CN110541920A

CN110541920A - Reverse transfer differential driver

Info

Publication number: CN110541920A
Application number: CN201810520464.3A
Authority: CN
Inventors: 罗灿
Original assignee: Individual
Current assignee: Individual
Priority date: 2018-05-28
Filing date: 2018-05-28
Publication date: 2019-12-06

Abstract

The invention relates to a reverse transfer differential driver, which consists of a reverse transfer case, a one-way speed changer and a homodromous clutch, has a specific connection mode and a transmission path, is a planet row composite structure, and is a two-degree-of-freedom determining system. The reverse transfer case planetary row meets the first condition of the present invention, the same-direction clutch planetary row meets the second condition of the present invention, and the one-way transmission gear ratio can be (1+ k)/k or k/(1+ k) if necessary, so that NB 2-NC 2 (1+ k) NB1-k NC 1. The invention has five application modes according to different operations and different connections between the output end and the application end. The first application mode and the second application mode can be used for transmission of coaxial reverse double rotors or coaxial reverse double rotors, the third application mode and the fourth application mode can be used as double-flow variable speed transmissions for driving wheels of motor vehicles such as tracked vehicles, and the fifth application mode can be used as variable damping differentials.

Description

Reverse transfer differential driver

Technical Field

The invention relates to a planetary row composite structure transmission machine, in particular to a differential transmission machine which is composed of a reverse transfer case, a one-way speed changer and a same-direction clutch and can output two rotating speeds which are coaxially and simultaneously rotated or coaxially and reversely rotated and control the differential between the absolute values of the two rotating speeds.

Background

The traditional crown differential and the planet row differential are easy to have insufficient total torque in differential operation. The traditional limited slip differential has better performance but complex structure. The differential damping value or the limited slip moment of the traditional differential gear during differential transmission is preset and cannot be adjusted, and differential transmission with the required differential damping value is difficult to realize.

The invention provides a novel differential driver which can output two rotating speeds which are coaxially co-rotating or coaxially counter-rotating and can control the differential between the absolute values of the two rotating speeds. The planetary row compound structure transmission machine can be used as a variable damping differential mechanism. The transmission mechanism with the structure can also be used as a double-flow variable speed transmission and can be used for coaxial reverse rotation double-rotor transmission.

Disclosure of Invention

The invention relates to a novel differential driver which outputs two rotating speeds which are coaxially co-rotating or coaxially counter-rotating and can control the differential speed between the absolute values of the two rotating speeds. The transmission is composed of a reverse transfer case, a one-way speed changer and a same-direction clutch.

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

The reverse transfer case is in a single-row planet row structure, and the planet row is characterized in that the form of a motion characteristic equation after finishing deformation meets the condition I: the inverse transfer case equation of motion NA1 ═ 1+ k × NB1-k × NC1, k > 1.0. The planet row of the reverse transfer case can be a variable linear speed single-layer planet row, a variable linear speed double-layer planet row, a common cylindrical gear single-layer planet row, a common cylindrical gear double-layer planet row, a bevel gear single-layer planet row or a bevel gear double-layer planet row, and the variable linear speed double-layer planet row and the common cylindrical gear single-layer planet row are 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 schematic structural diagram of the variable linear speed double-layer planetary row with the structure form six can be seen in fig. 1, and the planetary row composed of the components 1, 2 and 3 in fig. 1 is the structure form six of the variable linear speed double-layer planetary row with only one layer of planet wheels, which is simpler. Referring to fig. 2, a schematic structural diagram of a single-layer star planet row of a common cylindrical gear is shown, and a planet row formed by components 1, 2 and 3 in fig. 2 is the single-layer star planet row of the common cylindrical gear. The three components of the reverse transfer case planetary row are A1, B1 and C1 respectively, and the rotating speeds of the three components are NA1, NB1 and NC1 respectively. The rotational speed input value of NA1 is determined by taking the component a1 corresponding to the rotational speed NA1 as the input of the reverse transfer case, which is also the input of the entire reverse transfer differential 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 two connections are coaxial, one directly inside the coaxial and the other indirectly outside the coaxial, which contains a one-way speed changer.

The one-way speed changer is used in one of two connections between the power dividing end of the reverse power divider and the input end of the homodromous power combiner, and can convert two rotating speeds with unequal absolute values of the two power dividing ends into two rotating speeds with equal absolute values of the two input ends. The single-way speed changer is indirectly connected with a single-way connection, and is used for the indirect connection between the two connections and the coaxial outer side, when a transmission ratio value of (1+ k)/k is set for the indirect connection between the C1 and the C2, the NB2 is-NC 2, (1+ k) NB1 is-k NC 1. 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 element 4 in fig. 1 is a part of a one-way transmission, which can be understood as a single-shaft spur gear in the form of a parallel-shaft single-shaft spur gear, to which a spur gear (half-shaft in the figure) is connected being provided at the transfer end C1 of the reverse transfer case and a spur gear (half-shaft in the figure) being provided at the input end C2 of the co-rotating case, which may have different modules. The single-shaft cylindrical gear 4 (a whole gear in the figure) fixed by the bracket fixed bearing is provided with two sets of gears, the modulus of the two sets of gears can be different, the angular speed and the linear speed of the two sets of gears can be different, the two sets of gears are respectively meshed with the cylindrical gear arranged at the transfer end and the cylindrical gear arranged at the input end, the conversion of the rotating speed of the two transfer ends to the rotating speed of the two input ends is realized, and the indirectly connected transmission ratio can be (1+ k)/k or k/(1+ k) when necessary, so that NB2 is-NC 2, (1+ k) NB1 is-k NC 1. The single-way transmission in fig. 1 can also be understood as a variable-linear-speed double-layer planetary row in the schematic diagram of the half-width structural diagram of the planetary row, in which a cylindrical gear connected to the transfer end and a cylindrical gear connected to the input end (two central wheels as the variable-linear-speed double-layer planetary row of the single-way transmission) are also provided, a variable-linear-speed double-layer planetary wheel 4 with a fixed planetary carrier is provided, the entire variable-linear-speed planetary row converts the rotational speeds of the two transfer ends into the rotational speeds of the two input ends, and the indirect connection transmission ratio can be (1+ k)/k or k/(1+ k) as necessary so that (1+ k) ═ NB1-k ═ NC1 when NB2 is — NC 2.

The syntropy clutch is a single-row planet row structure, and the planet row is characterized in that the form of a motion characteristic equation after finishing deformation meets the second condition: the homodromous clutch motion equation NA2 is 0.5 NB2+0.5 NC2, the central wheel A2 corresponding to the NA2 serves as an epicyclic control end, and the B2 and the C2 are input ends of the homodromous clutch and output ends of the reverse transfer differential transmission. 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 or a common cylindrical gear double-layer planet row. The motion characteristic equation Nt2-a Nq2- (1-a) Nj 2-0 can be arranged and deformed into Nt 2-0.5 Nq2+0.5 Nj2 when a is 0.5, and t2 corresponding to Nt2 is used as a turnover control end, B2 and C2 are input ends of a homodromous clutch and output ends of a reverse transfer differential transmission, and the condition two is met; when a is 2.0, the transformation can be adjusted to Nq2 being 0.5 Nt2+0.5 Nj2, and q2 corresponding to Nq2 is used as a turnover control end, B2 and C2 are input ends of a homodromous clutch and output ends of a reverse transfer differential driver, and the condition two is met. The component A2 corresponding to the NA2 is used as a turnover control end, the turnover control end is also used as a turnover control end of the whole reverse transfer differential transmission, and the input value of the rotating speed NA2 of the turnover control end can be determined. Two components B2 and C2 corresponding to NB2 and NC2 are used as two input ends of a homodromous clutch and two output ends at the same time, are used as input ends and connected with a transfer end of a reverse transfer case, and are used as output ends to output two rotating speeds outwards. The B2 and the C2 are also two output ends of the reverse transfer differential transmission at the same time, and can be externally connected and output two coaxial same-rotation rotating speeds with the same rotating direction or two coaxial reverse rotating speeds with 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 adopted by the homodromous clutch, an external gear ring is arranged on the revolution control end 4, and a paraxial gear 7 meshed with the external gear ring can input the rotating speed NA2 to the revolution control end. The components shown in 4, 5 and 6 in fig. 2 form a common cylindrical gear double-layer star planetary row adopted by the homodromous clutch.

The reverse transfer differential transmission comprises a reverse transfer case, a one-way speed changer and a homodromous clutch, is a planetary row composite structure, is a two-degree-of-freedom determining system, and when the rotating speeds NA1 and NA2 of two rotating members, namely a reverse transfer case input end A1 and a homodromous clutch circulation control end A2, the rotating speeds of all the rotating members in the system are determined, and the rotating speeds NB2 and NC2 of two output ends B2 and C2 are also determined. When one of NA1 and NA2 determines, and the differential in absolute values of the rotational speeds of the two outputs also determines, the rotational speeds of all the rotating members in the system are also determined. The motion equations of the reverse transfer case planet row and the motion equations of the homodromous clutch planet row can form an equation set, and the rotation speed of each rotating member in the reverse transfer case differential transmission can be obtained by solving the equation set under the conditions of the determined values of the rotation speed NA1 and the rotation speed NA2 and the connection conditions, wherein the rotation speed comprises the rotation speeds of two output ends.

Since NB2 rotates in the opposite direction from NC2 and the negative sign indicates the opposite direction of rotation of the two speeds, the equation of the motion characteristic of the same directional clutch can be expressed as | NA2| -0.5 | -NB 2| -0.5 | -NC 2|, i.e., the equation between the absolute values of the three speeds.

The input end and the turnover control end of the reverse transfer differential driver are controlled in various modes, and the output end is connected to the application end in various modes. The present invention has five application modes according to different operations and different connections between the output end and the application end.

In the first application, the absolute value of NA1 is made larger and the absolute value of NA2 is made smaller, and these two determined degrees of freedom determine the rotational speed of each rotating member in the system. Two coaxial reverse rotating speeds are formed through transmission of the input NA1 through the reverse transfer differential driver, and the differential speed between two absolute values of the rotating speeds is actively adjusted through the input NA 2. And controlling the torque imbalance of forward rotation and reverse rotation of the turnover control end. The epicyclic control terminal a2 is controlled so that NA2 is 0, then | NB2| -NC 2|, and the differential speed is zero. By controlling the value of NA2 to be positive or negative, the differential speed can be controlled to be positive or negative. In the application mode, the reverse transfer differential driver can be used for transmission of coaxial reverse double rotors or coaxial reverse double propellers, the double rotors or the double propellers are used as application ends and connected with two output ends of the reverse transfer differential driver, and two rotating speeds of the coaxial reverse adjustable differential can be transmitted to the application ends from the output ends and still are two rotating speeds of the coaxial reverse from the output ends to drive the coaxial reverse double rotors or the double propellers. The two connections of the output to the application terminal are typically two direct connections, see fig. 1. Two indirect connections can also be used if desired, and can be seen in fig. 5. In fig. 5, the two rotational speeds of coaxial reversal from the output 1, 2 of the co-rotating clutch are transmitted to the application 3, 4, or to the two rotational speeds of coaxial reversal. The speed of rotation is directed to be suitable for connecting the coaxial contra-rotating twin rotors. Coaxial inversion is also referred to as coaxial inversion. In this application, the one-way speed changer can be omitted, and this indirect connection between the reverse transfer case and the co-rotating clutch is changed into a direct connection. Other control modes are unchanged, and the connection between the output end and the application end is unchanged.

In the second application, the absolute value of NA2 is made larger and the absolute value of NA1 is made smaller, and these two determined degrees of freedom determine the rotational speed of each rotating member in the system. The input NA2 is transmitted by a reverse transfer differential driver to form two rotating speeds which rotate coaxially and simultaneously, the differential speed between absolute values of the two rotating speeds is actively adjusted through the input NA1, the balance between the forward torque and the reverse torque during the differential speed is adjusted, and the differential speed can be adjusted by adjusting the rotating speed NA1 of the input end with small torque. Control a1 sets NA1 to 0, and | NB2| ═ NC2|, the differential speed is zero. By controlling the value of NA1 to be positive or negative, the differential speed can be controlled to be positive or negative. In the application mode, the reverse transfer differential driver can also be used for the transmission of coaxial reverse double rotors or coaxial reverse double propellers, the double rotors or the double propellers are used as application ends and connected with the output end of the invention, and the two rotating speeds of coaxial and same rotation are transmitted from the output end to the application ends to form two rotating speeds of coaxial and reverse rotation to drive the coaxial reverse double rotors or the double propellers. The two connections from the output to the application end are typically a direct connection and an indirect connection with a transmission ratio of-1.0, such as an indirect connection with a one-way commutator, see fig. 3. The speed of rotation is directed to be suitable for connecting the coaxial contra-rotating twin rotors. If desired, two indirect connections can be used, as shown in fig. 7 and 8. In the figures 7 and 8, two coaxial rotating speeds from the output ends 1 and 2 of the co-rotating clutch are transmitted to the application ends 3 and 4 and are converted into two coaxial rotating speeds. The reverse use of the transmission mechanism in fig. 7 and 8 can also convert two rotating speeds of coaxial and same rotation into two rotating speeds of coaxial and reverse rotation.

In the traditional coaxial reverse rotation double-rotor or double-rotor transmission, the rotating directions of the double rotors are opposite, and the absolute values of the rotating speeds are the same and are not adjustable. In the two application modes, the rotation directions of the double rotors are opposite in the transmission of the end coaxial reverse double rotors, and the differential speed between the absolute values of the rotation speeds of the two rotors can be adjusted without being zero, so that the control method of the transmission of the coaxial reverse double rotors is increased, and the performance of the coaxial reverse double rotors is improved.

And in the third application mode, the reverse transfer differential driver can be used as a double-flow variable speed driver for driving two driving wheels of a tracked vehicle or a multi-wheel special vehicle. Two driving wheels of the vehicle are used as application ends to be connected with two output ends of the invention. Two connections from the output to the application end, typically two indirect connections, can be seen in fig. 6. In fig. 6, two coaxially-reversed rotating speeds from the output ends 1 and 2 of the co-rotating clutch are transmitted to the application ends 3 and 4 and are converted into two coaxially-rotated rotating speeds, and the rotating speeds are oriented to be suitable for being connected with the two driving wheels. The input NA1 enables the two drive wheels to rotate in the same direction, and the vehicle to move forward or backward; the input NA2 can enable the two driving wheels to rotate reversely, and the vehicle turns in situ; meanwhile, the NA1 and the NA2 are input, the two driving wheels rotate in the same direction and rotate at a different speed, and the vehicle turns during running. It should be noted that during the input of NA1, the torque of the forward input is balanced with the torque of the reverse input. During the input of NA2, the torque of the forward input is unbalanced with the torque of the reverse input.

In the fourth application mode, the reverse transfer differential driver has another application mode which can be used as a double-flow variable speed driver for two driving wheels of a crawler vehicle or a multi-wheel special vehicle. Two driving wheels of the vehicle are used as application ends to be connected with the output end of the invention. The two connections from the output end to the application end generally adopt two indirect connections, which can be seen in fig. 9 and 10, wherein two rotating speeds coaxially and synchronously from the output ends 1 and 2 are transmitted to the application ends 3 and 4 or are coaxially and synchronously transmitted, and the rotating speeds are oriented to be suitable for connecting the two driving wheels. The input NA2 enables the two drive wheels to rotate in the same direction, and the vehicle to move forward or backward; the input NA1 can enable the two driving wheels to rotate reversely, and the vehicle turns in situ; meanwhile, the NA2 and the NA1 are input, the two driving wheels rotate in the same direction and rotate at a different speed, and the vehicle turns during running. It should be noted that during the input of NA1, the torque of the forward input is balanced with the torque of the reverse input. During the input of NA2, the torque of the forward input is unbalanced with the torque of the reverse input.

The double-flow speed change driver is also called a double-flow wave box, is a transmission system formed by two mature planet rows and other machines at present, is used for the same-speed transmission control and differential control of the driving wheels of a tracked vehicle or a special multi-wheel vehicle, the rotating speed input by the same-speed same-rotation input end of the transmission system finally enables the two driving wheels to rotate in the same direction, and the rotating speed input by the differential reverse input end of the transmission system finally enables the two driving wheels to rotate in the reverse direction. The reverse transfer differential driver combines two different output ends and an application end connecting structure to realize the same function as the traditional double-flow driver in two different application modes, and can also be used for the same-speed transmission control and differential control of a driving wheel of a tracked vehicle. The two structures of the invention are relatively simple and compact as a whole, and have the defect of unbalanced torque of forward rotation and reverse rotation when the NA2 is input.

In the fifth application mode, the rotating speeds of two output ends rotating coaxially and simultaneously are formed by the transmission of the input NA2 through a reverse transfer differential driver, the differential speed between the absolute values of the rotating speeds determined by the loads at the application ends connected with the output ends, and the rotating speeds of all rotating members in the system are determined by two determined degrees of freedom, namely NA2 and the differential speed. A brake device such as a brake or an electromagnetic force damper is provided at the input terminal a 1. By varying the braking force of the braking device, the damping of the input is varied, which can affect the differential speed of the two outputs. The damping at the input end is adjusted to be used as a variable damping differential. In this application, the equidirectional, differential transmission can also be used as a variable-damping differential between two drive wheels of a motor vehicle. With reference to fig. 4, the speed NA2 is input at the central input a2 and transmitted to the two outputs 6, 7 of the reverse transfer differential transmission, which connect the two application ends 9, 10, i.e. the two driving axles of the motor vehicle. Wherein the input 1 is shown as being connected to a brake, and represents that the input is provided with a braking device such as a brake or an electromagnetic force damper. The damping of the input end can be adjusted by adjusting the braking force of the braking device, and the differential speed can be zero through thorough braking, which is equivalent to the locking of a differential lock in a differential mechanism. By braking the input completely, a new decisive degree of freedom NA1 is formed, where NA2 and NA1 determine the rotational speed of the rotating elements in the system, and NB2 is NC 2.

The fifth application mode corresponds to a variable damping differential, and when the absolute value of the rotation speed difference of the two output ends is determined by the loads at the two application ends transmitted by the two output ends as determined by NA2, the braking force of the braking device connected with the input end A1 is adjusted to adjust the damping of the differential motion of the two application ends. The braking force of the braking device can be adjusted according to an adjusting scheme, and the braking force can be related to the rotating speed of the transmission, or the differential speed of the transmission, or the torque of the transmission, or other adjusting schemes can be implemented.

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 present invention may be used in combination with other machines.

The reverse transfer differential transmission has the beneficial effects that a planet row composite structure of a two-degree-of-freedom determining system consisting of a reverse transfer case and a homodromous clutch is provided as the structure of the reverse transfer case and homodromous clutch. The reverse transfer case is characterized in that the planet row of the reverse transfer case meets the first condition of the invention, and the homodromous clutch is characterized in that the planet row of the reverse transfer case meets the second condition. Corresponding to different controls and different output ends connected with the application end, five application modes of the invention are provided.

The invention provides that as long as a structure consisting of the reverse transfer case and the same-direction clutch is adopted in the transmission machinery, the characteristics of the reverse transfer case and the same-direction clutch accord with the characteristics of the invention, and the mutual connection accords with the characteristics of the invention. Such machines, which may be used for coaxial counter-rotating twin-propeller drives, as dual-flow variable speed drives or as variable damping differentials, are intended to fall within the scope of the present invention.

Drawings

Fig. 1 is a schematic view of a reverse transfer differential transmission of the present invention, and is also a schematic view of embodiment 1 of the present invention. The reverse transfer case adopts a variable linear speed double-layer star planet row, and the syntropy clutch adopts a variable linear speed double-layer star planet row. The planetary gear train comprises an input end 1 of A1, a branch end 2 of B1, another branch end 3 of C1, a parallel-shaft single-shaft cylindrical gear 4 fixed by a bearing, an input end and an output end 5 of a planet carrier of C2, another input end and an output end 6 of a central wheel of B2, a turnover control end 7 of a central wheel of A2, an outer gear ring and a paraxial gear 8 meshed with the outer gear ring and used for inputting rotating speed NA2 to the turnover control end. Wherein the components 1, 2 and 3 form a reverse transfer case. 5. The components shown in 6 and 7 form a homodromous clutch.

Fig. 2 is another schematic view of the reverse transfer differential transmission of the present invention. The reverse transfer case adopts a common cylindrical gear single-layer star planet row, and the syntropy clutch adopts a common cylindrical gear double-layer star planet row. The input end 1 of A1, one split end 2 of B1, the other split end 3 of C1, a parallel shaft single-shaft cylindrical gear 4 fixed by a bearing, one input end and output end 5 of a C2 planet carrier, the other input end and output end 6 of a B2 central wheel, an A2 central wheel turnover control end 7 are provided with an outer gear ring, and an input paraxial gear 8 which is meshed with the outer gear ring and inputs the rotating speed NA2 to the turnover control end. Wherein the components 1, 2 and 3 form a reverse transfer case. 5. The components shown in 6 and 7 form a homodromous clutch.

FIG. 3 is a schematic view of a second application of the reverse transfer differential transmission of the present invention. The reverse transfer case adopts a variable linear speed double-layer star planet row, and the syntropy clutch adopts a variable linear speed double-layer star planet row. The indirect connection transmission ratio is-1.0 through a one-way commutator 9 between the output end and the application end, wherein the indirect connection transmission ratio is-1.0 through an input end 1 of A1, one split end 2 of B1, the other split end 3 of C1, a parallel-shaft single-shaft cylindrical gear type single-way speed changer 4, an output end 5 of a planet carrier of C2, an output end 6 of a central wheel of B2, an turnover control end 7 of a central wheel of A2, a paraxial gear 8 for inputting the rotating speed to the turnover control end. Wherein the components 1, 2 and 3 form a reverse transfer case. 5. The components shown in 6 and 7 form a homodromous clutch.

FIG. 4 is a schematic view of an application mode of the reverse transfer differential transmission of the present invention, wherein the reverse transfer transmission adopts a variable linear speed double-layer planetary gear set, and the homodromous clutch adopts a variable linear speed double-layer planetary gear set. An input end 1 of A1 is connected with a braking device, one shunt end 2 of B1, the other shunt end 3 of C1, a parallel shaft single-shaft cylindrical gear 4 fixed by a bearing, an input end and an output end 5 of a C2 planet carrier, the other input end and an output end 6 of a B2 central wheel, an A2 central wheel turnover control end 7 are provided with an outer toothed ring, a paraxial gear 8 meshed with the outer toothed ring and used for inputting a rotating speed NA2 to the turnover control end, a driving wheel shaft 9 of a motor vehicle at one application end, and a driving wheel shaft 10 of the motor vehicle at the other application end.

Fig. 5 is a mechanical schematic diagram of transmission from the coaxial inversion output end to the coaxial inversion application end in the first application mode of the present invention. Output 1, another output 2, an application terminal 3, and another application terminal 4.

Fig. 6 is a mechanical schematic diagram of transmission from a coaxial inversion output end to a coaxial co-transport end in a third application mode of the invention. Output 1, another output 2, an application terminal 3, and another application terminal 4.

Fig. 7 is a mechanical schematic diagram of transmission from the coaxial co-rotating output end to the coaxial counter-rotating application end in the second application mode of the present invention. Output 1, another output 2, an application terminal 3, and another application terminal 4.

Fig. 8 is a schematic view of another transmission mechanism from the coaxial co-rotating output end to the coaxial counter-rotating application end in the second application mode of the present invention. Output 1, another output 2, an application terminal 3, and another application terminal 4.

Fig. 9 is a mechanical schematic diagram of the transmission from the coaxial co-rotating output end to the coaxial co-rotating end in the fourth application mode of the present invention. Output 1, another output 2, an application terminal 3, and another application terminal 4.

Fig. 10 is a schematic view of another transmission mechanism for transmitting from the coaxial co-rotating output end to the coaxial co-rotating end in the fourth application mode of the invention. Output 1, another output 2, an application terminal 3, and another application terminal 4.

Each planet row in each figure is represented by a half-row structure as is customary 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 embodiment 1 of the reverse transfer differential transmission of the invention is composed of a reverse transfer case, a one-way transmission and a homodromous clutch, and is shown in figure 1. The reverse transfer case adopts a variable-linear-speed double-layer star planetary row, and the motion characteristic equation can be arranged and modified into NA 1-10-NB 1-9-NC 1. Namely, the number of teeth of the central gear B1 at the transfer end of the variable-line-speed planetary row is 20, the number of teeth of the gear at one side of two sets of gears of the variable-line-speed planetary row, which is the same as the linear speed of the two sets of gears, is 20, the number of teeth of the central 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 row, which is the same as the linear speed of the two sets of gears of the variable-line-. 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.

A single-way speed changer of the transmission adopts a parallel shaft single-shaft cylindrical gear form, the number of cylindrical gears arranged at a transfer end C1 is 18, the number of cylindrical gears arranged at an input end C2 is 20, and the two cylindrical gears have different modules. In two sets of gears with different modules of the single-shaft cylindrical gear fixed by the bearing, the number of teeth of the gear meshed with C1 on one side and the number of teeth of the gear meshed with C2 on the other side are both 20, and the two gears have different modules. The single-way speed changer indirect connection has a gear ratio of 10/9 and is used for indirect connection between C1 and C2.

The homodromous clutch adopts a variable linear speed double-layer star planetary row, and the motion characteristic equation of the homodromous clutch is Nt2 ═ 0.5 Nq2+ (1-0.5) × Nj 2. The gear tooth number of a central gear j2 at the epicyclic control end is 40, the gear tooth number of one side of two sets of gears of the variable-linear-speed planetary gear, which has the same linear speed as the central gear, is 20, the gear tooth number of the central gear q2, which is taken as the input end of a homodromous clutch (simultaneously, the output end of a reverse transfer differential driver), is 30, the gear tooth number of the other side of the two sets of gears of the variable-linear-speed planetary gear, which has the same linear speed as the central gear, is 30, and a planet carrier j2, which is taken as the input end of the other homodromous clutch (simultaneously. 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 a is 0.5.

The transfer end B1 of the reverse transfer case is directly connected with the input end B2 of the hundred-direction transfer case, and NB1 is NB 2. The other transfer end C1 of the reverse transfer case is indirectly connected to the input C2 of the one-way transmission, and NC1 is ((1+9)/9) × NC 2.

According to the different operations and connections between the output terminal and the application terminal, the present embodiment has five application modes.

In the second application, the absolute value of NA2 is made larger and the absolute value of NA1 is made smaller, and these two determined degrees of freedom determine the rotational speed of each rotating member in the system. The input NA2 is transmitted by a reverse transfer differential driver to form two rotating speeds which rotate coaxially and simultaneously, the differential speed between absolute values of the two rotating speeds is actively adjusted through the input NA1, the balance between the forward torque and the reverse torque during the differential speed is adjusted, and the differential speed can be adjusted by adjusting the rotating speed NA1 of the input end with small torque. Control a1 sets NA1 to 0, and | NB2| ═ NC2|, the differential speed is zero. By controlling the value of NA1 to be positive or negative, the differential speed can be controlled to be positive or negative. This kind of application, reverse transfer differential driver also can be used to the transmission of coaxial reversal bispin wing or coaxial reversal bispin oar to bispin wing or bispin oar are connected with this embodiment output as the application end, and two rotational speeds of coaxial co-rotation form two rotational speeds of coaxial reversal from the output transmission to the application end, drive coaxial reversal bispin wing or bispin oar. The two connections from the output to the application end are typically a direct connection and an indirect connection with a transmission ratio of-1.0, such as an indirect connection with a one-way commutator, see fig. 3. The speed of rotation is directed to be suitable for connecting the coaxial contra-rotating twin rotors. If desired, two indirect connections can be used, as shown in fig. 7 and 8. In the figures 7 and 8, two coaxial rotating speeds from the output ends 1 and 2 of the co-rotating clutch are transmitted to the application ends 3 and 4 and are converted into two coaxial rotating speeds. The reverse use of the transmission mechanism in fig. 7 and 8 can also convert two rotating speeds of coaxial and same rotation into two rotating speeds of coaxial and reverse rotation.

And in the third application mode, the reverse transfer differential driver can be used as a double-flow variable speed driver for driving two driving wheels of a tracked vehicle or a multi-wheel special vehicle. Two driving wheels of the vehicle are used as application ends to be connected with two output ends of the embodiment. Two connections from the output to the application end, typically two indirect connections, can be seen in fig. 6. In fig. 6, two coaxially-reversed rotating speeds from the output ends 1 and 2 of the co-rotating clutch are transmitted to the application ends 3 and 4 and are converted into two coaxially-rotated rotating speeds, and the rotating speeds are oriented to be suitable for being connected with the two driving wheels. The input NA1 enables the two drive wheels to rotate in the same direction, and the vehicle to move forward or backward; the input NA2 can enable the two driving wheels to rotate reversely, and the vehicle turns in situ; meanwhile, the NA1 and the NA2 are input, the two driving wheels rotate in the same direction and rotate at a different speed, and the vehicle turns during running. It should be noted that during the input of NA1, the torque of the forward input is balanced with the torque of the reverse input. During the input of NA2, the torque of the forward input is unbalanced with the torque of the reverse input.

In the fourth application mode, the reverse transfer differential driver has another application mode which can be used as a double-flow variable speed driver for two driving wheels of a crawler vehicle or a multi-wheel special vehicle. Two driving wheels of the vehicle are used as application ends to be connected with the output end of the embodiment. The two connections from the output end to the application end generally adopt two indirect connections, which can be seen in fig. 9 and 10, wherein two rotating speeds coaxially and synchronously from the output ends 1 and 2 are transmitted to the application ends 3 and 4 or are coaxially and synchronously transmitted, and the rotating speeds are oriented to be suitable for connecting the two driving wheels. The input NA2 enables the two drive wheels to rotate in the same direction, and the vehicle to move forward or backward; the input NA1 can enable the two driving wheels to rotate reversely, and the vehicle turns in situ; meanwhile, the NA2 and the NA1 are input, the two driving wheels rotate in the same direction and rotate at a different speed, and the vehicle turns during running. It should be noted that during the input of NA1, the torque of the forward input is balanced with the torque of the reverse input. During the input of NA2, the torque of the forward input is unbalanced with the torque of the reverse input.

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

Claims

1. The reverse transfer differential driver is composed of a reverse transfer case, a single-way speed changer and a homodromous 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 I: the kinematic characteristic equation is in the form of NA1 ═ 1+ k ═ NB1-k × (NC 1, k >1.0 after the consolidation deformation, the one-way shift gear is used in one of the two connections between the transfer gear transfer end and the input end of the co-rotating clutch, for the indirect connection outside the coaxial of the two connections, when a transmission ratio value of (1+ k)/k is set for the indirect connection of C1 and C2, (1+ k) ═ NB1 ═ NC1 when NB2 is set to NC-NC 2, (1+ k) ═ NB1 ═ NC-k 1 when NB2 is set to NC2 when k/(1+ k) is set for the indirect connection of B1 and B2, the one-way shift gear can be in the form of a parallel axis cylindrical gear or a single-axis planetary gear row, the one-way shift gear can be in the form of a single-axis cylindrical gear row or a double-layer planetary row, the one-way shift gear row can be in the form of a double-layer planetary row, is characterized in that the planet row meets the second condition: the kinematic characteristic equation is in the form of a homodromous clutch kinematic equation NA2 being 0.5 × NB2+0.5 × NC2 after arrangement and deformation, a central wheel A2 corresponding to NA2 is used as a turnover control end, B2 and C2 are used as the input end of the homodromous clutch and the output end of a reverse transfer differential transmission, a component A1 corresponding to NA1 is used as the input end of the reverse transfer in a reverse transfer planetary row, which is also used as the input end of the reverse transfer differential transmission of the invention, the other two components of the reverse transfer are used as the transfer ends, a transfer end B1 is connected with the homodromous clutch input end B2, a transfer end C1 is connected with the homodromous clutch input end C2, which are connected coaxially, wherein one component A2 corresponding to NA2 is used as the turnover control end, which is also used as the turnover control end of the reverse transfer differential transmission of the invention, the other two components of the same-direction clutch are used as two input ends and two output ends, and the two components are also used as two output ends of the reverse transfer differential driver.

2. The reverse transfer differential transmission of claim 1, which is a planetary row composite structure, is a two-degree-of-freedom determination system, when the rotation speed NA1 of the input end and the rotation speed NA2 of the epicyclic control end are determined, the rotation speeds of all rotating members in the system are determined, including the rotation speeds NB2 and NC2 of the output ends, when one of NA1 and NA2 is determined, and the absolute value of the differential speed of the two output ends is also determined, the rotation speeds of all rotating members in the system are also determined, and according to different control and different connection of the output ends and the application ends, the invention has five application modes: the application mode I is used for coaxial reverse rotation double-rotor transmission, when the absolute value of NA1 is larger, the speed difference between the absolute values of the rotating speeds of the two output ends can be adjusted by adjusting NA2, the application mode II is used for coaxial reverse rotation double-rotor transmission, when the absolute value of NA2 is larger, the adjustment of NA1 can adjust the differential speed between the absolute values of the rotating speeds of two output ends, the application mode is three-way as a double-flow speed change transmission, the input NA1 can enable two driving wheels to rotate in the same direction, the input NA2 can enable the two driving wheels to rotate in opposite directions, the application mode is four-way as a double-flow speed change transmission, the input NA2 can enable the two driving wheels to rotate in the same direction, the input NA1 can enable the two driving wheels to rotate in opposite directions, the application mode is five-way as a variable damping differential, when NA2 determines that the differential in absolute values of the speeds at the two outputs is determined by the loads at the two application terminals to which the two outputs are connected, adjusting the braking force of the brake device to which input a1 is connected adjusts the damping of the differential motion of the two application ends.