阅读说明：本技术 一种内啮合斜齿轮传动机构 (Inner gearing helical gear transmission mechanism ) 是由 李轩 孙立宁 于 2020-06-12 设计创作，主要内容包括：本发明公开了一种内啮合斜齿轮传动机构,包括相啮合的内齿轮和外齿轮,内齿轮和外齿轮均为斜齿轮,外齿轮的法向齿廓曲线为圆弧曲线,内齿轮的法向齿廓曲线为摆线曲线。本发明提高了传动齿轮的齿根弯曲强度及齿面承载力,且不易发生根切,可以在相同体积及中心距条件下获得较大传动比,且大大降低了轮齿的滑动磨损,能够较好的满足高速、重载、高功率的齿轮传动要求。(The invention discloses an internal meshing helical gear transmission mechanism which comprises an internal gear and an external gear which are meshed with each other, wherein the internal gear and the external gear are helical gears, the normal tooth profile curve of the external gear is an arc curve, and the normal tooth profile curve of the internal gear is a cycloid curve. The invention improves the tooth root bending strength and the tooth surface bearing capacity of the transmission gear, is not easy to undercut, can obtain larger transmission ratio under the condition of the same volume and center distance, greatly reduces the sliding abrasion of the gear teeth, and can better meet the transmission requirements of high-speed, heavy-load and high-power gears.)

1. An internal meshing helical gear transmission mechanism comprises an internal gear and an external gear which are meshed with each other, and is characterized in that the internal gear and the external gear are helical gears, a normal tooth profile curve of the external gear is an arc curve, and a normal tooth profile curve of the internal gear is a cycloid curve.

2. The internally meshing helical gear transmission according to claim 1, wherein said cycloidal curve is formed by enveloping said circular arc curve.

3. The inside-meshing helical gear transmission according to claim 2, wherein the tooth surface equation of said external gear is:

wherein x is₁、y₁、z₁Respectively representing the coordinates of the tooth surface of the external gear in the x direction, the y direction and the z direction, e is the distribution circle radius of the normal outline of the external gear, rho is the circular arc radius of the normal tooth profile of the external gear, and n is₁Is the number of external gear teeth, phi₁＝2π/n₁The included angle between adjacent gear teeth of the external gear is k +/-1, gamma is the deflection angle of a connecting line between the circle center of the circular arc and the center of the external gear, and p is₁＝R₁tan β is the external gear pitch coefficient, β is the helix angle, R₁＝a/(i₁₂-1) is the base radius of the external gear, a is the center distance between the external gear and the internal gear, i₁₂＝n₂/n₁Is the gear ratio of the internal gear to the external gear, n₂The number of teeth of the internal gear is,

4. The inside helical gear transmission according to claim 3, wherein the tooth flank equation of said internal gear is:

wherein x is₂、y₂、z₂Respectively representing x, y, z coordinates of the tooth surface of the internal gear, a being the center distance between the external gear and the internal gear, phi₂＝2π/n₂Angle between adjacent teeth of the internal gear, α₁Indicates the rotation angle of the external gear, α₂Indicating the internal gear rotation angle, p₂＝R₂tan β is the internal gear pitch coefficient, R₂＝ai₁₂/(i₁₂-1) is the internal gear base radius,the spiral angle of the internal gear is variable,maximum value of helical angle of internal gear theta₂∈[θ_2o,θ_2t]For internal gear tooth profile angle parameter, theta_2oIs the minimum value of the internal gear tooth profile angle parameter, theta_2tThe maximum value of the internal gear tooth profile angle parameter.

5. The internally meshing helical gear transmission according to claim 1, wherein the external gear and the internal gear each employ a herringbone gear.

Technical Field

The invention relates to the technical field of gear transmission, in particular to an internal meshing helical gear transmission mechanism.

Background

A gear is a basic component that transfers motion and power through tooth flank engagement. Among various gear engagement pairs, involute gears are widely used due to the characteristics of convenience in processing and manufacturing, center distance separability and the like. However, the gear teeth of the involute gear are thin and high, the bending strength of the tooth root is poor, the bearing capacity of the tooth surface is low, and the tooth number is at least 17 teeth in order to prevent the involute gear from generating undercut in the machining process, so that the existing involute gear transmission mechanism cannot realize large transmission ratio under the condition of the same center distance and volume; meanwhile, the relative sliding speed is too high between the meshing tooth surfaces near the pitch circle and close to the tooth root part, so that the area is easy to be seriously abraded, and the requirements of high-speed, heavy-load and high-power gear transmission cannot be met.

Disclosure of Invention

The technical problem to be solved by the invention is to provide an internal meshing helical gear transmission mechanism, which can improve the tooth root bending strength and the tooth surface bearing capacity of a transmission gear, is not easy to undercut, can obtain a larger transmission ratio under the conditions of the same volume and center distance, is beneficial to reducing the sliding abrasion of gear teeth, and can better meet the gear transmission requirements of high speed, heavy load and high power.

In order to solve the technical problems, the technical scheme provided by the invention is as follows:

an inner gearing helical gear transmission mechanism comprises an inner gear and an outer gear which are meshed with each other, wherein the inner gear and the outer gear are helical gears, a normal tooth profile curve of the outer gear is an arc curve, and a normal tooth profile curve of the inner gear is a cycloid curve.

In one embodiment, the cycloid curve is formed by the circular arc curve in an enveloping motion.

In one embodiment, the tooth surface equation of the external gear is:

wherein x is₁、y₁、z₁Respectively representing the coordinates of the tooth surface of the external gear in the x direction, the y direction and the z direction, e is the distribution circle radius of the normal outline of the external gear, rho is the circular arc radius of the normal tooth profile of the external gear, and n is₁Is the number of external gear teeth, phi₁＝2π/n₁The included angle between adjacent gear teeth of the external gear is k +/-1, gamma is the deflection angle of a connecting line between the circle center of the circular arc and the center of the external gear, and p is₁＝R₁tan β is the external gear pitch coefficient, β is the helix angle, R₁＝a/(i₁₂-1) is the base radius of the external gear, a is the center distance between the external gear and the internal gear, i₁₂＝n₂/n₁Is the gear ratio of the internal gear to the external gear, n₂The number of teeth of the internal gear is,

is an external gearThe variable quantity of the angle of the spiral rotation,is the maximum value of the helical rotation angle of the external gear, B is the gear width, theta₁∈[θ_1o,θ_1t]Is the tooth profile angle parameter of the external gear theta_1oIs the minimum value of the tooth profile angle parameter of the external gear, theta_1tIs the maximum value of the tooth profile angle parameter of the external gear.

In one embodiment, the tooth surface equation of the internal gear is as follows:

wherein x is₂、y₂、z₂Respectively representing x, y, z coordinates of the tooth surface of the internal gear, a being the center distance between the external gear and the internal gear, phi₂＝2π/n₂Angle between adjacent teeth of the internal gear, α₁Indicates the rotation angle of the external gear, α₂Indicating the internal gear rotation angle, p₂＝R₂tan β is the internal gear pitch coefficient, R₂＝ai₁₂/(i₁₂-1) is the internal gear base radius,the spiral angle of the internal gear is variable,maximum value of helical angle of internal gear theta₂∈[θ_2o,θ_2t]For internal gear tooth profile angle parameter, theta_2oIs the minimum value of the internal gear tooth profile angle parameter, theta_2tThe maximum value of the internal gear tooth profile angle parameter.

In one embodiment, the external gear and the internal gear are both herringbone gears.

The invention has the following beneficial effects: according to the internal meshing helical gear transmission mechanism, the normal tooth profile curve of the external gear is an arc curve, and the normal tooth profile curve of the internal gear is a cycloid curve, so that a conjugate gear pair formed by a normal arc and a cycloid is formed, spiral meshing transmission is realized, the transmission mechanism has a small sliding rate, and the failure of the gear due to sliding abrasion can be effectively avoided; the undercut is not easy to occur, the processing is convenient, the minimum tooth number of the external gear can reach 1, and the design requirements of small tooth number and large transmission can be realized under the conditions of the same volume and center distance; the gear meshing pair has the advantages of small gear tooth height, wide gear root, large modulus, good tooth root bending strength and tooth surface contact strength, large tooth surface bearing capacity and small gear volume, and can better meet the transmission requirements of high speed, heavy load and high power.

Drawings

FIG. 1 is a schematic three-dimensional structure of an internally meshing helical gear transmission of the present invention;

FIG. 2 is a front elevational view of the internally meshing helical gear transmission of FIG. 1;

FIG. 3 is a schematic illustration of the meshing of the normal tooth profiles of the outer gear and the inner gear shown in FIG. 1;

FIG. 4 is a schematic illustration of the outer gear normal profile curve shown in FIG. 1;

FIG. 5 is a schematic illustration of the normal profile curve of the internal gear shown in FIG. 1;

FIG. 6 is a schematic three-dimensional structure of the external gear of FIG. 1;

FIG. 7 is a schematic three-dimensional structure of the internal gear of FIG. 1;

in the figure: 1. external gear, 2, internal gear.

Detailed Description

The present invention is further described below in conjunction with the following figures and specific examples so that those skilled in the art may better understand the present invention and practice it, but the examples are not intended to limit the present invention.

As shown in fig. 1 to 3, the present embodiment discloses an internal meshing helical gear transmission mechanism, which includes an internal gear 2 and an external gear 1 that are meshed with each other, where the internal gear 2 and the external gear 1 are helical gears, a normal tooth profile curve of the external gear 1 is a circular arc curve, and a normal tooth profile curve of the internal gear 2 is a cycloid curve.

Further, the cycloid curve is formed by enveloping the circular arc curve.

As shown in fig. 4, the normal tooth profile curve of the external gear 1 is a circular arc curve 1a, the radius of the circular arc curve 1a is ρ, the generating circle (radius ρ) where the circular arc curve 1a is located is 1b, as shown in fig. 5, the generating circle 1b where the circular arc curve 1a is located performs an envelope motion according to a relative motion relationship to form a cycloid curve 2b, and the normal tooth profile curve 2a of the internal gear 2 is a part of the cycloid curve 2 b.

In one embodiment, referring to fig. 6, the structure of the external gear 1, the tooth surface equation of the external gear 1 is:

wherein x is₁、y₁、z₁Respectively representing the coordinates of the tooth surface of the external gear 1 in the x, y and z directions, e is the distribution circle radius of the normal profile of the external gear 1, rho is the arc radius of the normal profile of the external gear 1, and n is the distribution circle radius of the normal profile of the external gear 1₁Is the number of teeth of the external gear 1, phi₁＝2π/n₁The included angle between adjacent gear teeth of the external gear 1 is defined as k ═ 1, k ═ 1 indicates that the tooth surface equation corresponds to the left side tooth surface of the gear teeth, k ═ -1 indicates that the tooth surface equation corresponds to the right side tooth surface of the corresponding gear teeth, and gamma is the center of the circular arc and the center O of the external gear₁Angle of deflection of connecting line, p₁＝R₁tan β is the pitch coefficient of the external gear 1, β is the helix angle, R₁＝a/(i₁₂-1) is the base radius of the external gear 1, a is the centre distance between the external gear 1 and the internal gear 2, i₁₂＝n₂/n₁The gear ratio of the internal gear 2 to the external gear 1, n₂The number of teeth of the internal gear 2,

is a variation of the helical angle of the outer gear 1,is the maximum value of the helix angle of the external gear 1, B is the gear width, theta₁∈[θ_1o,θ_1t]Is the tooth profile angle parameter, theta, of the external gear 1_1oIs the tooth profile angle of the external gear 1Minimum value of parameter, theta_1tIs the maximum value of the tooth profile angle parameter of the external gear 1.

Here, the helix angle β of the external gear 1 and the internal gear 2 is the same, and the gear width B is also the same.

Further, referring to fig. 7, the structure of the internal gear 2, the tooth surface equation of the internal gear 2 is:

wherein x is₂、y₂、z₂Respectively representing x, y, z coordinates of the tooth surface of the internal gear 2, a being the center distance between the external gear 1 and the internal gear 2, phi₂＝2π/n₂Angle between adjacent teeth of the ring gear 2, α₁Indicates the rotation angle of the external gear 1, α₂The rotation angle of the internal gear 2 is represented, that is, the rotation angle of the internal gear 2 in the envelope motion of the cycloid curve formed by the envelope motion of the circular arc curve;

p₂＝R₂tan β is the pitch coefficient of the internal gear 2, R₂＝ai₁₂/(i₁₂-1) is the base radius of the annulus gear 2,as a variable of the helical angle of the internal gear 2,is the maximum value of the helical angle of the internal gear 2, theta₂∈[θ_2o,θ_2t]Is a tooth profile angle parameter theta of the internal gear 2_2oIs the minimum value of the tooth profile angle parameter of the internal gear 2_2tIs the maximum value of the tooth profile angle parameter of the internal gear 2.

In one embodiment, the external gear 1 and the internal gear 2 can both adopt herringbone gears, that is, the tooth surfaces of the external gear 1 and the internal gear 2 can both be designed into herringbone structures which are axially symmetrical and have opposite spiral directions, so as to better eliminate the transverse force of the gears on the central shaft.

The transmission mechanism formed by the external gear 1 and the internal gear 2 is suitable for internal meshing fixed-axis gear transmission and is parallel-axis internal meshing gear transmission.

In the internal meshing helical gear transmission mechanism, the normal tooth profile curve of the external gear 1 is an arc curve, and the normal tooth profile curve of the internal gear 2 is a cycloid curve, so that a conjugate gear pair formed by a normal arc and a cycloid is formed, spiral meshing transmission is realized, the transmission mechanism has a small sliding rate, and failure of the gear due to sliding abrasion can be effectively avoided; the undercut is not easy to occur, the processing is convenient, the minimum tooth number of the external gear can reach 1, and the design requirements of small tooth number and large transmission can be realized under the conditions of the same volume and center distance; the gear meshing pair has the advantages of small gear tooth height, wide gear root, large modulus, good tooth root bending strength and tooth surface contact strength, large tooth surface bearing capacity and small gear volume, and can better meet the transmission requirements of high speed, heavy load and high power.

The above-mentioned embodiments are merely preferred embodiments for fully illustrating the present invention, and the scope of the present invention is not limited thereto. The equivalent substitution or change made by the technical personnel in the technical field on the basis of the invention is all within the protection scope of the invention. The protection scope of the invention is subject to the claims.