WO2019085882A1

WO2019085882A1 - Non-tapered gear differential

Info

Publication number: WO2019085882A1
Application number: PCT/CN2018/112604
Authority: WO
Inventors: 罗灿
Original assignee: 罗灿
Priority date: 2017-10-31
Filing date: 2018-10-30
Publication date: 2019-05-09
Also published as: CN109723792A; CN109891130B; CN109891130A

Abstract

A non-tapered gear differential has two structures. In the first structure, two single-layer planet gearsets are arranged, and each of them is not provided with annular gears. The planet gearsets are in start connection. A second planet gearset sun gear serving as an input connection end is connected to an input end; a first planet gearset sun gear serving as a first output connection end and a planet carrier serving as a second output connection end are separately connected to one output end. In the second structure, a double-layer planet gearset and a single-layer planet gearset are arranged, and each of them is not provided with annular gears. The planet gearsets are in start connection. A planet carrier serving as an input connection end is connected to an input end; a first planet gearset sun gear serving as a first output connection end and a second planet gearset sun gear serving as a second output connection end are separately connected to one output end.

Description

Non-bevel gear differential

Technical field

The invention relates to a planetary gear differential, in particular to a differential of a non-bevel gear planetary row structure of two structural forms.

Background technique

During the running of the motor vehicle, the rotational speed of each driving wheel will not be exactly the same due to the turning, the difference in the road surface, and the difference in the wheels. To avoid causing the wheels to slip and slip. The traditional method is to install a differential to accommodate this difference in speed. The differential is usually a bevel gear planetary differential. The bevel gear planetary differential has a large volume and complicated processing. Motor vehicles require a new planetary gear differential.

The ordinary cylindrical gear planetary row generally consists of two central wheels (one sun gear, one inner ring gear) and one planet carrier with planet gears. The meshing arrangement of the three components determines the planetary row type. The inner side of the planetary wheel meshes with the sun gear, and the planetary gear meshes with the inner ring gear. In general, the single-layer planetary carrier with a single-layer planetary gear is a double-layered planetary carrier with two layers of planetary gears that mesh with each other. Planetary platoon. When the structure requires it, the planetary row can be omitted without setting a center wheel (sun gear or ring gear). The rows of planet rows are interconnected to form a planetary row structure.

Summary of the invention

The invention is to solve the problem that the differential of the existing motor vehicle is a bevel gear planetary differential, which has the advantages of large volume and complicated processing, and provides a non-bevel gear with a planetary row structure, small volume and simple processing. Differential.

The non-bevel gear differential of the present invention is coupled to the input end and the output end, wherein the differential includes two planetary rows, each planetary row including a sun gear and a planet carrier with planet wheels, Set the inner ring gear; the connection between the two planetary rows is a star connection, the star connection is to a plurality of planetary rows, so that the number of planetary wheels of each planetary row is the same, and the size of each planetary row is adjusted, and some are enlarged. Some ratios are reduced until the distance between the axis of one of the planets in the planetary rows is equal to the axis of the planetary row; a certain planetary gear of a row of planetary rows and a certain planetary axle of an adjacent planetary row The heart is aligned, such that the ones of the planets participating in the connection have the same speed, and the planets participating in the connection have another identical speed; such planetary connections are called star connections of the planets. .

The invention has the following two structural forms:

Structural form 1: Set two planetary rows, the first planetary row and the second planetary row are single-layer planetary rows, the gear modules in the two planetary rows do not have to be equal; each planetary row includes one sun gear, one Planetary carrier with planetary gears, without inner ring gear, sun gear meshing with planetary gears; equalizing the number of planetary gear sets of two planetary rows, adjusting the size of two planetary rows until two planetary single-layer planetary axles The distance from the center of the planet to the axis of the planet is equal; a star connection is placed between the planet wheels of the two planet rows, and the two planet rows form the planetary row structure of the structural form one. Let the number of sun gears in the No. 1 planetary row be Nz, the number of teeth in the sun gear be Zz, and the number of teeth of the planetary gear meshing with the sun gear be Xz; the number of sun gears in the No. 2 planetary row is Ny, the number of sun gear teeth is Zy, and the sun gear The number of meshed planetary gear teeth is Xy, and the planetary carrier speeds of both planetary rows are Nj. Solving the equations, the structure of a planetary row structure obeys the equation of motion Nz-Zy*Xz/(Zz*Xy)*Ny=(1-Zy*Xz/(Zz*Xy))*Nj, the non-bevel gear of the present invention The structural form 1 of the differential is characterized by the number of teeth in the number one planet row, the number of single-plane planetary gears in the first planetary row, the number of teeth in the second planetary row, and the number of teeth in the single-plane planetary row of the first planetary row. Zy*Xz/(Zz*Xy)=2.0, such that the equation of motion is Nz-2*Ny=(1-2)*Nj, ie Nz+Nj=2*Ny. The second planetary row sun gear is used as the input terminal to connect the input end; the first planetary row sun gear is used as the first output connecting end, the planet carrier is used as the second output connecting end, and the two output connecting ends are connected to the two output ends. The non-cone gear differential structure form 1 is formed, see Fig. 1.

The second structural form is: two planet rows are arranged, the first planet is a double-layered planetary row, and the second planet is a single-layer planetary row. The gear modules in the two planetary rows are not necessarily equal; each planetary row Including a sun gear, a planet carrier with planet wheels, no inner ring gear, the sun gear meshes with the planet wheels; equalizes the number of planet wheels of the two planet rows, and adjusts the size of the two planet rows until the number one The distance from the outer planet axis of the planet to the axis of the planetary row is equal to the distance from the axis of the single-plane planetary wheel to the axis of the planetary row; the outer planet of the first planet and the single-plane planetary of the second planet The star connection is set up, and the two planetary rows form the planetary row structure of the structural form 2. Let the number of sun gears in the No. 1 planetary platoon be Nz, the number of teeth of the sun gear be Zz, and the number of teeth of the outer planetary gears indirectly meshed with the inner gear by the inner planetary gears is Xz; the speed of the sun gear in the second planetary platoon is Ny, the sun The number of teeth is Zy, the number of single-plane planetary gears meshed with the sun gear is Xy, and the planetary frame rotation speed of both planetary rows is Nj. Solving the equations, the structure of the second planetary row structure obeys the equation of motion Nz+Zy*Xz/(Zz*Xy)*Ny=(1+Zy*Xz/(Zz*Xy))*Nj, the non-bevel gear difference The structural form 2 of the speed governor is characterized by the number of teeth of the No. 1 planetary row, the number of teeth of the outer planet of the No. 1 planet, the number of teeth of the No. 2 planetary row, and the number of the number of teeth of the No. 2 planetary row. Zy* Xz / (Zz * Xy) = 1.0, such that the equation of motion is Nz + 1 * Ny = (1 + 1) * Nj, that is, Nz + Ny = 2 * Nj. The planet carrier is used as the input connection terminal to connect the input end; the first planetary row sun gear is used as the first output connection end, the second planetary row sun gear is used as the second output connection end, and the two output connection ends are connected to the two output terminals. The second form of the non-bevel gear differential is formed, see Figure 2.

The input end is a transmission shaft, a transmission gear, a transmission bevel gear, and the like after the power source or the power source, and the output end is a transmission shaft, a transmission half shaft, a universal joint, and the like before the left and right driving wheels or the driving wheels.

The transmission process of the non-bevel gear differential of the present invention is similar to the transmission process of the bevel gear planetary differential, and the rotational speed characteristic and the torque characteristic of an input connection end and two output connection ends when distributing power and providing differential speed are also similar. When the load torque of the two outputs is equalized, the input connection speed is equal to the speed of the two output connections. When the load torque of the two outputs is unbalanced, there is no change in the speed of the input connection, and the increment of the rotation speed of one output connection corresponds to the negative increment of the same magnitude of the rotation of the other output connection.

Planetary differentials, when the number of planetary wheels is constant, when it is necessary to increase the rated torque, usually by increasing the gear modulus of the component and increasing the tooth width. The adjustment range for increasing the gear modulus is limited, and the expansion of the rated torque mainly depends on the method of increasing the tooth width. The increase in the tooth width of the conventional bevel gear planetary differential means that the diameter is increased simultaneously in the three directions of the x, y, and z axes, and thus the volume increase is large when the same rated torque is expanded. And the bevel gear planetary row processing is complicated. The non-bevel gear differential of the present invention is a non-bevel gear planetary row structure, and the gears in the planetary row structure adopt parallel gears, such as ordinary cylindrical gears, cylindrical helical gears, ordinary circular gears, circular helical gears and the like. Non-bevel gear planetary differentials increase the tooth width only by increasing the length dimension parallel to the output shaft, and the volume increase is smaller when the same rated torque is increased. And the non-bevel gear planetary row processing is relatively simple. Therefore, the present invention is advantageous in that the non-bevel gear differential is small in size and simple in processing.

DRAWINGS

1 is a schematic structural view of a non-bevel gear differential of a non-bevel gear differential of the present invention, and is also a schematic view of Embodiment 1 of the present invention. In the figure, 1 is the No. 2 planet row sun gear, 2 is the planet carrier, 3 is the No. 1 planet row sun gear, and 4 is the input bevel gear.

2 is a schematic structural view of a non-bevel gear differential of the present invention, and is a schematic view of Embodiment 2 of the present invention. In the figure, 1 is the planet carrier, 2 is the number one planet row sun wheel, 3 is the second planet row sun gear, and 4 is the input bevel gear.

In the figure, the planetary row and the input bevel gear are shown in the half-frame structure diagram according to the industry practice. The input end is indicated by the input arrow and the output end is indicated by the output arrow. The components in the figure only show the structural relationship and do not reflect the true size.

Detailed ways

Embodiment 1: Structure of a non-bevel gear differential of the present invention A non-bevel gear differential is also Embodiment 1 of the present invention. Two planetary rows are arranged. The first planetary row and the second planetary row are single-layer planetary rows. The gear modules in the two planetary rows do not have to be equal; each planetary row includes a sun gear and a planetary gear. Planet carrier, no inner ring gear is set, the sun gear meshes with the planet gears; the number of planet wheelsets of the two planet rows is equal, and the size of the two planet rows is adjusted until the two planets are single-layer planetary wheel axles to the planetary row The distance between the axes is equal; a star connection is provided between the single-plane planetary wheels of the two planetary rows, and the two planetary rows form a planetary row structure of the structural form one. Let the number of the sun gear (3) in the first planetary row be Nz, and the speed of the sun gear (1) in the second planetary row be Ny, and the planetary frame rotation speed of both planetary rows is Nj. Set the number of teeth of the No. 1 planetary row sun gear (3) to Zz=20, the number of teeth of the planetary gear meshing with the sun gear is Xz=24; set the number of teeth of the second planetary row sun gear (1) to Zy=30, mesh with the sun gear The number of planetary gear teeth is Xy=18. The non-bevel gear differential of the first embodiment is characterized by the number of teeth of the first planetary row, the number of single-plane planetary gears of the first planetary row, the number of teeth of the second planetary row, and the number of single-plane planetary gears of the first planetary row. The value is such that Zy*Xz/(Zz*Xy)=30*24/(20*18)=2.0, and the equation of motion is Nz+Nj=2*Ny. The second planetary row sun gear (1) is used as the input connection terminal to connect the input end; the first planetary row sun gear (3) is used as the first output connection end, and the planet carrier (2) is used as the second output connection end, two The output connecting end is connected to each of the two output ends to form the first structural form of the non-bevel gear differential of the first embodiment. Referring to Figure 1, the input is illustrated as a longitudinal input arrow and the input is connected to the input connection via an input bevel gear (4). If the input input shaft is lateral, the input and input connections are instead connected via the input slewing gear, as is the case when the engine is a transverse front drive. According to its equation of motion, when the load torque of the two output connections is equalized, the input link speed is equal to the speed of the two output terminals. When the load torque of the two output terminals is unbalanced, when the speed of the input terminal 2 planet row sun gear (1) is constant, the output terminal 1 planet row sun gear (3) rotates less than one angle, corresponding to the output connection end The planet carrier (2) rotates at the same angle; the output connection planet carrier (2) rotates less than one angle, corresponding to the output connection end of the first planetary row sun gear (3) multi-turn the same angle; in both cases, two output connections are formed The difference in rotational speed between the ends. This is the working process of the differential of the first embodiment.

Embodiment 2: Structure of the non-bevel gear differential of the present invention Two non-bevel gear differentials are also Embodiment 2 of the present invention. Set two planetary platoons, the first planet is a double-decker planetary platoon, and the second planet is a single-layer planetary platoon. The gear modules in the two planetary volleys do not have to be equal; each planetary platoon includes a sun gear. A planet carrier with planet gears, without an inner ring gear, the sun gear meshes with the planet wheels; the number of planet wheelsets of the two planet rows is equal, and the size of the two planet rows is adjusted (the double-layered planetary rows can also Adjust the distance between the circumference of the sun gear indexing circle and the circle circumference of the outer planet gears) until the distance from the outer planet axis of the planet No. 1 to the axis of the planetary row and the single-plane planetary center of the second planet to the planetary row The distance between the axes is equal; the outer planets of the first planet and the single planets of the second planet are connected by stars, and the two planets form the planetary structure of the second structure. Let the number of the sun gear (2) in the first planetary row be Nz, the speed of the sun gear (3) in the second planetary row be Ny, and the speed of the planet carrier (1) of the two planetary rows be Nj. Set the number of teeth of the No. 1 planet row (2) to Zz=18, and the number of teeth of the outer planets indirectly meshed with the inner gear by the inner planet is Xz=18; set the number of teeth of the second row of planets (3) to Zy =22, the number of single-layer planetary gears meshed with the sun gear is Xy=22. Solving the equations, the structure of the second planetary row structure obeys the equation of motion Nz+Zy*Xz/(Zz*Xy)*Ny=(1+Zy*Xz/(Zz*Xy))*Nj, the non-bevel gear difference The structural form 2 of the speed governor is characterized by the number of teeth of the No. 1 planetary row, the number of teeth of the outer planet of the No. 1 planet, the number of teeth of the No. 2 planetary row, and the number of the number of teeth of the No. 2 planetary row. Zy* Xz/(Zz*Xy)=22*18/(18*22)=1.0, and its equation of motion is Nz+Ny=2*Nj. The planet carrier (1) is used as the input connection terminal to connect the input terminal; the first planet row sun gear (2) is used as the first output connection end, and the second planet row sun gear (3) is used as the second output connection terminal, two The output terminals are connected to the two output terminals to form a non-bevel gear differential structure. Referring to Figure 2, the input is illustrated as a longitudinal input arrow, and the input is connected to the input connection via an input bevel gear (4). If the input input shaft is lateral, the input and input connections are instead connected via the input slewing gear, as is the case when the engine is a transverse front drive. According to its equation of motion, when the load torque of the two output connections is equalized, the input link speed is equal to the speed of the two output terminals. When the load torque of the two outputs is unbalanced, when the speed of the input connection planet carrier (1) is constant, the output terminal 1 planet row sun gear (2) rotates one angle less, corresponding to the output connection end of the second planet The row of sun wheels (3) rotates at the same angle; the output connection end of the second planet row sun gear (3) rotates one angle less, corresponding to the output connection end of the first planet row sun wheel (2) more turns the same angle; both cases A difference in rotational speed between the two output connections is formed. This is the working process of the differential of the second embodiment.

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

Claims

A non-bevel gear differential coupled to an input end and an output end, wherein the differential includes two planetary rows, each planetary row including a sun gear and a planet carrier with planet wheels, not set The inner ring gear; the connection between the two planetary rows is a star connection, the star connection is to the two planetary rows, so that the number of planetary wheels of each planetary row is the same, the size of each planetary row is adjusted, and some are enlarged, Some ratios are reduced until the distance between the axis of one planet in each planetary row is equal to the axis of the planetary row; one planet of a row of planets and one of the adjacent planets The alignment is such that the connections have the same rotational speed for each of the planets participating in the connection, and the respective planet carriers participating in the connection have another identical rotational speed, such a planetary row connection, called a planetary connection of the planetary row; One of the planetary rows of the sun gear constitutes one rotating member, and the other planetary row of the sun gear constitutes another rotating member, and the two planets of the same planetary frame rotate to form a third rotating member; Species structure: Structure I, Structure II.
The non-bevel gear differential according to claim 1, wherein the first form: two planetary rows, the first planetary row and the second planetary row are single-layer planetary rows, and the gear modules in the two planetary rows. Not necessarily equal; each planetary platoon consists of a sun gear, a planet carrier with planet gears, no inner ring gear, the sun gear meshes with the planet wheels; equalizes the number of planet wheelsets of the two planet rows, and regulates two planets The size of the row is such that the distance between the axis of the two planetary row single-plane planetary wheels and the axis of the planetary row is equal, and a star connection is arranged between the planet wheels of the two planetary rows; the structural form of the non-bevel gear differential of the present invention is The characteristics are: the number of sun gears in the number one planet, the number of single-plane planetary gears in the first planetary row, the number of sun gear teeth in the second planetary row, and the number of single-plane planetary gear teeth in the first planetary row make Zy*Xz/(Zz* Xy)=2.0, the equation of motion of the planetary row structure is Nz+Nj=2*Ny; the sun gear of the second planetary row is used as the input connection terminal, and the sun gear of the first planet is used as the first output connection end. With the planet carrier as the second output connection , Two output connections connected to the respective two output terminals, the non-formed structure a bevel gear differential.
The non-bevel gear differential according to claim 1, the second form: two planetary rows are arranged, the first planetary row is a double-layer planetary row, the second planetary row is a single-layer planetary row, and two planetary rows are arranged. The gear modules in the gears do not have to be equal; each planetary row consists of a sun gear, a planet carrier with planet gears, no inner ring gear, the sun gear meshes with the planet wheels, and the number of planet wheels of the two planet rows equals , adjust the size of the two planetary rows until the distance between the outer planet axis of the planets of the No. 1 planet and the axis of the planetary row is equal to the distance from the axis of the single-plane planetary wheel of the second planet to the axis of the planetary row; A planetary connection is arranged between the planetary carrier and the single-plane planetary gear of the second planetary gear. The structural form 2 of the non-bevel gear differential is characterized by the number of teeth of the first planetary row, the number of teeth of the outer planet of the first planetary row and The number of solar gears on the second planet and the number of single-plane planetary gears on the second planetary row make Zy*Xz/(Zz*Xy)=1.0, so that the equation of motion of the planetary row structure is Nj, Nz+Ny=2* Nj; connect the planet carrier as an input connector At the end, the No. 1 planet row sun wheel is used as the first output connection end, the No. 2 planet row sun wheel is used as the second output connection end, and the two output connection ends are connected to the two output ends; the non-bevel gear differential is formed Structural form two.