CN111566387B

CN111566387B - Equidirectional transfer double-control hundred-direction driver

Info

Publication number: CN111566387B
Application number: CN201980006282.7A
Authority: CN
Inventors: 罗灿
Original assignee: Individual
Current assignee: Individual
Priority date: 2018-05-28
Filing date: 2019-05-24
Publication date: 2021-06-01
Anticipated expiration: 2039-05-24
Also published as: CN110541919A; WO2019228261A1; CN111566387A

Abstract

The invention relates to a equidirectional transfer double-control one-hundred-direction driver, which consists of a equidirectional transfer case, a sleeve shaft reverser, a double-control device and a clutch. The homodromous transfer case adopts one of five planetary rows, and the component corresponding to the maximum coefficient absolute value term in the motion characteristic equation of the homodromous transfer case is used as an input end, and the other two components are respectively used as an inner output end and an outer output end. One or two sleeve shaft commutators are adopted, and four types of sleeve shaft commutators are respectively provided with an arrangement method. The double controller adopts one of three double-layer star planet rows. The clutch adopts one of two single-layer star planet rows. The invention has two methods of setting the components of the equidirectional transfer case, the double-controller and the clutch and connecting the components. The revolution of the output shaft around the clutch shaft is controlled by inputting one of the revolution speed and the double-control rotation speed, the forward rotation and the reverse rotation are balanced, the output shaft has no unidirectional support moment, and the revolution control device and the double-control device have simple structures.

Description

Equidirectional transfer double-control hundred-direction driver

Technical Field

The invention relates to a planetary row structure transmission machine, which consists of a equidirectional transfer case, a sleeve shaft commutator, a double-controller and a clutch; in the transmission process of the power rotating speed, the output shaft is controlled to rotate around the clutch shaft, and the rotation of positive rotation and negative rotation controls the torque balance, so that the transmission is a hundred-direction transmission with simple structures of a rotation control device and a double control device.

Background

Background knowledge of the planet row: the planet row is composed of three components, namely two central wheels and a planet carrier with planet wheels, and the arrangement meshing structure relationship of the three components determines a motion characteristic equation of the planet row and determines the type of the planet row. The existing planet row is divided into a cylindrical gear planet row and a bevel gear planet row. The cylindrical gear planetary row comprises a sun gear, an inner gear ring and a planet carrier with planet gears, wherein the sun gear, the inner gear ring and the planet gears are all cylindrical gears. The cylindrical gear planet row is divided into a single-layer planet row or a double-layer planet row according to the number of the planet wheels which is one layer or double layers; a sun wheel in the single-layer planet row is meshed with a planet wheel, and the planet wheel is meshed with an inner gear ring; the sun gear is meshed with the inner planet gear in the double-layer planet row, the inner planet gear is meshed with the outer planet gear, and the outer planet gear is meshed with the inner gear ring. The bevel gear planet row comprises two central wheels and a planet carrier with planet wheels, generally a single-layer planet row, the planet wheels are one layer, and the two central wheels and the planet wheels are both bevel gears; the left central wheel is meshed with the planet wheel, and the planet wheel is meshed with the right central wheel. The sun gear and the inner gear ring both belong to a central wheel, the sun gear is a central wheel with a small pitch circle diameter on the left side, and the inner gear ring is a central wheel with a large pitch circle diameter on the right side. The invention provides that all transmission machinery consisting of two central wheels and a planet carrier with planet wheels are planet rows, one central wheel is meshed with the planet wheels, a plurality of layers of planet wheels are mutually meshed or directly connected, the planet wheels are meshed with the other central wheel, the planet carrier drives the planet wheels to rotate around the axis of the central wheel, and the planet wheels revolve and rotate; the number of the planet wheels can be one layer, two layers or three layers. For example, a double-sun-wheel planetary row is a double-layer planetary row, and comprises two central wheels (sun wheels) and a planetary carrier with planetary wheels, wherein the two central wheels and the planetary wheels are cylindrical gears; each planet gear is two coaxial gears which are called as a left planet gear and a right planet gear; the left planetary gear is meshed with the left central gear, the left planetary gear is directly connected with the right planetary gear, and the right planetary gear is meshed with the right central gear; the pitch circle diameter of the left central wheel is not equal to that of the right central wheel, and the gear module of the left central wheel is not necessarily equal to that of the right central wheel. For another example, the double-inner-gear-ring planet row is a double-layer planet row which comprises two central wheels (inner gear rings) and a planet carrier with planet wheels, wherein the two central wheels and the planet wheels are cylindrical gears; each planet gear is two coaxial gears which are called as a left planet gear and a right planet gear; the left planetary gear is meshed with the left central gear, the left planetary gear is directly connected with the right planetary gear, and the right planetary gear is meshed with the right central gear; the pitch circle diameter of the left central wheel is not equal to that of the right central wheel, and the gear module of the left central wheel is not necessarily equal to that of the right central wheel. For another example, the double-sun-wheel double-planet-wheel-shaft planet row is a single-layer planet row, and comprises two central wheels (sun wheels) and a planet carrier with two planet wheels, wherein the two central wheels and the planet wheels are cylindrical gears; the planet carrier is provided with an inner planet wheel shaft and an outer planet wheel shaft, an inner planet wheel is arranged on the inner planet wheel shaft, and each planet wheel on the outer planet wheel shaft is two coaxial gears which are called as a left outer planet wheel and a right outer planet wheel; the left central wheel is meshed with the inner planetary wheel, the inner planetary wheel is meshed with the left outer planetary wheel, the left outer planetary wheel is directly connected and coaxial with the right outer planetary wheel, and the right outer planetary wheel is meshed with the right central wheel; the left side sun gear module does not have to be equal to the right side sun gear module. The method comprises the following steps of setting a left central wheel as z, a planet carrier as j, a right central wheel as y, a left planet wheel or a left outer planet wheel as xz, a right planet wheel or a right outer planet wheel as xy, setting Zz as the number of teeth of the left central wheel, Zy as the number of teeth of the right central wheel, Zxz as the number of teeth of the left planet wheel or the left outer planet wheel, Zxy as the number of teeth of the right planet wheel or the right outer planet wheel, Nz as the rotating speed of the left central wheel, Ny as the rotating speed of the right central wheel, and Nj as the rotating speed of the planet carrier; the characteristic parameters a of the cylindrical gear planet row and the bevel gear planet row are Zy/Zz, and the characteristic parameters of the double-sun gear planet row, the characteristic parameters of the double-inner-gear ring planet row and the characteristic parameters of the double-sun gear double-planet-shaft planet row are all a ═ Zy Zxz)/(Zz Zxy). The motion characteristic equation of all single-layer star planet rows is as follows: nz + a by Ny ═ 1+ a by Nj, and the rows of planets subject to the kinematic characteristic equation are all single-layer planetary rows; in the motion characteristic equation, the term of maximum absolute value of the coefficient is Nj, and the component corresponding to the term is the carrier. The motion characteristic equation of all the double-layer star-planet rows is as follows: nz-a Ny ═ (1-a) × Nj, the planet rows obeying the kinematic characteristic equation are all double-layer planet rows; when a <1.0, the term of maximum coefficient absolute value in the motion characteristic equation is Nz, and the term corresponding to the part is the one-side center wheel denoted as z, and when a >1.0, the term of maximum coefficient absolute value in the motion characteristic equation is Ny, and the term corresponding to the part is the one-side center wheel denoted as y.

The transmission with the input shaft and the output shaft having an included angle is called a zigzag transmission, the included angle is called a zigzag angle, and the transmission with the zigzag angle kept unchanged and the output shaft rotating is called a rotatable zigzag transmission. The traditional turnover folding driver is mainly a bevel gear folding driver, the folding driver is realized by utilizing a bevel gear pair, a folding angle is fixed, and an output shaft of the traditional turnover folding driver is controlled to turn around an input shaft and then is used as the turnover folding driver; when the transmission is folded, a large unidirectional support moment is formed on the output shaft, the unidirectional support moment is related to the power torque of the transmission, and the larger the power torque is, the larger the unidirectional support moment is; the unidirectional support moment is related to the size of the turning angle, and the larger the turning angle is, the larger the unidirectional support moment is. Due to the existence of the unidirectional support moment, when the traditional turnover folding driver controls the turnover of the output shaft, the turnover control moment required by forward rotation and reverse rotation is completely unbalanced; the epicyclic control device is complicated in structure, requiring a device with a very large torque, such as a hydraulic device, to control the output shaft epicyclic, or requiring additional balancing means, such as a reverse spring device, to provide a reverse torque to counteract the unidirectional support torque.

The invention provides a structure of a unidirectional driver, which is a equidirectional transfer double-control unidirectional driver.A revolution speed or a double-control revolution speed is input to control an output shaft to revolve around a clutch shaft; the double-control transmission is a new type of reversible transmission, in the transmission process of power rotating speed, the output shaft is controlled to rotate around the clutch shaft, the forward rotation and the reverse rotation are controlled to control the torque balance, and the reversible control device and the double-control device are simple in structure and are called as double-control one-hundred-direction transmission.

Disclosure of Invention

The invention relates to a equidirectional transfer double-control one-hundred-direction driver, which consists of an equidirectional transfer case, a sleeve shaft reverser, a double-control device and a clutch.

The homodromous transfer case has a homodromous transfer case input end, a homodromous transfer case internal output end, a homodromous transfer case external output end, and the homodromous transfer case makes a rotational speed of its input end convert into its internal output end, two rotational speeds that the direction of rotation of its external output end is the same. The homodromous transfer case adopts a planet row, the wheel set number of planet wheel is a set to six groups, one of three parts that set up the planet row is as homodromous transfer case input, and other two parts are as homodromous transfer case internal output end, homodromous transfer case outer output end respectively, and the condition of setting makes the rotation direction of two rotational speeds of homodromous transfer case internal output end, homodromous transfer case outer output end output the same when the input rotational speed of homodromous transfer case input. It can also be expressed as: and a component corresponding to the maximum absolute value of the coefficient in the motion characteristic equation of the planetary row of the equidirectional transfer case is set as the input end of the equidirectional transfer case, and the other two components are respectively used as the inner output end of the equidirectional transfer case and the outer output end of the equidirectional transfer case. The equidirectional transfer case planet row adopts one of five kinds of planet rows, wherein: when the bevel gear single-layer star planet row is adopted, the part corresponding to the maximum absolute value of the coefficient in the motion characteristic equation of the bevel gear single-layer star row is a planet carrier, the planet carrier is used as the input end of the equidirectional transfer case, and the left central wheel and the right central wheel are respectively used as the inner output end and the outer output end of the equidirectional transfer case. Referring to fig. 3, in fig. 3, a planet carrier of a single-layer planet row of bevel gears is used as an input end (1) of the equidirectional transfer case, a left central wheel is used as an inner output end (2) of the equidirectional transfer case, and a right central wheel is used as an outer output end (3) of the equidirectional transfer case. When a double-sun-wheel double-planet-wheel-shaft planet row is adopted, the part corresponding to the maximum absolute value of the coefficient in the motion characteristic equation is a planet carrier, the planet carrier is used as the input end of the equidirectional transfer case, and the left central wheel and the right central wheel are respectively used as the inner output end and the outer output end of the equidirectional transfer case. Referring to fig. 4, in fig. 4, a planet carrier of a double-sun-wheel double-planet-wheel-shaft planet row is used as an input end (1) of the equidirectional transfer case, a left central wheel (4) is used as an inner output end (2) of the equidirectional transfer case, a right central wheel (5) is used as an outer output end (3) of the equidirectional transfer case, and in fig. 4, (6) is an inner planet wheel, (7) is a left outer planet wheel, and (8) is a right outer planet wheel. When the double-layer planetary gear row of the cylindrical gear is adopted, the part corresponding to the maximum absolute value of the coefficient in the motion characteristic equation is a central wheel (inner gear ring) with a large pitch circle diameter, the central wheel (inner gear ring) with the large pitch circle diameter is used as the input end of the equidirectional transfer case, and the planet carrier and the central wheel (sun gear) with the small pitch circle diameter are respectively used as the inner output end and the outer output end of the equidirectional transfer case. Referring to fig. 5, in fig. 5, the inner gear ring of the double-layer planetary row of the cylindrical gear is used as the input end (1) of the equidirectional transfer case, the planet carrier is used as the inner output end (2) of the equidirectional transfer case, and the sun gear is used as the outer output end (3) of the equidirectional transfer case. When the double-sun-wheel planet row is adopted, the part corresponding to the maximum absolute coefficient value in the motion characteristic equation is the larger pitch circle diameter of the two central wheels (sun wheels), the central wheel (sun wheel) with the larger pitch circle diameter is used as the input end of the equidirectional transfer case, and the planet carrier and the other central wheel (sun wheel) are respectively used as the inner output end and the outer output end of the equidirectional transfer case. Referring to fig. 6, in fig. 6, a central gear with a larger pitch circle diameter of a double-sun-gear planet row is used as an input end (1) of the equidirectional transfer case, a planet carrier is used as an inner output end (2) of the equidirectional transfer case, and the other central gear is used as an outer output end (3) of the equidirectional transfer case. When the double-inner-gear-ring planet row is adopted, the part corresponding to the maximum absolute coefficient value in the motion characteristic equation is the smaller pitch circle diameter of the two central wheels (inner gear rings), the central wheel (inner gear ring) with the smaller pitch circle diameter is used as the input end of the equidirectional transfer case, and the planet carrier and the other central wheel (inner gear ring) are respectively used as the inner output end and the outer output end of the equidirectional transfer case. Referring to fig. 7, in fig. 7, a central wheel with a smaller pitch circle diameter of a double-ring gear planet row is used as an input end (1) of the equidirectional transfer case, a planet carrier is used as an inner output end (2) of the equidirectional transfer case, and the other central wheel is used as an outer output end (3) of the equidirectional transfer case.

The quill commutator comprises an inner shaft and an outer shaft of the quill, the inner shaft is provided with an inner input end and an inner output end, and the outer shaft is provided with an outer input end and an outer output end. The sleeve shaft commutator converts two rotating speeds with the same rotating direction of the inner input end and the outer input end thereof into two rotating speeds with opposite rotating directions of the inner output end and the outer output end thereof; and two rotating speeds with the same rotating direction of the inner output end and the outer output end are converted into two rotating speeds with opposite rotating directions of the inner input end and the outer input end. The invention adopts one or two sleeve shaft commutators, which are called as a left sleeve shaft commutators and a right sleeve shaft commutators when two sleeve shaft commutators are adopted, and the left sleeve shaft commutators and the right sleeve shaft commutators are not necessarily the same. There are four types of quill commutators: the first type is a bevel gear planet row commutator, and the outer shaft adopts a bevel gear single-layer planet row, which is shown in figure 8. In fig. 8, an inner input end (1) and an inner output end (2) are arranged on an inner shaft of a sleeve shaft, a left central wheel of a bevel gear single-layer planet row on an outer shaft of the sleeve shaft is used as an outer input end (2) of a commutator, a right central wheel is used as an outer output end (4) of the commutator, a bevel gear planet wheel (5) is meshed with the left central wheel and the right central wheel, so that the planet carrier is fixed, and the number of the wheel sets of the bevel gear planet wheel (5) in the planet row can be from one set to six sets. The rotation direction of the external input end (2) of the commutator is opposite to that of the external output end (4) of the commutator. The second type is a double-sun-wheel double-planet-wheel-shaft planet row commutator, and a double-sun-wheel double-planet-wheel-shaft planet row is adopted as an outer shaft, which is shown in figure 9. In fig. 9, an inner input end (1) and an inner output end (3) are arranged on an inner shaft of a sleeve shaft, a left central wheel of a double-sun-wheel double-planet-shaft planet row on the outer shaft of the sleeve shaft is used as an outer input end (2) of a commutator, a right central wheel is used as an outer output end (4) of the commutator, so that the planet carrier is fixed, and the number of the wheel sets of the inner planet wheel (5), the left outer planet wheel (6) and the right outer planet wheel (7) of the planet row can be from one set to six sets. The rotation direction of the external input end (1) of the commutator is opposite to that of the external output end (3) of the commutator. The third type is a position-retaining two-way commutator, and an inner shaft and an outer shaft are respectively driven by bevel gear pairs, which is shown in figure 10. In fig. 10, the inner input end and the outer input end of the position-retaining two-way commutator form an input sleeve shaft, the inner output end and the outer output end form an output sleeve shaft, an input sleeve shaft bearing and an output sleeve shaft bearing are respectively fixed, and the input sleeve shaft and the output sleeve shaft form an included angle of 90 degrees; an inner driving bevel gear is arranged on the inner input end (1), an outer driving bevel gear is arranged on the outer input end (2), an inner driven bevel gear (5) is arranged on the inner output end (3), an outer driven bevel gear (6) is arranged on the outer output end (4), the inner driving bevel gear is meshed with the inner driven bevel gear (5), the outer driving bevel gear is meshed with the outer driven bevel gear (6), and the modulus of the inner driving bevel gear is not necessarily equal to that of the outer driving bevel gear. Two rotating speeds with the same rotating direction are input to the inner input end and the outer input end, and two rotating speeds with opposite rotating directions are output to the inner output end and the outer output end. The fourth type is a transposition two-way commutator, an inner shaft and an outer shaft are respectively driven by bevel gear pairs, referring to fig. 11, an inner input end and an outer input end of the transposition two-way commutator in fig. 11 form an input sleeve shaft, an inner output end and an outer output end form an output sleeve shaft, and the input sleeve shaft and the output sleeve shaft form an included angle of 90 degrees; an inner driving bevel gear is arranged on an inner input end (1), an outer driving bevel gear is arranged on an outer input end (2), an inner driven bevel gear (5) is arranged on an inner output end (3), an outer driven bevel gear (6) is arranged on an outer output end (4), the inner driving bevel gear is meshed with the outer driven bevel gear (6), the outer driving bevel gear is meshed with the inner driven bevel gear (5), and the modulus of the inner driving bevel gear is not necessarily equal to that of the outer driving bevel gear. Two rotating speeds with the same rotating direction are input to the inner input end and the outer input end, and two rotating speeds with opposite rotating directions are output to the outer output end and the inner output end. In the invention, the transmission ratio of the inner shafts of the bevel gear planet row commutator and the double-sun gear double-planet-shaft planet row commutator is set to be 1.0, the transmission ratio of the outer shafts is set to be-1.0, and the setting method is a method known in the industry; for example: and making the tooth number of the left central gear in the bevel gear planet row commutator equal to the tooth number of the right central gear equal to the tooth number of the bevel gear planet gear. The transmission ratio of the position-keeping two-way reverser from the inner input end to the inner output end is set to be-1.0, the transmission ratio from the outer input end to the outer output end is set to be 1.0, and the setting method comprises the following steps: the inner driving bevel gear tooth number is equal to the inner driven bevel gear tooth number, and the outer driving bevel gear tooth number is equal to the outer driven bevel gear tooth number. The transmission ratio of the transposition two-way commutator from the inner input end to the outer output end is set to be-1.0, and the transmission ratio of the transposition two-way commutator from the outer input end to the inner output end is set to be 1.0.

The double controller has one double controller input, one left inner output and right inner output, one left outer output and one right outer output, and converts the input rotation speed into two rotation speeds with the same rotation direction and the same rotation direction. The double-controller adopts a double-layer planet row, the number of the wheel sets of the planet wheels is one to six, a left central wheel is used as the input end of the double-controller, the other central wheel is used as the left inner output end and the right inner output end, the planet carrier is used as the left outer output end and is used as the right outer output end, and the left central wheel is also a component corresponding to the maximum coefficient absolute value in the motion characteristic equation of the double-controller planet row. The double-controller adopts one of three double-layer star planet rows, the first double-layer star planet row adopts a cylindrical gear, the part corresponding to the maximum absolute value of the coefficient in the motion characteristic equation is a central wheel (inner gear ring) with a large pitch circle diameter, referring to fig. 12, the central wheel (inner gear ring) with the large pitch circle diameter is used as the input end (1) of the double-controller in fig. 12, the other central wheel (sun gear) is used as the left inner output end and the right inner output end (2), and the planet carrier is used as the left outer output end (3) and the right outer output end (4). External connection of the dual controller input end is as follows: the double control gear (5) is directly connected with the inner gear ring, the paraxial gear (6) meshed with the double control gear is arranged, and double control rotating speed is input to the input end (1) of the double controller through the paraxial gear (6) and the double control gear (5). The second one adopts a double-sun-wheel planet row, the part corresponding to the maximum absolute value of the coefficient in the motion characteristic equation is the part with larger pitch circle diameter in two central wheels (sun wheels), see fig. 13, the central wheel with larger pitch circle diameter in fig. 13 is used as the input end (1) of the double controller, the other central wheel is used as the left inner output end and the right inner output end (2), and the planet carrier is used as the left outer output end (3) and the right outer output end (4). External connection of the dual controller input end is as follows: the worm wheel (5) is directly connected with the sun wheel, the worm (6) is matched with the worm wheel, and the double-control rotating speed is input to the input end (1) of the double-controller through the worm wheel and worm device. The third method adopts a double-inner-gear-ring planet row, the part corresponding to the maximum coefficient absolute value item in the motion characteristic equation is the part with the smaller pitch circle diameter in two central wheels (inner gear rings), referring to fig. 14, the central wheel with the smaller pitch circle diameter in fig. 14 is used as the input end (1) of the double-controller, the other central wheel is used as the left inner output end and the right inner output end (2), and the planet carrier is used as the left outer output end (3) and the right outer output end (4). External connection of the dual controller input end is as follows: the worm wheel (5) is directly connected with the inner gear ring, the worm (6) is matched with the inner gear ring, and the double-control rotating speed is input to the input end (1) of the double-controller through the worm wheel and worm device.

The clutch is a transmission device which synthesizes and converts two rotating speeds with opposite rotating directions at the inner input end and the outer input end thereof into the rotating speed of the planet gear thereof, and converts two rotating speeds with the same rotating direction at the inner input end and the outer input end thereof into the rotating speed of the planet carrier thereof. The method comprises the following steps that a single-layer planet row is adopted, the number of wheel sets of planet wheels ranges from one set to six sets, the planet row shaft is a clutch shaft, a left central wheel is used as an external input end of the clutch, a right central wheel is used as an internal input end of the clutch, a planet carrier is used as a turnover control end, one to six planet wheels are used as output ends, an output shaft is the planet wheel shafts, and the output shaft and the clutch shaft form a folding angle; the output end of the clutch is also the output end of the equidirectional split double-control hundred-direction driver. The clutch adopts one of two single-layer star planetary rows, the first single-layer star planetary row adopts a bevel gear single-layer star planetary row, referring to fig. 15, in fig. 15, a left central wheel is used as an external input end (2) of the clutch, a right central wheel is used as an internal input end (1) of the clutch, a planet carrier is used as a turnover control end (3), one or more bevel gear planet wheels are used as an output end (4), an output shaft is a shaft of the bevel gear planet wheels, and the output shaft and the shaft of the clutch form a 90-degree folding angle. The second type adopts a double-sun-wheel double-planet-wheel-shaft planet row, referring to fig. 16, in fig. 16, a left central wheel is used as an external input end (2) of a clutch, a right central wheel is used as an internal input end (1) of the clutch, a planet carrier is used as a turnover control end, one to six planet wheels are used as output ends (5), output shafts are the planet wheel shafts, and the output shafts and the clutch shaft are parallel to form a 0-degree folding angle. External connection of the epicyclic control terminal is as follows: a worm wheel (3) is arranged on the planet carrier at the turnover control end, and a worm (4) meshed with the worm wheel is arranged. The epicyclic rotation speed can be input to the epicyclic control end through the worm gear device, so that the planet carrier is circulated around the clutch shaft, and the output shaft is also circulated around the clutch shaft.

The setting method of each component of the equidirectional transfer case, the double-controller and the clutch in the equidirectional transfer double-control hundred-direction driver is as follows: when the homodromous transfer case adopts a single-layer star planet row, the characteristic parameter is equal to 1.0, and when the homodromous transfer case adopts a double-layer star planet row, the characteristic parameter is equal to 2.0; the characteristic parameter of the double-controller double-layer star planet row is equal to 2.0; the characteristic parameter of the single-layer star planet row of the clutch is equal to 1.0. The setting methods adopt the expression of the characteristic parameters of the digital planet row, and the characteristic parameters of the planet row are substantially the expression of the tooth number and the structural setting of each component of the equidirectional transfer double-control hundred-direction driver. For example, when the homodromous transfer case adopts a bevel gear single-star planetary row, "making its characteristic parameter equal to 1.0" means setting the number of teeth of its left-side sun gear equal to the number of teeth of its right-side sun gear. As can be understood by persons skilled in the art, characteristic parameters of each planet row are set, the tooth number and the structure of each planet row are correspondingly set, and finally, the equidirectional transfer double-control hundred-direction driver structure is correspondingly set.

The present invention has two connection methods. When a sleeve shaft commutator is adopted, the first connecting method of the invention is as follows: the inner output end of the homodromous transfer case is directly connected with the inner input end of a sleeve shaft commutator, the outer output end of the homodromous transfer case is directly connected with the outer input end of the sleeve shaft commutator, the inner output end of the sleeve shaft commutator is directly connected with the left inner output end of a dual-controller, the outer output end of the sleeve shaft commutator is directly connected with the left outer output end of the dual-controller, the right inner output end of the dual-controller is directly connected with the inner input end of a clutch, and the right outer output end of the dual-controller is directly connected with the outer input end of the clutch; the input end of the equidirectional transfer case is connected with a power source, the input end of the double-controller is indirectly connected with the double-control device through the double-control gear and the paraxial gear, the turnover control end is connected with the turnover control device, and the output end of the clutch is connected with the power using device. The input epicyclic or twin rotational speeds do not exclude a rotational speed of zero. When two sleeve shaft commutators are adopted, the second connecting method of the invention is as follows: the inner output end of the homodromous transfer case is directly connected with the inner input end of the left sleeve shaft commutator, the outer output end of the homodromous transfer case is directly connected with the outer input end of the left sleeve shaft commutator, the inner output end of the left sleeve shaft commutator is directly connected with the left inner output end of the dual-controller, the outer output end of the left sleeve shaft commutator is directly connected with the left outer output end of the dual-controller, the right inner output end of the dual-controller is directly connected with the inner input end of the right sleeve shaft commutator, the right outer output end of the dual-controller is directly connected with the outer input end of the right sleeve shaft commutator, the inner output end of the right sleeve shaft commutator is directly connected with the inner input end of the clutch, and the outer output end; the input end of the double-controller is indirectly connected with a power source through a double-control gear and a paraxial gear, the input end of the equidirectional transfer case is connected with a double-control device, the turnover control end is connected with a turnover control device, and the output end of the clutch is connected with a power using device. The input epicyclic or twin rotational speeds do not exclude a rotational speed of zero, i.e. the setting of a brake.

The power rotating speed input from a power source is converted into the rotating speed of the output end of the clutch through transmission of the clutch, and the input and output of the power rotating speed are not interfered with the revolving rotating speed and are not interfered with the double-control rotating speed; the invention controls the output shaft to rotate around the clutch shaft by inputting one of the rotating speed and the double-control rotating speed. The input and output of the power rotating speed are not interfered with the revolving rotating speed and the double-control rotating speed, the forward rotation and the reverse rotation of the revolving output shaft are controlled to be balanced, the output shaft has no unidirectional support moment, and the revolving control device and the double-control device do not need to overcome the unidirectional support moment, so the structures of the revolving control device and the double-control device are simple. In the control process, the turnover control device and the double-control device are linked, the turnover control device can passively rotate when the double-control device inputs a non-zero double-control rotating speed, and the double-control device can passively rotate when the turnover control device inputs a non-zero turnover rotating speed.

The connection of the invention is divided into direct connection and indirect connection, the direct connection enables the rotating speeds of all the parts participating in the connection to be the same, and the indirect connection enables all the parts participating in the connection to form a fixed rotating speed proportional relation. The connection in the present invention means a direct connection or an indirect connection. The inner output end and the outer output end mean that the two components form a sleeve shaft, the inner output end is used as an inner shaft of the sleeve shaft, and the outer output end is used as an outer shaft of the sleeve shaft; the inner input end and the outer input end mean that the two components form a sleeve shaft, the inner input end is used as an inner shaft of the sleeve shaft, and the outer input end is used as an outer shaft of the sleeve shaft; with exceptions, this will be specifically noted. The power source is an engine such as a fuel engine and an electric engine, or a transmission reducer transmission device of a transmission behind the engine; the power source is directly connected with the input end of the equidirectional transfer case, so that the power rotating speed can be input to the input end of the equidirectional transfer case; the power source is indirectly connected with the input end of the double controller through the double control gear and the paraxial gear, and can input power rotating speed to the input end of the double controller. The turnover control device is an electric control device, a hydraulic control device and the like; the turnover control device is connected with the turnover control end and can input turnover rotating speed to the turnover control end. The double-control device is an electric control device, a hydraulic control device and the like; the double-control device is directly connected with the input end of the equidirectional transfer case and can input double-control rotating speed to the input end of the equidirectional transfer case; the double-control device is indirectly connected with the input end of the double-controller through a double-control gear, a paraxial gear or a worm gear device, and can input double-control rotating speed to the input end of the double-controller. The power using device is a rear end device connected with the output end of the clutch, such as a rotor wing, a double rotor wing, a propeller, a double propeller, a wind wheel, a driving shaft and the like.

The invention can be used for the transmission of aircraft tiltably-rotating rotors, helicopter direction-changeable rotors, ship direction-changeable propellers and the like in all directions. The cross-movable joint transmission for the robot is a hundred-direction transmission. The wind driven generator is used for adjusting the direction of a wind wheel shaft. The transmission device is used for the transmission of the steering driving wheel of the motor vehicle.

The equidirectional transfer double-control one-hundred-direction driver has the advantages that the equidirectional transfer case, the sleeve shaft reverser, the double-control device and the clutch form the equidirectional transfer case, the method for setting each part is provided, and two connection methods are provided; in the transmission process of the power rotating speed, the output shaft is controlled to rotate around the clutch shaft by inputting one of the rotating speed for rotating and the double-control rotating speed, so that the purposes that the output shaft rotates around the clutch shaft, the rotation of the forward rotation and the reverse rotation controls the torque balance, and the structures of the rotation control device and the double-control device are simple are achieved. The invention controls the output shaft to rotate around the clutch shaft by inputting one of the rotating speed for rotating and the double-control rotating speed, the former is convenient for controlling the output shaft to rotate nearby, and the latter is convenient for remotely controlling the output shaft to rotate.

Drawings

Fig. 1 is a schematic diagram of a co-rotating double-control hundred-direction transmission adopting a sleeve shaft commutator, and is also a schematic diagram of embodiment 1 of the invention. 1 is syntropy transfer case input, 2 is syntropy transfer case internal output end, 3 is syntropy transfer case outer output end, 4 is bevel gear planet row commutator, 5 is the dual accuse ware input, 6 is dual accuse ware left side internal output end and right internal output end, 7 is dual accuse ware left side outer output end, 8 is dual accuse ware right side outer output end, 9 is the clutch internal input end, 10 is the clutch external input end, 11 is the turnover control end, 12 is the clutch output end, 13 is double control gear, 14 is the paraxial gear. In the figure, a bidirectional transfer case adopts a double-sun-wheel planetary row, a double-controller adopts a double-sun-wheel planetary row, and a clutch adopts a bevel gear single-layer planetary row; in the figure, each planet row is a half-width sketch, and the paraxial gear is a whole sketch.

Fig. 2 is a schematic diagram of a co-rotating double-control hundred-direction transmission of the invention using two sleeve shaft commutators, and is also a schematic diagram of embodiment 2 of the invention. 1 is syntropy transfer case input, 2 is syntropy transfer case interior output, 3 is syntropy transfer case outer output end, 4 is left side quill commutator, 5 is the dual control ware input, 6 is dual control ware left side interior output end and right interior output end, 7 is dual control ware left side outer output end, 8 is dual control ware right side outer output end, 9 is the inter-engaging ware input, 10 is the inter-engaging ware outer input end, 11 is the turnover control end, 12 is the inter-engaging ware output, 13 is double control gear, 14 is the paraxial gear, 15 is right side quill commutator. In the figure, a bidirectional transfer case adopts a double-sun-wheel planet row, a left-side reverser and a right-side reverser both adopt bevel-gear planet row reversers, a double-controller adopts a double-sun-wheel planet row, and a clutch adopts a bevel-gear single-layer planet row; in the figure, each planet row is a half-width sketch, and the paraxial gear is a whole sketch.

FIG. 3 is a schematic diagram of a homodromous transfer case adopting a bevel gear single-layer star planet row, and is a half sketch. 1 is an input end, 2 is an inner output end, and 3 is an outer output end.

Fig. 4 is a schematic diagram of a homodromous transfer case adopting a double-sun-wheel double-planet-wheel-shaft planet row, and is a semi-schematic diagram. 1 is the input, 2 is interior output, 3 is outer output, 4 is left side centre wheel, 5 is right side centre wheel, 6 is interior planet wheel, 7 is the outer planet wheel of left side, 8 is the outer planet wheel of right side.

Fig. 5 is a schematic diagram of a homodromous transfer case adopting a cylindrical gear double-layer star planet row, and is a half-width schematic diagram. 1 is an input end, 2 is an inner output end, and 3 is an outer output end.

Fig. 6 is a schematic diagram of a homodromous transfer case adopting a double-sun-wheel planet row, and is a semi-sketch. 1 is an input end, 2 is an inner output end, and 3 is an outer output end.

Fig. 7 is a schematic diagram of a homodromous transfer case adopting a double-ring gear planet row, which is a semi-schematic diagram. 1 is an input end, 2 is an inner output end, and 3 is an outer output end.

FIG. 8 is a schematic illustration of a bevel gear planet row reverser, in semi-schematic. 1 is an inner input end, 2 is an outer input end, 3 is an inner output end, 4 is an outer output end, and 5 is a bevel gear planet gear.

Fig. 9 is a schematic diagram of a double-sun-wheel double-planet-wheel-shaft planet row commutator, which is a semi-schematic diagram. 1 is an inner input end, 2 is an outer input end, 3 is an inner output end, 4 is an outer output end, 5 is an inner planet wheel, 6 is a left outer planet wheel, and 7 is a right outer planet wheel.

Fig. 10 is a schematic view of a position-retaining two-way diverter, which is a full sketch. 1 is an inner input end, 2 is an outer input end, 3 is an inner output end, 4 is an outer output end, 5 is an inner driven bevel gear, and 6 is an outer driven bevel gear.

Fig. 11 is a schematic view of a transposed two-way commutator, shown in full diagrammatic view. 1 is an inner input end, 2 is an outer input end, 3 is an inner output end, 4 is an outer output end, 5 is an inner driven bevel gear, and 6 is an outer driven bevel gear.

Fig. 12 is a schematic diagram of a dual-controller adopting a cylindrical gear and a double-layer star planetary row. 1 is an input end, 2 is a left inner output end and a right inner output end, 3 is a left outer output end, 4 is a right outer output end, 5 is a double control gear, and 6 is a paraxial gear. In the figure, the paraxial gear is a whole sketch, and the rest is a half sketch.

Fig. 13 is a schematic diagram of a dual-controller adopting a double-sun-wheel planetary row. 1 is input end, 2 is left inner output end and right inner output end, 3 is left outer output end, 4 is right outer output end, 5 is worm wheel, 6 is worm. In the figure, the worm is a whole sketch, and the rest is a half sketch.

Fig. 14 is a schematic diagram of a dual controller adopting a dual ring gear planetary row. 1 is input end, 2 is left inner output end and right inner output end, 3 is left outer output end, 4 is right outer output end, 5 is worm wheel, 6 is worm. In the figure, the worm is a whole sketch, and the rest is a half sketch.

Fig. 15 is a schematic diagram of a clutch adopting a bevel gear single-layer star planetary row, and is a half-frame schematic diagram. 1 is the internal input end of the clutch, 2 is the external input end of the clutch, 3 is the turnover control end, and 4 is the output end.

Fig. 16 is a schematic diagram of a clutch employing a double sun gear, double planet shafts and a planet row. 1 is the clutch inner input end, 2 is the clutch outer input end, 3 is the worm wheel that sets up on the turnover control end, 4 is the worm, and 5 is the output. In the figure, the worm is a whole sketch, and the rest is a half sketch.

Each planet row in each figure is illustrated as a half sketch as much as possible according to industry practice, and each part in each figure only illustrates structural relation and does not reflect real size.

Detailed Description

Example 1: the invention discloses a equidirectional transfer double-control hundred-direction driver adopting a sleeve shaft commutator, which consists of an equidirectional transfer case, a sleeve shaft commutator, a double-controller and a clutch, wherein the equidirectional transfer case adopts double-sun-wheel planet rows, the bevel-gear planet-row commutator is adopted, the double-controller adopts double-sun-wheel planet rows, and the clutch adopts a bevel-gear single-layer planet row, which is shown in figure 1.

The homodromous transfer case has a homodromous transfer case input end, a homodromous transfer case internal output end, a homodromous transfer case external output end, and the homodromous transfer case makes a rotational speed of its input end convert into its internal output end, two rotational speeds that the direction of rotation of its external output end is the same. And a component corresponding to the maximum absolute value of the coefficient in the motion characteristic equation of the planetary row of the equidirectional transfer case is set as the input end of the equidirectional transfer case, and the other two components are respectively used as the inner output end of the equidirectional transfer case and the outer output end of the equidirectional transfer case. The homodromous transfer case adopts a double-sun-wheel planet row, a part corresponding to a maximum coefficient absolute value item in a motion characteristic equation of the homodromous transfer case is a central wheel with a large pitch circle diameter, the central wheel with the large pitch circle diameter is used as an input end (1) of the homodromous transfer case, a planet carrier is used as an inner output end (2) of the homodromous transfer case, and the other central wheel is used as an outer output end (3) of the homodromous transfer case. The number of the planetary wheel sets in the planetary row is two.

The sleeve shaft commutator comprises an inner shaft and an outer shaft of the sleeve shaft, the inner shaft is provided with an inner input end and an inner output end, the outer shaft is provided with an outer input end and an outer output end, and the sleeve shaft commutator converts two rotating speeds with the same rotating direction of the inner input end and the outer input end thereof into two rotating speeds with opposite rotating directions of the inner output end and the outer output end thereof; and two rotating speeds with the same rotating direction of the inner output end and the outer output end are converted into two rotating speeds with opposite rotating directions of the inner input end and the outer input end. In the embodiment, a bevel gear planet row commutator (4) is adopted, an inner input end and an inner output end are arranged on an inner shaft of a sleeve shaft, a left central wheel of a bevel gear planet row on an outer shaft of the sleeve shaft is used as an outer input end of the commutator, a right central wheel is used as an outer output end of the commutator, a bevel gear planet wheel is meshed with the left central wheel and meshed with the right central wheel, a planet carrier is fixed, and the number of groups of bevel gear planet wheels of the planet row is two. The rotation direction of the external input end of the commutator is opposite to that of the external output end of the commutator. The number of teeth of the left central gear is equal to that of teeth of the right central gear is equal to that of teeth of the bevel gear planet gear 18, and the gear module of the left central gear is not equal to that of the right central gear.

The double controller has one double controller input, one left inner output and right inner output, one left outer output and one right outer output, and converts the input rotation speed into two rotation speeds with the same rotation direction and the same rotation direction. The double-controller adopts a double-layer planet row, the number of the wheel sets of the planet wheels is one to six, the left central wheel is used as the input end of the double-controller, the other central wheel is used as the left inner output end and is used as the right inner output end, the planet carrier is used as the left outer output end and is used as the right outer output end, and the left central wheel is also a component corresponding to the maximum coefficient absolute value in the motion characteristic equation of the double-layer planet row. The double-controller adopts double-sun-wheel planet rows, the number of the wheel sets of the planet wheels is two, the part corresponding to the maximum coefficient absolute value item in the motion characteristic equation is a central wheel with a large pitch circle diameter, the central wheel with the large pitch circle diameter is used as the input end (5) of the double-controller, the other central wheel is used as the left inner output end and the right inner output end (6) of the double-controller, and the planet carrier is used as the left outer output end (7) and is used as the right outer output end (8).

The clutch is a transmission device which synthesizes and converts two rotating speeds with opposite rotating directions at the inner input end and the outer input end thereof into the rotating speed of the planet gear thereof, and converts two rotating speeds with the same rotating direction at the inner input end and the outer input end thereof into the rotating speed of the planet carrier thereof. The method comprises the following steps that a single-layer planet row is adopted, the number of wheel sets of planet wheels ranges from one set to six sets, the planet row shaft is a clutch shaft, a left central wheel is used as an external input end of the clutch, a right central wheel is used as an internal input end of the clutch, a planet carrier is used as a turnover control end, one to six planet wheels are used as output ends, an output shaft is the planet wheel shafts, and the output shaft and the clutch shaft form a folding angle; the output end is also the output end of the equidirectional split double-control hundred-direction driver. The clutch of the embodiment adopts a bevel gear single-layer star planet row, a left central wheel is used as an external input end (10) of the clutch, a right central wheel is used as an internal input end (9) of the clutch, a planet carrier is used as a turnover control end (11), a bevel gear planet wheel is used as an output end (12), an output shaft is a shaft of the bevel gear planet wheel, and the output shaft and the clutch shaft form a 90-degree folding angle; the number of the wheel sets of the bevel gear planet wheels in the planet row is two.

The method for setting the components in the equidirectional transfer case, the double-controller and the clutch in the embodiment comprises the following steps: the homodromous transfer case adopts a double-sun-wheel planet row to enable the characteristic parameter of the double-sun-wheel planet row to be equal to 2.0, the characteristic parameter of the double-controller double-sun-wheel planet row to be equal to 2.0, and the characteristic parameter of the clutch bevel gear single-layer planet row to be equal to 1.0. The number of teeth of each part is set as: taking the left sun gear of the double sun gear planet row of the homodromous transfer case as 36 in number, the left planet gear as 18 in number, the right planet gear as 18 in number and the right sun gear as 18 in number; the number of left-side sun gears of the double-controller double-sun-gear planet row is 36, the number of left-side planet gears is 18, the number of right-side planet gears is 18, and the number of right-side sun gears is 18; and the tooth number of a left central gear of the clutch bevel gear single-layer planet row is equal to the tooth number of a right central gear, which is equal to the tooth number of a bevel gear planet gear, which is equal to 18.

In the embodiment, a sleeve shaft commutator is adopted, and a first connection method is adopted: the inner output end (2) of the equidirectional transfer case is directly connected with the inner input end of a sleeve shaft commutator, the outer output end (3) of the equidirectional transfer case is directly connected with the outer input end of the sleeve shaft commutator, the inner output end of the sleeve shaft commutator is directly connected with the left inner output end (6) of a dual-controller, the outer output end of the sleeve shaft commutator is directly connected with the left outer output end (7) of the dual-controller, the right inner output end (6) of the dual-controller is directly connected with the inner input end (9) of a combiner, and the right outer output end (8) of the dual-controller is directly connected with the outer input end (10) of the combiner; the input end (1) of the equidirectional transfer case is connected with a power source, the input end (5) of the double-control device is indirectly connected with the double-control device through the double-control gear (13) and the paraxial gear (14), the turnover control end (11) is connected with the turnover control device, and the output end (12) of the clutch is connected with the power using device.

The power rotating speed input from a power source is converted into the rotating speed of the output end of the clutch through the transmission of the embodiment, the input and output of the power rotating speed are not interfered with the revolving rotating speed, and the input and output of the power rotating speed are not interfered with the double-control rotating speed; the embodiment controls the revolution of the output shaft around the clutch shaft by inputting one of the revolution speed and the double-control revolution speed. The input and output of the power rotating speed are not interfered with the revolving rotating speed and the double-control rotating speed, the forward rotation and the reverse rotation of the revolving output shaft are controlled to be balanced, the output shaft has no unidirectional support moment, and the revolving control device and the double-control device do not need to overcome the unidirectional support moment, so the structures of the revolving control device and the double-control device are simple. In the control process, the turnover control device and the double-control device are linked, the turnover control device can passively rotate when the double-control device inputs a non-zero double-control rotating speed, and the double-control device can passively rotate when the turnover control device inputs a non-zero turnover rotating speed.

Example 2: the invention discloses a equidirectional transfer double-control hundred-direction driver adopting two sleeve shaft commutators, which consists of a equidirectional transfer case, a left sleeve shaft commutators, a double-controller, a right sleeve shaft commutators and a clutch, wherein the equidirectional transfer case adopts double-sun-wheel planet rows, the left sleeve shaft commutators and the right sleeve shaft commutators both adopt bevel gear planet row commutators, the double-controller adopts double-sun-wheel planet rows, and the clutch adopts bevel gear single-layer planet rows, which is shown in figure 2.

The homodromous transfer case has a homodromous transfer case input end, a homodromous transfer case internal output end, a homodromous transfer case external output end, and the homodromous transfer case makes a rotational speed of its input end convert into its internal output end, two rotational speeds that the direction of rotation of its external output end is the same. And a component corresponding to the maximum absolute value of the coefficient in the motion characteristic equation of the planetary row of the equidirectional transfer case is set as the input end of the equidirectional transfer case, and the other two components are respectively used as the inner output end of the equidirectional transfer case and the outer output end of the equidirectional transfer case. In this embodiment 2, the equidirectional transfer case adopts a double-sun-gear planetary row, a component corresponding to the maximum absolute value of the coefficient in the motion characteristic equation is a central wheel with a large pitch circle diameter, the central wheel with the large pitch circle diameter is used as an input end (1) of the equidirectional transfer case, the planet carrier is used as an internal output end (2) of the equidirectional transfer case, and the other central wheel is used as an external output end (3) of the equidirectional transfer case. The number of the planetary wheel sets in the planetary row is two.

The sleeve shaft commutator comprises an inner shaft and an outer shaft of the sleeve shaft, the inner shaft is provided with an inner input end and an inner output end, the outer shaft is provided with an outer input end and an outer output end, and the sleeve shaft commutator converts two rotating speeds with the same rotating direction of the inner input end and the outer input end thereof into two rotating speeds with opposite rotating directions of the inner output end and the outer output end thereof; and two rotating speeds with the same rotating direction of the inner output end and the outer output end are converted into two rotating speeds with opposite rotating directions of the inner input end and the outer input end. The left sleeve shaft commutator (4) and the right sleeve shaft commutator (15) of the embodiment 2 are all provided with bevel gear planet row commutators, the inner shaft of the sleeve shaft is provided with an inner input end and an inner output end, the left central wheel of a bevel gear planet row on the outer shaft of the sleeve shaft is used as the outer input end of the commutators, the right central wheel is used as the outer output end of the commutators, the bevel gear planet wheels are meshed with the left central wheel and meshed with the right central wheel, the planet carrier is fixed, and the number of the wheel sets of the bevel gear planet wheels in the two planet rows is two. The rotation direction of the external input end of the commutator is opposite to that of the external output end of the commutator. In the two sleeve shaft commutators, the left central gear tooth number equals to the right central gear tooth number equals to the bevel gear planet gear tooth number equals to 18, and the left central gear module is not equal to the right central gear module.

The double controller has one double controller input, one left inner output and right inner output, one left outer output and one right outer output, and converts the input rotation speed into two rotation speeds with the same rotation direction and the same rotation direction. The double-controller adopts a double-layer planet row, the number of the wheel sets of the planet wheels is one to six, the left central wheel is used as the input end of the double-controller, the other central wheel is used as the left inner output end and is used as the right inner output end, the planet carrier is used as the left outer output end and is used as the right outer output end, and the left central wheel is also a component corresponding to the maximum coefficient absolute value in the motion characteristic equation of the double-layer planet row. In this embodiment 2, the dual controller adopts a dual sun gear planetary row, a component corresponding to the maximum absolute value of coefficient in the motion characteristic equation is a central wheel (sun gear) with a large pitch circle diameter, the number of the wheel sets of the planetary gears is two, the central wheel with the large pitch circle diameter is used as the input end (5) of the dual controller, the other central wheel is used as the left inner output end and the right inner output end (6) of the dual controller, and the planet carrier is used as the left outer output end (7) and the right outer output end (8).

The clutch is a transmission device which synthesizes and converts two rotating speeds with opposite rotating directions at the inner input end and the outer input end thereof into the rotating speed of the planet gear thereof, and converts two rotating speeds with the same rotating direction at the inner input end and the outer input end thereof into the rotating speed of the planet carrier thereof. The method comprises the following steps that a single-layer planet row is adopted, the number of wheel sets of planet wheels ranges from one set to six sets, the planet row shaft is a clutch shaft, a left central wheel is used as an external input end of the clutch, a right central wheel is used as an internal input end of the clutch, a planet carrier is used as a turnover control end, one to six planet wheels are used as output ends, an output shaft is the planet wheel shafts, and the output shaft and the clutch shaft form a folding angle; the output end is also the output end of the equidirectional split double-control hundred-direction driver. In the embodiment 2, a clutch adopts a bevel gear single-layer star planetary row, a left central gear serves as an external input end (10) of the clutch, a right central gear serves as an internal input end (9) of the clutch, a planet carrier serves as a turnover control end (11), a bevel gear planet gear serves as an output end (12), an output shaft is a shaft of the bevel gear planet gear, and the output shaft and the clutch shaft form a 90-degree folding angle; the number of the wheel sets of the bevel gear planet wheels in the planet row is two.

In this embodiment 2, the setting method of each component in the equidirectional transfer case, the dual controller, and the clutch is as follows: the homodromous transfer case adopts a double-sun-wheel planet row to enable the characteristic parameter of the double-sun-wheel planet row to be equal to 2.0, the characteristic parameter of the double-controller double-sun-wheel planet row to be equal to 2.0, and the characteristic parameter of the clutch bevel gear single-layer planet row to be equal to 1.0. The number of teeth of each part is set as: taking the left sun gear of the double sun gear planet row of the homodromous transfer case as 36 in number, the left planet gear as 18 in number, the right planet gear as 18 in number and the right sun gear as 18 in number; the number of left-side sun gears of the double-controller double-sun-gear planet row is 36, the number of left-side planet gears is 18, the number of right-side planet gears is 18, and the number of right-side sun gears is 18; and the tooth number of a left central gear of the clutch bevel gear single-layer planet row is equal to the tooth number of a right central gear, which is equal to the tooth number of a bevel gear planet gear, which is equal to 18.

In this embodiment 2, two sleeve shaft commutators are adopted, and the connection method two is adopted: an inner output end (2) of the homodromous transfer case is directly connected with an inner input end of the left sleeve shaft commutator, an outer output end of the homodromous transfer case is directly connected with an outer input end of the left sleeve shaft commutator, an inner output end of the left sleeve shaft commutator is directly connected with a left inner output end (6) of the dual-controller, an outer output end of the left sleeve shaft commutator is directly connected with a left outer output end (7) of the dual-controller, a right inner output end (6) of the dual-controller is directly connected with an inner input end of the right sleeve shaft commutator, a right outer output end (8) of the dual-controller is directly connected with an outer input end of the right sleeve shaft commutator, an inner output end of the right sleeve shaft commutator is directly connected with an inner input end (9) of the dual-controller, and an; the input end (5) of the double-controller is indirectly connected with a power source through a double-control gear (13) and a paraxial gear (14), the input end (1) of the equidirectional transfer case is connected with a double-control device, the turnover control end (11) is connected with a turnover control device, and the output end (12) of the clutch is connected with a power using device.

In the embodiment 2, the power rotating speed input from the power source is converted into the rotating speed at the output end of the clutch through the transmission of the embodiment, the input and output of the power rotating speed are not interfered with the revolving rotating speed, and the input and output of the power rotating speed are not interfered with the double-control rotating speed; in the embodiment 2, the revolution of the output shaft around the clutch shaft is controlled by inputting one of the revolution speed and the double-control revolution speed. The input and output of the power rotating speed are not interfered with the revolving rotating speed and the double-control rotating speed, the forward rotation and the reverse rotation of the revolving output shaft are controlled to be balanced, the output shaft has no unidirectional support moment, and the revolving control device and the double-control device do not need to overcome the unidirectional support moment, so the structures of the revolving control device and the double-control device are simple. In the control process, the turnover control device and the double-control device are linked, the turnover control device can passively rotate when the double-control device inputs a non-zero double-control rotating speed, and the double-control device can passively rotate when the turnover control device inputs a non-zero turnover rotating speed.

The foregoing illustrates and describes the principles, general features, and advantages of the present invention. It will be understood by those skilled in the art that the present invention is not limited to the embodiments described above, and that various changes and modifications may be made without departing from the spirit and scope of the invention as defined in the appended claims. The scope of the invention is defined by the appended claims and equivalents.

Claims

1. The equidirectional transfer double-control one-hundred-direction driver consists of an equidirectional transfer case, a sleeve shaft reverser, a double-controller and a clutch; the homodromous transfer case is provided with a homodromous transfer case input end, a homodromous transfer case internal output end and a homodromous transfer case external output end, the homodromous transfer case converts a rotating speed of the input end into two rotating speeds with the same rotating direction of the internal output end and the external output end, the homodromous transfer case adopts a planet row, a component corresponding to the maximum absolute value of a coefficient in a motion characteristic equation of the component is set as the homodromous transfer case input end, other two components are respectively used as the homodromous transfer case internal output end and the homodromous transfer case external output end, and the homodromous transfer case planet row adopts one of five planet rows;

the five planetary rows are respectively as follows:

the component corresponding to the maximum absolute value of the coefficient in the motion characteristic equation of the bevel gear single-layer star planet row is a planet carrier, the planet carrier of the bevel gear single-layer star planet row is used as the input end of the homodromous transfer case, the left central wheel is used as the inner output end of the homodromous transfer case, and the right central wheel is used as the outer output end of the homodromous transfer case;

the planet carrier of the planet row with the double sun wheels and the double planet wheel shafts is used as the input end of the equidirectional transfer case, the left central wheel is used as the inner output end of the equidirectional transfer case, and the right central wheel is used as the outer output end of the equidirectional transfer case;

the part corresponding to the maximum absolute value of the coefficient in the motion characteristic equation of the double-layer planetary row of the cylindrical gear is a central wheel with a large pitch circle diameter, an inner gear ring of the double-layer planetary row of the cylindrical gear is used as the input end of the equidirectional transfer case, a planet carrier is used as the inner output end of the equidirectional transfer case, and a sun gear is used as the outer output end of the equidirectional transfer case;

the double-sun-wheel planet row is characterized in that parts corresponding to the maximum absolute coefficient value in a motion characteristic equation are two central wheels, the central wheel with the larger pitch circle diameter of the double-sun-wheel planet row is used as the input end of the homodromous transfer case, the planet carrier is used as the inner output end of the homodromous transfer case, and the other central wheel is used as the outer output end of the homodromous transfer case;

the double-inner-gear-ring planet row is characterized in that parts corresponding to the maximum absolute coefficient value in a motion characteristic equation are two central wheels, the central wheel with the smaller pitch circle diameter of the double-inner-gear-ring planet row is used as the input end of the homodromous transfer case, the planet carrier is used as the inner output end of the homodromous transfer case, and the other central wheel is used as the outer output end of the homodromous transfer case;

the sleeve shaft commutator comprises an inner shaft and an outer shaft of the sleeve shaft, the inner shaft is provided with an inner input end and an inner output end, the outer shaft is provided with an outer input end and an outer output end, the sleeve shaft commutator converts two rotating speeds with the same rotating direction of the inner input end and the outer input end thereof into two rotating speeds with opposite rotating directions of the inner output end and the outer output end thereof, and also converts two rotating speeds with the same rotating direction of the inner output end and the outer output end thereof into two rotating speeds with opposite rotating directions of the inner input end and the outer input end thereof, the homodromous double-control transmission one or two sleeve shaft commutators are adopted, the sleeve shaft commutators are of four types, one of the four types is selected as the sleeve shaft commutator, the transmission ratio of the inner shafts of the bevel gear planet row commutators and the double sun gear double planet gear planet shaft planet row commutators is set to be 1.0, the transmission ratio of the outer shaft is set to be-1.0, and, The transmission ratio from the external input end to the external output end is set to be 1.0, the transmission ratio from the internal input end to the external output end of the transposition double-way commutator is set to be-1.0, and the transmission ratio from the external input end to the internal output end is set to be 1.0; the sleeve shaft commutator adopts a bevel gear planet row commutator, the outer shaft adopts a bevel gear single-layer planet row, the inner shaft of the sleeve shaft is provided with an inner input end and an inner output end, a left central wheel of the bevel gear single-layer planet row on the outer shaft of the sleeve shaft is used as the outer input end of the commutator, a right central wheel is used as the outer output end of the commutator, the bevel gear planet wheel is meshed with the left central wheel and meshed with the right central wheel, so that the planet carrier is fixed, and the rotating directions of the outer input end of the commutator and the outer output end of the commutator are opposite;

the double controller has a double controller input end, a left inner output end and a right inner output end, a left outer output end, a right outer output end, the double controller converts a rotating speed input by the input end into two rotating speeds with the same rotating direction of the left inner output end and the left outer output end, and simultaneously converts the rotating speed into two rotating speeds with the same rotating direction of the right inner output end and the right outer output end, the double controller adopts a double-layer star planet row, a left central wheel is used as the input end of the double controller, the other central wheel is used as the left inner output end and the right inner output end, a planet carrier is used as the left outer output end and the right outer output end, the left central wheel is also a component corresponding to the maximum coefficient absolute value in the double controller planet row motion characteristic equation, and the double controller adopts one of three double-layer planet rows;

the three double-layer planet rows are respectively as follows:

the cylindrical gear double-layer star planet row is characterized in that a part corresponding to the maximum coefficient absolute value term in the motion characteristic equation is a central wheel with a large pitch circle diameter, namely an inner gear ring; a central wheel with a large pitch circle diameter, namely an inner gear ring, is used as an input end of a dual-controller, the other central wheel, namely a sun wheel, is used as a left inner output end and a right inner output end, and a planet carrier is used as a left outer output end and a right outer output end;

the planet row with double sun gears has the components corresponding to the maximum absolute coefficient value in the motion characteristic equation, namely two central gears, namely the larger diameter of the pitch circle in the sun gear; a central wheel with a larger pitch circle diameter is used as an input end of the double-controller, the other central wheel is used as a left inner output end and a right inner output end, and the planet carrier is used as a left outer output end and a right outer output end;

the parts corresponding to the maximum absolute value of the coefficient in the motion characteristic equation of the double-inner-gear-ring planet row are two central wheels, namely the part with the smaller diameter of the pitch circle in the inner gear ring; a central wheel with a smaller pitch circle diameter is used as an input end of the double-controller, the other central wheel is used as a left inner output end and a right inner output end, and the planet carrier is used as a left outer output end and a right outer output end;

the clutch is a transmission device which synthesizes and converts two rotating speeds with opposite rotating directions of an inner input end and an outer input end thereof into the rotating speed of a planet wheel of the clutch, converts the rotating speeds with the same rotating directions of the inner input end and the outer input end thereof into the rotating speed of a planet carrier of the clutch, adopts a single-layer planet row, the planet row shaft of the clutch is the clutch shaft, the left central wheel is used as the outer input end of the clutch, the right central wheel is used as the inner input end of the clutch, the planet carrier is used as a turnover control end, one to six planet wheels are used as output ends, the output shafts are the planet wheel shafts, the output shafts and the clutch shaft form a folding angle, the output end of the clutch is also the output end of a homodromous double-control one;

the two single-layer star planet rows are respectively as follows:

a bevel gear single-layer star planet row; the left central wheel is used as an external input end of the clutch, the right central wheel is used as an internal input end of the clutch, the planet carrier is used as a turnover control end, one or more bevel gear planet wheels are used as output ends, the output shafts are the shafts of the bevel gear planet wheels, and the output shafts and the clutch shafts form a 90-degree folding angle;

a double sun wheel and double planet wheel shaft planet row; the left central wheel is used as an external input end of the clutch, the right central wheel is used as an internal input end of the clutch, the planet carrier is used as a turnover control end, one to six planet wheels are used as output ends, the output shafts are the axes of the planet wheels, and the output shafts are parallel to the axis of the clutch and form a 0-degree folding angle;

the setting method of each component of the equidirectional transfer case, the double-controller and the clutch in the equidirectional transfer double-control hundred-direction driver is as follows: setting characteristic parameters of a homodromous transfer case to be equal to 1.0 when a single-layer star planet row is adopted by the homodromous transfer case, setting characteristic parameters of a double-controller double-layer star planet row to be equal to 2.0 when a double-layer star row is adopted by the homodromous transfer case, and setting characteristic parameters of a single-layer star planet row of a clutch to be equal to 1.0; when a sleeve shaft commutator is adopted, the first connecting method of the equidirectional transfer double-control hundred-direction driver is as follows: the internal output end of a homodromous transfer case is directly connected with the internal input end of a sleeve shaft commutator, the external output end of the homodromous transfer case is directly connected with the external input end of the sleeve shaft commutator, the internal output end of the sleeve shaft commutator is directly connected with the left internal output end of a dual-controller, the external output end of the sleeve shaft commutator is directly connected with the left external output end of the dual-controller, the right internal output end of the dual-controller is directly connected with the internal input end of a clutch, the right external output end of the dual-controller is directly connected with the external input end of the clutch, the input end of the homodromous transfer case is connected with a power source, the input end of the dual-controller is indirectly connected with a dual-control device through a dual-control gear and a side shaft gear, the epicyclic control end is connected with; the second connection method comprises the following steps: the inner output end of the homodromous transfer case is directly connected with the inner input end of the left sleeve shaft commutator, the outer output end of the homodromous transfer case is directly connected with the outer input end of the left sleeve shaft commutator, the inner output end of the left sleeve shaft commutator is directly connected with the left inner output end of the dual-controller, the outer output end of the left sleeve shaft commutator is directly connected with the left outer output end of the dual-controller, the right inner output end of the dual-controller is directly connected with the inner input end of the right sleeve shaft commutator, the right outer output end of the dual-controller is directly connected with the outer input end of the right sleeve shaft commutator, the inner output end of the right sleeve shaft commutator is directly connected with the inner input end of the clutch, the outer output end of the right sleeve shaft commutator is directly, the paraxial gear is indirectly connected with a power source, the input end of the equidirectional transfer case is connected with the double-control device, the turnover control end is connected with the turnover control device, and the output end of the clutch is connected with the power using device; the equidirectional transfer double-control one-hundred-direction driver converts the power rotating speed input by the power source into the rotating speed of the output end of the clutch, and the input and output of the power rotating speed are not interfered with the revolving rotating speed and the double-control rotating speed; the same-direction transfer double-control one-hundred-direction driver controls the output shaft to rotate around the clutch shaft by inputting one of the rotating speed and the double-control rotating speed, controls the forward rotation and the reverse rotation torque of the output shaft to be balanced, has no unidirectional support torque, and has simple structures because the rotating control device and the double-control device do not need to overcome the unidirectional support torque.

2. The co-rotating dual-control hundred-direction driver as claimed in claim 1, wherein the sleeve shaft reverser is a double-sun-wheel double-planet-wheel-shaft planet row reverser, the outer shaft is a double-sun-wheel double-planet-wheel-shaft planet row reverser, the inner shaft of the sleeve shaft is provided with an inner input end and an outer output end, the left central wheel of the double-sun-wheel double-planet-shaft planet row on the outer shaft of the sleeve shaft is used as the outer input end of the reverser, the right central wheel is used as the outer output end of the reverser, the planet carrier is fixed, and the rotation direction of the outer input end of the reverser is opposite to that of the.

3. The co-rotating double-control hundred-direction transmission as claimed in claim 1, wherein the sleeve shaft reverser adopts a position-retaining two-way reverser, the inner shaft and the outer shaft respectively adopt bevel gear pair transmission, the inner input end and the outer input end of the position-retaining two-way reverser form an input sleeve shaft, the inner output end and the outer output end form an output sleeve shaft, the input sleeve shaft bearing and the output sleeve shaft bearing are respectively fixed, and the input sleeve shaft and the output sleeve shaft form a 90-degree included angle, an inner driving bevel gear is arranged on the inner input end, an outer driving bevel gear is arranged on the outer input end, an inner driven bevel gear is arranged on the inner output end, an outer driven bevel gear is arranged on the outer output end, the inner driving bevel gear is meshed with the inner driven bevel gear, the outer driving bevel gear is meshed with the outer driven bevel gear, two rotating speeds with the same rotating direction are input to the inner input end and the outer input end, and two rotating speeds with opposite rotating directions are output to the inner output end and the outer output end.

4. The unidirectional transfer double-control hundred-direction driver as claimed in claim 1, wherein the sleeve shaft reverser adopts a transposition two-way reverser, the inner shaft and the outer shaft respectively adopt bevel gear pair transmission, the inner input end and the outer input end of the transposition two-way reverser form an input sleeve shaft, the inner output end and the outer output end form an output sleeve shaft, the input sleeve shaft and the output sleeve shaft form a 90-degree included angle, the inner input end is provided with an inner driving bevel gear, the outer input end is provided with an outer driving bevel gear, the inner output end is provided with an inner driven bevel gear, the outer output end is provided with an outer driven bevel gear, the inner driving bevel gear is meshed with the outer driven bevel gear, the outer driving bevel gear is meshed with the inner driven bevel gear, the inner input end and the outer input end input two rotating speeds with the same rotating direction, and the outer output end and the inner output end output ends output two rotating speeds with opposite rotating directions.