CN110541918A - Reverse transfer double-control one-hundred-direction driver - Google Patents

Abstract

The invention relates to a reverse transfer double-control one-hundred-direction driver, which consists of a reverse transfer case, a same-direction clutch and a one-hundred-direction clutch, has a specific connection mode and a specific transmission path, is a planet row composite structure, and is a two-degree-of-freedom decision system. The reverse transfer case planet row meets the first condition of the invention, the equidirectional clutch meets the second condition of the invention, and the hundred-direction clutch planet row meets the third condition of the invention. The rear end between the equidirectional actuator and the hundreds-directional actuator is connected with two connection modes. The invention has five application modes corresponding to two connection modes, and can realize that the axial direction of the output end forms a certain included angle with the shaft of the unidirectional clutch, and the axial direction of the output end can be circulated around the shaft of the unidirectional clutch and has controllable unidirectional transmission.

Description

Reverse transfer double-control one-hundred-direction driver

Technical Field

The invention relates to a transmission machine with a planet row composite structure, which particularly comprises a reverse transfer case, a syntropy clutch and a hundred-direction clutch, wherein a specific connection mode is formed between the syntropy clutch and the hundred-direction clutch, the axial direction of an output end forms a certain included angle with the axis of the hundred-direction clutch, and the axial direction of the output end can be circulated around the axis of the hundred-direction clutch and is a hundred-direction transmission device with controllable 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 an output end to axially point to form a certain included angle with a hundred-direction clutch shaft and control the output end to axially point to circulate around the hundred-direction clutch shaft and the circulation is controllable. When the transmission direction of the unidirectional 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 unidirectional clutch, so that the torque is balanced, the circulation can be controlled only by small circulation control torque, and the transmission efficiency is high. And the turnover remote control can be carried out.

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 device specifically comprises a reverse transfer case, a homodromous actuator and a hundred-direction actuator, wherein a specific connection mode is arranged between the homodromous actuator and the 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 defining a single-layer planet row of bevel gears is 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 for a variable line speed double star of structural form six is defined as Nxt + b Nt- (1+ b) Nj ═ 0: the circled star equation is: nxq + c Nq- (1+ c) Nj is 0. The space equation of the variable linear speed single-layer star planet row with the structural form two is defined as 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 a single-row planet row, 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 commonly used. 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 sixth structural form can be seen in fig. 1 and 2, and the planetary row composed of the components 1, 2 and 3 in fig. 1 and 2 is the structural form six of the variable linear speed double-layer planetary row with only one layer of planet wheels, which is simpler. The structural schematic diagram of a common cylindrical gear single-layer star planet row is shown in figure 6, and the structural schematic diagram of a bevel gear single-layer star planet row is shown in figure 7. 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 component A1 corresponding to the rotating speed NA1 is used as the input end of the reverse transfer case, and the reverse transfer case is also used as the input end of the whole reverse transfer double-control hundred-direction transmission. The other two components are used as the transfer ends, the transfer end B1 is connected with the input end B2 of the equidirectional clutch, and the transfer end C1 is connected with the input end C2 of the equidirectional clutch.

The syntropy clutch is a single-row planet row, and the planet row is characterized in that the form of a motion characteristic equation after finishing deformation meets the second condition: the motion equation NA2 of the homodromous clutch is 0.5 × NB2+0.5 × NC2, a central wheel A2 corresponding to the NA2 serves as a central input end, B2 and C2 are two input ends and two output ends of the homodromous clutch, serve as input ends and are connected with a transfer end of the reverse transfer case, and serve as output ends and are connected with a central wheel of the hundred-way transfer case. The three components of the planetary row of the homodromous clutch are A2, B2 and C2 respectively, and the rotating speeds of the three components are NA2, NB2 and NC2 respectively. The planet row can be a variable linear speed double-layer planet row and a common cylindrical gear double-layer planet row. The motion characteristic equation Nt2-a × Nq2- (1-a) × Nj2 ═ 0 can be arranged and deformed into Nt2 ═ 0.5 × Nq2+0.5 × Nj2 when a is 0.5, and t2 corresponding to Nt2 is used as a central input end, and B2 and C2 are two input ends of a homodromous clutch and also two output ends, which meets the condition two; when a is 2.0, the modification can be arranged to be Nq2 is 0.5 × Nt2+0.5 × Nj2, q2 corresponding to Nq2 is used as a central input end, and two input ends of B2 and C2 homodromous combiners are also two output ends, which meets the condition two. The two input ends B2 and C2 are two output ends at the same time, are connected with two central wheels of the hundred-direction clutch, and can output two rotating speeds which are coaxially and synchronously rotated in the same rotating direction or coaxially and reversely rotated in the opposite rotating direction, namely NB2 and NC 2. The components shown in 4, 5 and 6 in fig. 1 form a variable linear speed double-layer planetary row used by the homodromous clutch, an outer gear ring is arranged outside a central input end 6, a paraxial gear 7 is meshed with the outer gear ring, and the rotational speed NA2 can be input to the central input end. Referring to fig. 8, a central input end 1 is provided with an outer gear ring on the outer side, 2 and 3 are two input end output ends of a homodromous clutch, and 4 is a paraxial gear meshed with the outer gear ring and can input rotating speed NA2 to the central input end.

The one-way clutch is a single-row planet row, the axis of the planet row is the axis of the one-way clutch, and the planet row is characterized in that the form of the motion characteristic equation after finishing deformation meets the condition three: the variator motion equation NA3 is 0.5 × NB3+0.5 × NC3, and the carrier j3 corresponding to NA3 is also A3 as an epicyclic control end. The three parts of the planetary row of the coupling are A3, B3 and C3 respectively, and the rotating speeds of the three parts are NA3, NB3 and NC3 respectively. The planet row can be a bevel gear single-layer planet row or a variable linear speed single-layer planet row. For the two single-layer star planet rows, the kinematic characteristic equation Nt3+ a × Nq3- (1+ a) × Nj3 ═ 0 can be modified into Nj3 ═ 0.5 × Nt3+0.5 × Nq3 when a is 1.0, and the planet carrier j3 corresponding to NA3 is also A3 as the epicyclic control end, which meets the condition three. Two corresponding parts of NB3 and NC3 are used as two central wheels of the planetary row of the unidirectional clutch. The center wheel B3 is connected to the output B2 of the co-rotating clutch and the center wheel C3 is connected to the output C2 of the co-rotating clutch, both connections being referred to as back-end connections with a particular connection pattern. One, two or more groups of planet wheels can be arranged in the planet row of the hundred-direction clutch, one or two planet wheels are used as a single-path output end or a double-path output end, the output end is also the output end of the whole reverse transfer double-control hundred-direction clutch, and the output rotating speed is the planet wheel rotation rotating speed NX 3. One planet wheel is taken as an output end, called a one-way output end, and is marked by 11 in fig. 1. Two planetary wheels which coaxially rotate reversely are taken as output ends and are called double-path output ends. The output end can rotate around the shaft of the universal joint actuator along with the planet carrier j3 and A3, and the rotation speed NX3 can exist at the same time. The components shown in 8, 9, 10 and 11 in the figure 1 form the unidirectional clutch adopting a bevel gear single-layer star planetary row. The unidirectional clutch composed of components shown in 8, 9, 10 and 11 in fig. 3 adopts a variable linear speed single-layer planet row, a planet carrier j3 and an A3 are used as an epicyclic control end 10, an external gear ring is arranged on the planet carrier, and if necessary, an epicyclic rotating speed NA3 can be input to the planet carrier through a paraxial gear 12 meshed with the external gear ring. 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, which is the structural form II of the variable linear speed planet row, wherein the outer planet wheels are selected as output ends in fig. 3, the output ends axially point to be parallel to the axis of the unidirectional clutch (form an included angle of 0 degrees) and rotate around the axis of the unidirectional clutch, and the rotating speed of the output ends is planet carrier rotating speed NA 3.

The connection between the output end of the equidirectional clutch and the central wheel of the hundred-directional clutch is called rear-end connection, and the rear end is connected with two specific connection modes. In the first connection mode, the transmission ratios of the two rear-end connections are both n or-n, that is, the two original rotation speeds in the same direction are connected and transmitted and then keep in the same direction, and the two original rotation speeds in the opposite direction are connected and transmitted and then keep in the opposite direction. Such as the two back-end connections in fig. 1. The simplest connection form of the first connection mode is two direct connections, i.e. the transmission ratio of the two connections is 1.0. In the second connection mode, one of the transmission ratios of the two rear-end connections is n, and the other transmission ratio is-n, namely, the two rotation speeds which are originally in the same direction are converted into the opposite directions after being connected and transmitted, and the two rotation speeds which are originally in the opposite directions are converted into the same direction after being connected and transmitted. Such as the two back-end connections in fig. 2. The connection structure shown in fig. 4 and 5 can achieve the connection transmission effect of the connection mode two. The simpler connection form of the second connection mode is that a direct connection is adopted in one connection, the transmission ratio is 1.0, an indirect connection is formed in the other connection, and the transmission ratio of the indirect connection is-1.0. Such as the back end connection in fig. 9. In the figure 9, one of the homodromous clutch and the other of the homodromous clutch is directly connected, and the other of the homodromous clutch is indirectly connected in a bevel gear form, the transmission ratio of the indirect connection is-1.0, and a component 12 in the figure is a bevel gear fixed by a bearing in a single-way commutator in a bevel gear form.

The invention relates to a reverse transfer double-control one-hundred-direction driver which consists of a reverse transfer case, a same-direction clutch and a one-hundred-direction clutch, is a planet row composite structure and is a two-degree-of-freedom decision system. The rotational speeds of any two rotating members in the system are determined and the rotational speeds of all the rotating members in the system are determined. The motion equations of the reverse transfer case, the motion equations of the homodromous clutch and the motion equations of the one-hundred-direction clutch can form an equation set, and the rotation speed of each rotating member in the reverse transfer case double-control one-hundred-direction transmission can be obtained by solving the equation set under the conditions of the determined values of any two rotation speeds and the transmission ratio of each connection and rear end connection. Therefore, the reverse transfer double-control one-hundred-direction driver has four application modes. The reverse transfer double-control one-hundred-direction transmission has an application mode corresponding to the connection mode, namely, when the rotating speed NA1 of the input end A1 of the reverse transfer case and the rotating speed NA2 of the center input end A2 of the homodromous transmission are determined, the rotating speeds of all rotating components in the system are determined. The output planetary rotation speed NX3 is determined, and the epicyclic rotation speed NA3 of the sun gear carrier, i.e. the axially directed epicyclic rotation speed NA3 of the output is determined. The input end A1 inputs a rotating speed NA1 which can be transmitted to the output end to form an output rotating speed NX3, the output end is axially directed and can rotate around the shaft of the unidirectional clutch, so that the rotating control end is kept free, the rotating speed NA3 axially directed at the output end can be adjusted by adjusting the rotating speed NA2 of the central input end with small torque, the rotation can be controlled, and NA2 is in direct proportion to NA 3. In the application mode, a turnover control end can be omitted, and the structure is simpler. If the rear end is far away from the connection, the control of the axial direction turnover of the output end is realized by adjusting the rotating speed of the input end of the center, namely the remote control. Corresponding to the first connection mode and the second application mode, when the rotating speed NA1 of the input end A1 of the reverse transfer case and the rotating speed NA3 of the epicyclic control end A3 of the hundred direction coupling are determined, the rotating speeds of all rotating components in the system are determined. The input end A1 inputs a rotating speed NA1 which can be transmitted to the output end to form an output rotating speed NX3, the axial direction of the output end can be rotated around the shaft of the unidirectional clutch, so that the central input end is kept free, the axial direction of the output end can be adjusted by adjusting the rotating speed NA3 of the rotating control end with small torque, and the rotation can be controlled. In this application mode, the reverse transfer double-control one-hundred-direction driver is equivalent to a reverse transfer one-hundred-direction driver, and the same-direction clutch does not actually work. The same-direction clutch can be cancelled, and the reverse transfer double-control one-hundred-direction driver is converted into a reverse transfer one-hundred-direction driver.

The reverse transfer double-control one-hundred-direction transmission has a third application mode corresponding to the second connection mode, and when the rotating speed NA1 of the input end A1 of the reverse transfer case and the rotating speed NA2 of the central input end A2 of the homodromous clutch are determined, the rotating speeds of all rotating components in the system are determined. The rotating speed NA2 is input at the central input end A2 and can be transmitted to the output end to form the output rotating speed NX3, the output end is axially directed and can rotate around the shaft of the unidirectional clutch, so that the rotating control end is kept free, the rotating speed NA1 of the input end can be adjusted by small torque, the rotating speed NA3 axially directed at the output end can be adjusted, the rotation can be controlled, and NA1 is in direct proportion to NA 3. In the application mode, a turnover control end can be omitted when necessary, and the structure is simpler. If the rear end is far away from the connection distance, the control of the axial direction turnover of the output end is realized by adjusting the rotating speed of the input end, namely the remote control. Corresponding to the second connection mode and the fourth application mode, when the rotating speed NA2 of the homodromous clutch center input end A2 and the rotating speed NA3 of the hundreds clutch turnover control end A3 are determined, the rotating speeds of all rotating components in the system are also determined. The rotating speed NA2 is input at the central input end A2 and can be transmitted to the output end to form the output rotating speed NX3, the axial direction of the output end can be rotated around the shaft of the unidirectional clutch, so that the input end is kept free, the rotating control torque for controlling the forward rotation and the reverse rotation of the rotating control end has no torque difference, the axial direction of the output end can be adjusted by adjusting the rotating speed NA3 of the rotating control end with small torque, and the rotation can be controlled. In the application mode, the reverse transfer double-control one-hundred-direction driver is equivalent to a same-direction transfer one-hundred-direction driver, and the reverse transfer case does not work actually. The reverse transfer case can be cancelled, and the reverse transfer case double-control one-hundred-direction transmission is converted into a same-direction transfer case one-hundred-direction transmission.

The four application modes can realize that the axial direction of the output end forms a certain included angle with the shaft of the unidirectional clutch, and the axial direction of the output end can be circulated around the shaft of the unidirectional clutch and has controllable unidirectional transmission.

In the third application mode of the connection mode II, a single-way speed changer can be additionally arranged, so that one direct connection between the reverse transfer case and the same-direction clutch is converted into an indirect connection. Similar to the third application mode, a reverse transfer double-control hundred-direction transmission provided with a one-way speed changer is added, and the reference is made to fig. 10. Fig. 10 shows a one-way transmission 13 provided between the reverse transfer case and the same-direction clutch. The central purpose is that NB 2-NC 2 (1+ k) -NB 1-k-NC 1 can be changed by this single transmission. Therefore, the rotating speed NA2 is input at the central input end A2 and can be transmitted to the output end to form the output rotating speed NX3, the output end is axially directed and can rotate around the shaft of the unidirectional clutch, so that the rotating control end is kept free (the rotating control end can be cancelled if necessary), the rotating control torque for adjusting the rotating speed of the input end in the forward rotation and the reverse rotation is free from torque difference, the rotating speed NA3 axially directed at the output end can be adjusted by adjusting the rotating speed NA1 of the input end with small torque, the rotation can be controlled, and NA1 is in direct proportion to NA 3. The third application mode in which the single-way speed changer is additionally arranged can be called as third application mode. The single-speed gearbox, see fig. 10 at 13, is used in one of the two connections between the power take-off of the reversing gear and the input of the co-rotating clutch, for an indirect connection outside the same shaft of the two connections, and when a transmission ratio of (1+ k)/k is provided for the indirect connection of C1 and C2, (1+ k) NB1-k NC1 can be used when NB2 is-NC 2. When a transmission ratio value k/(1+ k) is provided for the indirect connection of B1 to B2, (1+ k) NB1-k NC1 in NB 2-NC 2 is also possible. The single-way speed changer is generally in a parallel-axis single-shaft cylindrical gear form or a variable linear speed double-layer star planet row form.

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.

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 axial pointing of the direction-variable output end of a helicopter to a tail rotor, the axial pointing of the direction-variable output end of a steamship to a 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.

The reverse transfer double-control one-hundred-direction driver has the advantages that a planet row composite structure of a two-degree-of-freedom determination system consisting of a reverse transfer case, a same-direction clutch and a one-hundred-direction clutch is provided as the structure of the reverse transfer case double-control one-hundred-direction driver. The reverse transfer case is characterized in that a planet row of the reverse transfer case meets the first condition of the invention, the homokinetic clutch is characterized in that a planet row of the homokinetic clutch meets the second composite condition, and the unidirectional clutch is characterized in that a planet row of the homokinetic clutch meets the third condition. The connection mode between the reverse transfer case and the same-direction clutch is provided, and a specific connection mode between the same-direction transfer case and the hundred-direction clutch is provided. The four application modes and the three application modes are provided to realize that the axial direction of the output end keeps a certain included angle with the shaft of the unidirectional clutch, and the axial direction of the output end can be circulated around the shaft of the unidirectional clutch and has controllable unidirectional transmission.

The invention provides that only a structure consisting of a reverse transfer case, a same-direction clutch and a hundred-direction clutch is adopted in the transmission machinery. The characteristics of the reverse transfer case, the same-direction clutch and the one-hundred-direction clutch are in accordance with the invention, and the connection mode between the reverse transfer case and the same-direction clutch and the connection mode between the same-direction clutch and the one-hundred-direction clutch are in accordance with the invention. The output end axial direction and the hundred direction clutch shaft are kept at a certain included angle through one of four application modes and three application modes, and the output end axial direction can be circulated around the hundred direction clutch shaft and has controllable hundred direction transmission. Such a drive is intended to fall within the scope of the present invention.

Drawings

Fig. 1 is a schematic diagram of a reverse transfer double-control hundred-direction transmission according to the invention, and is a schematic diagram of embodiment 1 of the invention. The input end 1, one transfer end 2, the other transfer end 3, one input end output end 4 of the homodromous clutch, the other input end output end 5 of the homodromous clutch, the central input end 6 is provided with an outer gear ring, a paraxial gear 7 meshed with the outer gear ring of the central input end can input rotating speed NA2 to the central input end, one central wheel 8 of the unidirectional clutch, the other central wheel 9 of the unidirectional clutch, an epicyclic control end 10 and a planet wheel output end 11. Wherein the reverse transfer case composed of the components 1, 2 and 3 adopts a variable linear speed double-layer star planet row. 4. 5 and 6 adopts a variable linear speed double-layer star planet row. The central wheels 8 and 9 of the single-layer star planet row of the bevel gear of the unidirectional clutch have the same tooth number, and 11 is a single-path output end.

Fig. 2 is another schematic diagram of the reverse transfer double-control hundred-direction driver of the invention. The input end 1, one transfer end 2, the other transfer end 3, one input end output end 4 of the homodromous clutch, the other input end output end 5 of the homodromous clutch, the central input end 6 is provided with an outer gear ring, a paraxial gear 7 meshed with the outer gear ring of the central input end can input rotating speed NA2 to the central input end, one central wheel 8 of the unidirectional clutch, the other central wheel 9 of the unidirectional clutch, an epicyclic control end 10 and a planet wheel output end 11. Wherein the reverse transfer case composed of the components 1, 2 and 3 adopts a variable linear speed double-layer star planet row. 4. 5 and 6 adopts a variable linear speed double-layer star planet row. The central wheels 8 and 9 of the single-layer star planet row of the bevel gear of the unidirectional clutch have the same tooth number, and 11 is a single-path output end. The two input ends and the output ends of the two input ends and the two central wheels of the two input ends and the two output ends of the two input ends and the two central wheels of the two input ends.

FIG. 3 is another schematic diagram of the reverse transfer double control hundred-direction driver of the invention. The input end 1, one transfer end 2, the other transfer end 3, one input end output end 4 of the homodromous clutch, the other input end output end 5 of the homodromous clutch, the central input end 6 is provided with an outer gear ring, a paraxial gear 7 meshed with the outer gear ring of the central input end can input rotating speed NA2 to the central input end, one central wheel 8 of the unidirectional clutch, the other central wheel 9 of the unidirectional clutch, an epicyclic control end 10 and a planet wheel output end 11. Wherein the reverse transfer case composed of the components 1, 2 and 3 adopts a variable linear speed double-layer star planet row. 4. 5 and 6 adopts a variable linear speed double-layer star planet row. The unidirectional clutch adopts a variable linear speed single-layer planet row, the planet carrier 10 is provided with an outer gear ring, and the paraxial gear 12 meshed with the planet carrier outer gear ring can input the rotating speed NA3 to the planet carrier, and 11 is a single-way output end.

Fig. 4 is a schematic diagram of the rear end connection mode two of the reverse transfer double-control hundred-direction driver of the invention. Two input rotating speeds which are coaxial and rotate at the same time can be converted into two rotating speeds which are coaxial and rotate at opposite directions to be output after being transmitted by the reversing double-driver.

FIG. 5 is another schematic diagram of the rear end connection mode II of the reverse transfer double-control hundred-direction driver of the invention. The two coaxial and same-rotation input rotating speeds can be converted into two coaxial and reverse rotating speed outputs after being transmitted by the reversing double-driver.

Fig. 6 is a schematic diagram of a common cylindrical gear single-layer star planetary row adopted by the reverse transfer case of the reverse transfer case double-control one-hundred-direction transmission. Input 1, one tap 2, and the other tap 3.

Fig. 7 is a schematic diagram of a bevel gear single-layer star planetary row adopted by the reverse transfer case of the reverse transfer case double-control one-hundred-direction transmission. Input 1, one tap 2, and the other tap 3.

Fig. 8 is a schematic diagram of a common cylindrical gear double-layer star planetary row adopted by a homodromous clutch of the reverse transfer double-control one-hundred-direction driver. The outer side of the central input end 1 is provided with an outer gear ring, one input end output end 2, the other input end output end 3, and the paraxial gear 4 is meshed with the outer gear ring, so that the rotating speed NA2 can be input to the central input end.

Fig. 9 is a schematic diagram of the reverse transfer double-control hundred-direction transmission of the invention with the rear end connected in the connection mode two. The input end 1, one transfer end 2, the other transfer end 3, one input end output end 4 of the homodromous clutch, the other input end output end 5 of the homodromous clutch, the central input end 6 is provided with an outer gear ring, a paraxial gear 7 meshed with the outer gear ring of the central input end can input rotating speed NA2 to the central input end, one central wheel 8 of the unidirectional clutch, the other central wheel 9 of the unidirectional clutch, a turnover control end 10, a planet wheel output end 11 and a bevel gear 12 fixed by a bearing. Wherein the reverse transfer case composed of the components 1, 2 and 3 adopts a variable linear speed double-layer star planet row. 4. 5 and 6 adopts a variable linear speed double-layer star planet row. The central wheels 8 and 9 of the single-layer star planet row of the bevel gear of the unidirectional clutch have the same tooth number, and 11 is a single-path output end. The bevel gear 12 drive with the rear end connected with the middle bearing fixed can make the transmission ratio of the indirect connection be-1.0.

Fig. 10 is a third schematic diagram of an application mode of the reverse transfer double-control hundred-direction transmission of the invention, in which a single-way transmission is additionally arranged and the rear end of the transmission is connected into a connection mode II. The input end 1, one of the driving ends 2, the other of the driving ends 3, one of the input ends and the output ends 4 of the homodromous clutch, the other of the input ends and the output ends 5 of the homodromous clutch, the central input end 6 is provided with an outer gear ring, a paraxial gear 7 meshed with the outer gear ring of the central input end can input rotating speed NA2 to the central input end, one central wheel 8 of the unidirectional clutch, the other central wheel 9 of the unidirectional clutch, a turnover control end 10, a planet wheel output end 11, a bevel gear 12 fixed by a bearing and a one-way speed changer 13. Wherein the reverse transfer case composed of the components 1, 2 and 3 adopts a variable linear speed double-layer star planet row. 4. 5 and 6 adopts a variable linear speed double-layer star planet row. The central wheels 8 and 9 of the single-layer star planet row of the bevel gear of the unidirectional clutch have the same tooth number, and 11 is a single-path output end. The bevel gear 12 drive with the rear end connected with the middle bearing fixed can make the transmission ratio of the indirect connection be-1.0. An indirect connection involving a single transmission 13 may be such that k NC1 is (1+ k) NC 2.

The reversing double drive of fig. 1, 4 and 5 is shown in full-width configuration, and the planetary rows of the remaining figures are shown in semi-width planetary row configuration schematics 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

Example 1: the reverse transfer double-control one-hundred-direction driver disclosed by the invention comprises an embodiment 1 of a reverse transfer case, a same-direction clutch and a one-hundred-direction clutch, and is shown in a figure 1. The reverse transfer case adopts a variable-linear-speed double-layer star planet row, and the motion characteristic equation can be arranged and transformed into a reverse transfer case motion equation NA 1-10-NB 1-9-NC 1. Namely, the number of teeth of the sun gear B1 at the transfer end of the variable-line-speed planetary gear row is 20, the number of teeth of the gear at one side of two sets of gears of the variable-line-speed planetary gear, which is the same as the linear speed of the two sets of gears, is 20, the number of teeth of the gear C1 at the other transfer end is 18, the number of teeth of the gear at the other side of the two sets of gears of the variable-line-speed planetary gear, which is the same as the linear speed of the two sets of gears, is 20, and. The two sets of gear modules on the variable-linear-speed planetary gear of the variable-linear-speed double-layer planetary gear row are different, and the characteristic parameter is 0.9. K in the motion equation of the reverse transfer case is 9.

The homodromous clutch adopts a variable-linear-speed double-layer star planet row, the motion characteristic equation of the homodromous clutch is Nt2-0.5 Nq2- (1-0.5) Nj2 is 0, and the motion equation of the homodromous clutch is NA2 is 0.5 NB2+0.5 NC 2. That is, the number of gear teeth of the sun gear t2, i.e., a2, of the variable-linear-speed double-star planetary row is 30, the number of gear teeth of the ring gear q2, i.e., C2, is 20, the number of gear teeth of one side of the variable-linear-speed planetary gear, which is engaged with the sun gear, is 30, and the number of gear teeth of the other side of the variable-linear-speed planetary gear, which is engaged with the ring gear, is 40. Sun gear t2, i.e., a2, is used as a central input end, B2, i.e., ring gear q2, is used as an input end and an output end, and C2, i.e., carrier j2, is used as the other input end and the output end.

The dynamic equation of the coupling gear is Nt3+1 Nq3- (1+1) Nj3 is 0, and the dynamic equation of the coupling gear is NA3 is 0.5 NB3+0.5 NC 2. The gear tooth numbers of two central gears B3 and C3 of a single-layer planet row of the bevel gear are both 20, a planet carrier j3 and A3 are also used as a turnover control end, planet gears are uniformly distributed on the planet carrier, the gear tooth numbers of the planet gears are all 20, one planet gear is used as a single-path output end, the axial direction of the output end forms an included angle of 90 degrees with a shaft of a unidirectional clutch, and the rotating speed of the output end is NX 3. The characteristic parameter of the single-layer planet row of the bevel gear is 1.0.

The output end B2 of the equidirectional transfer case is connected with a central wheel B3 of the hundred-direction clutch, the other output end C2 of the equidirectional transfer case is connected with a central wheel C3 of the hundred-direction clutch, the two connections are called rear-end connection, and two connection modes are provided. The back end connection of the embodiment adopts a first connection mode. The syntropy combiner output ends B2 and C2 are directly connected with the syntropy combiner central wheels B3 and C3 respectively, NB2 is NB3, and NC2 is NC 3.

The present embodiment has two application modes. In a first application, when the input speed NA1 is determined, the epicyclic control terminal A3 is kept free, and the input speed NA2 of the centre is adjusted with a lower torque to be zero, the output speed is proportional to the input speed: NX3 ═ NA1 (1/19). The output end is axially directed to form a 90-degree included angle with the shaft of the unidirectional clutch for directional transmission, and the output end is not directed to rotate around the shaft of the unidirectional clutch. The input rotation speed NA1 is maintained, and NX3 is (1/19) NA 1. When the rotating speed NA2 of the input end of the center is adjusted to be not zero by small torque, the axial direction of the output end is transmitted at an included angle of 90 degrees with the shaft of the unidirectional clutch, meanwhile, the axial direction of the output end is rotated around the shaft of the unidirectional clutch, the rotating speed NA3 is in direct proportion to the rotating speed NA2 of the input end of the center, and long-distance operation and control of transmission rotation of the unidirectional clutch are achieved.

In the second application mode, when the input end rotating speed NA1 is determined, the central input end A2 is kept free, and the rotating speed NA3 of the regulating epicyclic control end with smaller torque is determined to be zero, the output rotating speed is equal to or greater than the input rotating speed: NX3 ═ NA1 (1/19). The output end is axially directed to form a 90-degree included angle with the shaft of the unidirectional clutch for directional transmission, and the output end is not directed to rotate around the shaft of the unidirectional clutch. The input rotation speed NA1 is maintained, and NX3 is (1/19) NA 1. When the rotating speed NA3 of the turnover control end is adjusted by a small torque and is determined to be not zero, the axial direction of the output end is transmitted at an included angle of 90 degrees with the shaft of the hundred-direction clutch, and the axial direction of the output end is circulated around the shaft of the hundred-direction clutch according to the rotating speed NA3, so that the tail end control of the hundred-direction transmission turnover is realized.

The above examples are only some of the embodiments of the present invention.

Claims (2)

1. The reverse transfer double-control one-hundred-direction driver consists of a reverse transfer case, a same-direction clutch and a one-hundred-direction clutch, has a specific connection mode and a specific transmission path, and is a single-row planetary row, and is characterized in that the planetary row meets the condition one: the motion characteristic equation of the reverse transfer case is a reverse transfer case motion equation NA1 ═ 1+ k) × (NB 1-k) × NC1, k >1.0 after being sorted and deformed, in a reverse transfer case planet row, a component A1 corresponding to NA1 is used as the input end of the reverse transfer case, which is also the input end of the reverse transfer case double-control one-hundred-way transmission, the other two components are used as the transfer ends of the reverse transfer case, the transfer end B1 is connected with the output end B2 of the input end of a homodromous case, the transfer end C1 is connected with the output end C2 of the input end of the homodromous case double-layer planet row which can be a variable linear speed double-layer planet row or a common cylindrical gear double-layer planet row, and the planet row is characterized in that the form of the motion characteristic equation after being sorted and deformed meets the condition two: the motion equation NA2 of the homodromous clutch is 0.5 × NB2+0.5 × NC2, a central wheel A2 corresponding to the NA2 serves as a central input end, B2 and C2 are two input ends of the homodromous clutch and two output ends, the two input ends serve as input ends and are respectively connected with two transfer ends of the reverse transfer case, two connections between the output ends and the central wheel of the transfer case are called rear end connections, and the rear end connections are in two connection modes: in the first connection mode, the transmission ratios of two rear-end connections are n or-n, namely two rotation speeds which are originally in the same direction are connected and transmitted and then keep in the same direction, two rotation speeds which are originally in the same direction are connected and transmitted and then keep in the opposite direction, in the second connection mode, one of the transmission ratios of the two rear-end connections is n, the other is-n, namely the two rotation speeds which are originally in the same direction are connected and transmitted and then converted into the opposite direction, the two rotation speeds which are originally in the opposite direction are connected and transmitted and then converted into the same direction, the one-way clutch is a single-row planetary gear, the shaft of the planetary gear is a shaft of the one-way clutch, the planetary gear can be a bevel gear single-layer planetary gear or a variable linear speed single-layer planetary gear, and the characteristic is that the planetary: the motion characteristic equation is in a form of NA3 being 0.5 × NB3+0.5 × NC3 after arrangement and deformation, a planet carrier j3 corresponding to NA3 is also A3 as a turnover control end, and the turnover control end is also the turnover control end of the reverse transfer double-control hundred-direction transmission, one or two planet wheels in the hundred-direction clutch are used as output ends, the output rotating speed is the output end self-rotating speed NX3, and the output end is also the output end of the reverse transfer double-control hundred-direction transmission.

2. The reverse transfer double-control hundred-direction driver as claimed in claim 1 is a planet row composite structure, is a two-degree-of-freedom determination system, has different connection modes at the rear end thereof, and has different corresponding application modes, wherein one corresponding connection mode has an application mode one: the input end A1 inputs a rotating speed NA1, the rotating speed NA1 can be transmitted to the output end to form an output rotating speed NX3, the output end is axially directed and can rotate around a hundred-direction clutch shaft, a rotating control end is kept free, the rotating speed NA2 of the central input end can be adjusted by small torque, the rotating speed NA3 of the output end, which is axially directed, can be adjusted, the rotating can be controlled, the NA2 is in direct proportion to the NA3, and the first connecting mode and the second connecting mode correspond to the first connecting mode: the input rotating speed NA1 at the input end A1 can be transmitted to the output end to form the output rotating speed NX3, the axial direction of the output end can be rotated around the shaft of the unidirectional clutch, the central input end is kept free, the axial direction of the output end can be adjusted by adjusting the rotating speed NA3 of the rotating control end with smaller torque, the rotation can be controlled, and the application mode corresponding to the second connection mode is three: the rotating speed NA2 is input at the central input end A2 and can be transmitted to the output end to form an output rotating speed NX3, the output end can be axially directed and can be rotated around the shaft of the one-way clutch, so that the rotating control end can be kept free, the rotating speed NA1 of the input end can be adjusted by a small torque, the rotating speed NA3 of the output end which is axially directed can be adjusted, the rotating speed NA1 can be controlled and is in direct proportion to the NA3, in the third application mode, a single-way speed changer can be additionally arranged and is connected between the reverse transfer case and the same-direction clutch, the core purpose is that (1+ k) NB1-k NC1 can be realized by the single-way speed changer, so that the rotating speed NA3 of the output end which is axially directed can be adjusted by adjusting the rotating speed NA1 of the input end by a small torque, and the rotating speed NA3 can be controlled, the NA1 is proportional to NA3, and the third application mode in which a single speed changer is added can be called as the third application mode, and the fourth application mode corresponds to the second connection mode: the rotating speed NA2 is input at the central input end A2 and can be transmitted to the output end to form output rotating speed NX3, the axial direction of the output end can rotate around the shaft of the shutter, the input end is kept free, the axial direction of the output end can be adjusted by adjusting the rotating speed NA3 of the turnover control end with small torque, and turnover can be controlled.