 3 adopts a variable linear speed double-layer star planet row. The central wheels 4 and 5 of the single-layer star planet row of the bevel gear of the unidirectional clutch have the same tooth number.

The hundreds clutch in fig. 1 is schematically illustrated in a full planetary row configuration, and the planetary rows in the remaining figures are schematically illustrated in a half planetary row configuration as is conventional in the industry. The components in the figures are only schematic in structural relationship and do not reflect actual dimensions.

Detailed Description