Intersecting-axis non-circular-face gear transmission mechanism
阅读说明:本技术 一种相交轴非圆面齿轮传动机构 (Intersecting-axis non-circular-face gear transmission mechanism ) 是由 刘大伟 吕珍珍 于 2019-11-21 设计创作,主要内容包括:一种相交轴非圆面齿轮传动机构,所述传动机构包括小圆柱齿轮和非圆面齿轮,所述小圆柱齿轮与非圆面齿轮的回转轴线非正交,且啮合过程中,小圆柱齿轮的节圆柱与非圆面齿轮的节圆锥保持相切,切线为非圆面齿轮的节圆锥母线;所述非圆面齿轮的节曲线为缠绕在其节圆锥面上的一条曲线,所述非圆面齿轮节曲线在节圆锥底面上的投影是一条关于节圆锥轴线的非圆曲线。本发明由一对齿轮啮合构成的传动机构实现了以往相交轴传动结构非正交时至少两对齿轮才能获得的减-变速复合传动效果,最大限度地简化传动结构、缩短传动链、减少传动零件、提高传动效率和精度,尤其适用于任意相交轴结构、有空间限制且有减-变速复合传动要求的场合。(A kind of intersecting axis non-circular face gear drive, the said drive includes small cylindrical gear and non-circular face gear, the said small cylindrical gear is non-orthogonal with the axis of revolution of non-circular face gear, and in the course of engaging, the pitch circle column of the small cylindrical gear keeps tangent with pitch circle cone of the non-circular face gear, the tangent line is the pitch circle cone generating line of the non-circular face gear; the pitch curve of the non-circular face gear is a curve wound on the pitch cone surface of the non-circular face gear, and the projection of the pitch curve of the non-circular face gear on the bottom surface of the pitch cone is a non-circular curve relative to the axis of the pitch cone. The invention realizes the composite speed-reducing and speed-changing transmission effect which can be obtained only by at least two pairs of gears when the transmission structure of the prior intersecting shaft is not orthogonal by the transmission mechanism formed by meshing a pair of gears, simplifies the transmission structure to the utmost extent, shortens the transmission chain, reduces the transmission parts, improves the transmission efficiency and precision, and is particularly suitable for occasions with any intersecting shaft structure, space limitation and composite speed-reducing and speed-changing transmission requirements.)
1. The utility model provides an intersecting axis non-circular face gear drive which characterized in that: the transmission mechanism comprises a small cylindrical gear and a non-circular face gear, the rotation axes of the small cylindrical gear and the non-circular face gear are non-orthogonal, in the meshing process, a pitch cylinder of the small cylindrical gear and a pitch cone of the non-circular face gear are tangent, the tangent line is a pitch cone bus of the non-circular face gear, and the universal transmission ratio function of the continuous transmission mechanism is
In the formula, theta1Is the angle of rotation of a cylindrical gear ij=Z2/Z1Wherein Z is1,Z2The number of teeth of the small cylindrical gear and the non-circular gear respectively, n is the order of the pitch curve of the non-circular gear, M is any positive integer, akAnd bkAre transmission ratio coefficients, all of which are less than 1/ij(ii) a The pitch curve of the non-circular face gear is a curve wound on the pitch cone surface of the non-circular face gear, the projection of the pitch curve of the non-circular face gear on the bottom surface of the pitch cone is a non-circular curve relative to the axis of the pitch cone, and the expression is that
In the formula, r2,θ2Respectively the radial direction and polar angle r of the projection curve of the pitch curve of the non-circular face gear on the bottom surface of the pitch cone of the non-circular face gear1The equation of the closed pitch curve of the non-circular face gear is the radius of the pitch cylinder of the small cylindrical gear
Wherein λ is the coning angle of the non-circular face gear pitch cone.
2. An intersecting axis non-circular face gear transmission as claimed in claim 1 wherein: the value range of the taper angle lambda is 0-180 degrees.
3. An intersecting axis non-circular face gear transmission as claimed in claim 1 wherein: the gear teeth of the non-circular face gear are distributed along the pitch curve and are formed by enveloping a standard straight-tooth cylindrical gear slotting tool, the modulus of the standard straight-tooth cylindrical gear slotting tool is the same as that of the small cylindrical gear, and the number of teeth of the standard straight-tooth cylindrical gear slotting tool is more than that of the small cylindrical gear.
4. An intersecting axis non-circular face gear transmission as claimed in any one of claims 1 to 3 wherein: the pitch curve of the non-circular face gear is closed, and the simplest transmission ratio function of the transmission mechanism is
In the formula, n represents the order of the pitch curve of the non-circular face gear, and epsilon represents the eccentricity of the pitch curve of the non-circular face gear.
5. An intersecting axis non-circular face gear transmission as claimed in any one of claims 1 to 3 wherein: the small cylindrical gear is a straight tooth involute cylindrical gear or a helical tooth involute cylindrical gear or a cycloid cylindrical gear.
Technical Field
The invention relates to the field of transmission machinery, in particular to a crossed-axis non-circular-face gear transmission mechanism.
Background
In the field of mechanical transmissions, the transmission ratio transmission is a very large proportion. In order to meet specific process requirements, many applications require equipment with variable transmission ratio functions. In a plurality of variable-speed-ratio transmission mechanisms, a non-circular gear pair has the transmission characteristics of a cam and a gear, can realize high-efficiency and high-power accurate transmission ratio, and is widely applied to the fields of agricultural machinery, metallurgical machinery, printing machinery, light industrial machinery and the like. Because the prime motor of the equipment is generally an electric motor, has higher rotating speed and can not be directly connected with a speed change transmission mechanism to output speed change movement, a speed reduction mechanism is arranged between a non-circular gear pair and the prime motor in actual production, so that the speed reduction and speed change transmission can be realized by forming a series device by the speed reduction mechanism and the non-circular gear pair, compared with a single pair of gear pairs, the series transmission structure increases the length of a transmission chain, increases the transmission space and reduces the transmission efficiency, therefore, if the speed reduction and speed change functions can be integrated on one pair of gear pairs, the speed reduction and speed change integrated transmission can be realized, the transmission ratio of a driven gear and a driving gear of the gear pair is decomposed into the reciprocal of the product of a speed reduction ratio and a speed change ratio, the requirement of the equipment on the speed reduction and speed change composite transmission effect can be realized by the arbitrary combination of the speed reduction ratio and the speed change ratio, the transmission device is simplified, the transmission performance of the mechanism is improved, but the conventional non-circular gear pair can only realize speed reduction and speed change transmission in certain specific environments and cannot meet the requirements of actual production.
The plane non-circular gear can realize variable angular speed transmission between two parallel rotating shafts, and can be divided into various types according to the shape of the plane non-circular gear, but in practice, the most applied type is an elliptic gear pair and an eccentric circular gear pair. If the speed reduction and speed change integrated transmission is realized through a pair of plane non-circular gear pairs, a small non-circular gear and a large non-circular gear are matched for transmission. According to the conjugate principle of the non-circular gear, the rotation period T1 of the small non-circular gear and the rotation period T2 of the large non-circular gear must satisfy T1/n1 ═ T2/n2, wherein n1 and n2 are the period numbers of the pitch curves of the small non-circular gear and the large non-circular gear respectively, the deceleration effect of a pair of plane non-circular gear pairs is controlled by parameters n1 and n2, when the difference between n2 and n1 is larger, the deceleration effect is more obvious, and n2 also controls the period number of the output angular speed of the large non-circular gear rotating for one circle. If the planar non-circular gear pair realizes the speed reduction effect, the value of n2 must be greater than 1, so that the large non-circular gear rotates for a circle, the number of the change cycles of the angular speed is greater than 1, and the number of the cycles is also limited by the speed reduction ratio, that is, once the speed reduction ratio of the planar non-circular gear is determined, the number of the cycles of the output angular speed is also determined, so that the speed reduction transmission effect that the speed reduction ratio and the number of the cycles of the output angular speed can be combined arbitrarily in the traditional serial mechanism cannot be realized, and the planar non-circular gear pair can only realize certain specific speed reduction transmission effect.
The space noncircular gear can be used for realizing variable angular speed transmission between two intersecting shafts, the noncircular gear is a noncircular gear structure appearing earlier in the space noncircular gear, and the pitch curve mainly adopts an elliptic curve, a deformed elliptic curve improved by the elliptic curve and a high-order elliptic curve at present, such as an oval bevel gear pair disclosed in a Chinese patent with the publication number of CN1648490A, an eccentric elliptic bevel gear disclosed in a Chinese patent with the publication number of CN102003538A and a variable transmission ratio high-order modified elliptic bevel gear disclosed in a Chinese patent with the publication number of CN 101975247A. However, when the non-conical gears and the planar non-circular gears adopt the same elliptical pitch curve or a modified elliptical pitch curve, the gear ratios achieved by the non-conical gears and the planar non-circular gears are the same. Therefore, the speed reduction and shift effect achieved by the noncircular gears is the same as that of the planar noncircular gears, and any combination of the reduction ratio and the number of output angular speed cycles cannot be achieved. On the basis of this, patent publication No. CN102518756A discloses a variable-ratio transmission mechanism composed of a flat elliptic gear and a special face gear for transmitting a variable transmission ratio between two orthogonal shafts. The pitch curve periodicity of the elliptic gear is 1, when the pitch curve periodicity of the special face gear is an integer greater than 1, the speed reduction transmission can be realized, but like other types of non-circular gear pairs, the speed reduction ratio of the non-circular gear pair is limited by the output angular speed periodicity, and the effect of arbitrary speed reduction-speed change composite transmission between crossed shaft structures cannot be realized, for example, a patent with publication number of CN104500654A discloses a speed change ratio transmission mechanism composed of a cylindrical gear and a face gear, which is used for transmitting arbitrary speed reduction-speed change transmission between two orthogonal shafts, but the speed reduction-speed change composite transmission cannot be realized because two rotating shafts are orthogonal.
In summary, all types of non-circular gears cannot realize arbitrary reduction-speed change composite transmission between space arbitrary intersecting shaft structures at present.
Disclosure of Invention
In view of the above problems, the present invention aims to provide a non-circular face gear transmission mechanism with intersecting shafts, which can realize arbitrary speed reduction-change composite transmission between the intersecting shafts, reduce transmission space to the maximum extent, reduce transmission quality, and improve transmission efficiency.
The technical scheme adopted by the invention is as follows:
the invention provides a transmission mechanism of a crossed-axis non-circular-surface gear, which comprises a small cylindrical gear and a non-circular-surface gear, wherein the rotating axes of the small cylindrical gear and the non-circular-surface gear are non-orthogonal, a pitch cylinder of the small cylindrical gear and a pitch cone of the non-circular-surface gear are tangent in the tangential meshing process, the tangent line is a pitch cone bus of the non-circular-surface gear, and a universal transmission ratio function of the transmission mechanism during continuous transmission is that
In the formula, theta1Is the angle of rotation of a cylindrical gear ij=Z2/Z1Wherein Z is1,Z2The number of teeth of the small cylindrical gear and the non-circular gear respectively, n is the order of the pitch curve of the non-circular gear, M is any positive integer, akAnd bkAre transmission ratio coefficients, all of which are less than 1/ijThe pitch curve of the non-circular face gear is a curve wound on the pitch cone surface of the non-circular face gear, the projection of the pitch curve of the non-circular face gear on the bottom surface of the pitch cone is a non-circular curve relative to the axis of the pitch cone, and the expression is that
In the formula, r2,θ2Respectively the radial direction and polar angle r of the projection curve of the pitch curve of the non-circular face gear on the bottom surface of the pitch cone of the non-circular face gear1The equation of the closed pitch curve of the non-circular face gear is the radius of the pitch cylinder of the small cylindrical gear
Wherein λ is the coning angle of the non-circular face gear pitch cone.
Furthermore, the value range of the taper angle lambda is 0-180 degrees.
Furthermore, the gear teeth of the non-circular face gear are distributed along the pitch curve and are formed by enveloping a standard straight-tooth cylindrical gear slotting tool, the modulus of the standard straight-tooth cylindrical gear slotting tool is the same as that of the small cylindrical gear, and the number of the teeth of the standard straight-tooth cylindrical gear slotting tool is more than that of the small cylindrical gear.
Further, the pitch curve of the non-circular face gear is closed, and the simplest transmission ratio function of the transmission mechanism is
In the formula, n represents the order of the pitch curve of the non-circular face gear, and epsilon represents the eccentricity of the pitch curve of the non-circular face gear.
Furthermore, the small cylindrical gear is a straight tooth involute cylindrical gear or a helical tooth involute cylindrical gear or a cycloid cylindrical gear.
Compared with the prior art, the invention has the following beneficial effects:
the transmission mechanism formed by meshing a pair of gears realizes the reduction-speed change composite transmission effect which can be obtained by at least two pairs of gears when the transmission structure of the prior intersecting shaft is not orthogonal, simplifies the transmission structure to the maximum extent, shortens the transmission chain, reduces the transmission parts, improves the transmission efficiency and precision, and is particularly suitable for occasions with any intersecting shaft structure, space limitation and reduction-speed change composite transmission requirements.
Drawings
FIG. 1 is a schematic view of an assembled structure of an embodiment of an intersecting axis non-circular face gear transmission mechanism of the present invention;
FIG. 2 is a front view of the present invention;
FIG. 3 is a right side view of the present invention;
FIG. 4 is a view of the relative positions of the pitch cone surface of a non-circular gear and the pitch cylinder surface of a small cylindrical gear;
FIG. 5 shows the ratio of small cylindrical to non-circular face gears i12A graph of (a);
FIG. 6 shows the gear ratio i between the small cylindrical gear and the non-circular face gearbA graph of (a).
Wherein, the reference numbers: 1. a small cylindrical gear; 2. a non-circular face gear; 3. a non-circular face gear pitch conical face; 4. a non-circular face gear pitch curve; 5. pitch cylinder of small cylindrical gear.
Detailed Description
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without creative efforts.
Referring to fig. 1 to 4, a specific structure of an embodiment of an intersecting axis non-circular face gear transmission mechanism proposed by the present invention is given. The transmission mechanism comprises a driving gear and a driven gear which are meshed with each other, wherein the driving gear is a small
The axes of the small
In the formula, theta1Is the rotation angle of a small
The
In the formula, theta2Is said toThe polar angle of the projection curve of the
Wherein λ is the sub-cone angle of the non-circular face gear pitch cone, and the sub-cone angle λ is in the range of 0-180 °.
When the non-circular face
When the small
In the present invention, the non-circular face gear pitch curve4 determines the reduction-speed transmission ratio rule of the gear pair, therefore, the shape of the non-circular face
Connecting a small
An imaginary straight-toothed spur gear is meshed with the non-circular-
The change rule of the transmission ratio when the axes of the small
(1) Taking epsilon as 0.15, n as 1, m as 2mm, Z1=17,Z2At 70, λ is 80 °. When the
(2) Keeping the small cylindrical gear unchanged, taking Z1 as 17 and m as 2mm, changing the period number n of the non-circular face
(3) The small
(4) The
When the
The above-mentioned embodiments are merely illustrative of the preferred embodiments of the present invention, and do not limit the scope of the present invention, and various modifications and improvements of the technical solution of the present invention by those skilled in the art should fall within the protection scope defined by the claims of the present invention without departing from the spirit of the present invention.
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