CN110848332B - Intersecting-axis non-circular-face gear transmission mechanism - Google Patents
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
- F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
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Abstract
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.
Description
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 of the gear pair, and the series structure of the gear transmission can be thoroughly changed, 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 cylindrical gear 1, the driven gear is a non-circular face gear 2, the small cylindrical gear 1 can be selected to be a straight tooth involute cylindrical gear or a helical involute cylindrical gear or a cycloid cylindrical gear, and in the embodiment, the small cylindrical gear 1 is a straight tooth involute cylindrical gear.
The axes of the small cylindrical gear 1 and the non-circular face gear 2 are non-orthogonal, the pitch surface of the non-circular face gear 2 is a conical surface, the pitch curve 4 of the non-circular face gear is a spatial non-circular curve on the pitch conical surface 3, gear teeth of the non-circular face gear are distributed along the pitch curve and are enveloped by 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 involute straight-tooth small cylindrical gear 1, and the number of teeth of the standard straight-tooth cylindrical gear slotting tool is more than that of the small cylindrical gear 1; the cylindrical surface of the reference circle on the small cylindrical gear 1 is the pitch cylindrical surface 5; as shown in fig. 3, the small cylindrical gear 1 and the non-circular gear 2 both rotate around the fixed shaft, the included angle between the rotation axes of the two gears is not equal to 90 degrees, the pitch cylindrical surface 5 of the small cylindrical gear is tangent to the pitch conical surface 3 of the non-circular gear, the tangent line is the pitch conical generatrix of the non-circular gear 2, and the pitch cylindrical surface 5 of the small cylindrical gear is in point contact with the pitch conical surface 4 of the non-circular gear and keeps pure rolling; the small cylindrical gear 1 is connected with a prime motor as an input component of the transmission mechanism, the non-circular face gear 2 is connected with a load as an output component of the transmission mechanism, and the universal transmission ratio function of the transmission mechanism taking the rotation angle of the small cylindrical gear 1 as an independent variable is
In the formula, theta1Is the rotation angle of a small cylindrical gear 1, n is the order of a non-circular face gear pitch curve 4, M is a positive integer, akAnd bkFor the transmission ratio coefficient, the value is less than ijThe reciprocal of (a); the transmission ratio of the non-circular face gear 2 and the small cylindrical gear 1 is decomposed into a reduction ratio ijAnd a speed change ratio ibInverse of the product, i.e. i21＝1/(ijib(θ1) And i) and ibFor variable gear ratios related to the rotation angle of the spur gear 1, ij＝Z2/Z1Wherein Z is1，Z2The number of teeth of the small cylindrical gear 1 and the number of teeth of the non-circular face gear 2 are respectively.
The pitch curve 4 of the non-circular face gear is a space curve wound on the pitch cone face 3, the projection of the pitch curve on the bottom surface of the pitch cone is a plane non-circular curve relative to the axis of the pitch cone, and the expression of the plane non-circular curve is
In the formula, theta2The polar angle of the projection curve of the non-circular face gear pitch curve 4 on the bottom surface of the pitch cone thereof; a coordinate system is established by taking the vertex of the pitch cone of the non-circular face gear 2 as an origin, and the closed pitch curve 4 of the non-circular face gear is expressed as
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 gear pitch curve 4 is a closed curve, the simplest transmission ratio function of the transmission mechanism is
When the small cylindrical gear 1 rotates relative to the non-circular gear 2, the pitch cylindrical surface 5 of the small cylindrical gear is in point contact with the pitch curve 4 of the non-circular gear and keeps rolling purely, and the achievable transmission ratio of the small cylindrical gear 1 to the non-circular gear 2 is represented as i12＝r2(θ2)/r1The pitch curve 4 of the non-circular face gear is a space non-circular curve, and the radial direction r of the projection curve of the pitch curve on the bottom surface of the pitch cone2Angle of rotation theta following non-circular face gear2Variation, pitch circle radius r of small cylindrical gear1Is a fixed value, so the transmission ratio i of the transmission mechanism12Angle of rotation theta following non-circular face gear2(ii) a change; when the pitch curve of the non-circular face gear 2 is a closed curve, the small cylindrical gear 1 and the non-circular face gear 2 can realize the continuous reduction-speed change composite transmission effect of the crossed shaft structure, and when the pitch curve 4 of the non-circular face gear is not closed, the small cylindrical gear 1 and the non-circular face gear 2 can only realize the local reduction-speed change composite transmission effect of the crossed shaft structure, and the former is more widely applied in practical production, so the invention further explains the reduction-speed change composite transmission scheme of the small cylindrical gear 1 and the non-circular face gear 2 when the crossed shaft structure is non-orthogonal by taking the closed space non-circular curve as the pitch curve of the non-circular face gear.
In the invention, the shape of the non-circular face gear pitch curve 4 determines the reduction-speed change transmission ratio rule of the gear pair, so the shape of the non-circular face gear pitch curve 4 is a key factor for designing the transmission mechanism; there are two ways to obtain the pitch curve 4, one is to obtain the required transmission ratio according to the actual requirements and by means of the formula i12＝r2(θ2)/r1Obtain pitch curve of non-circular face gear, and anotherThe existing space non-circular curve is directly adopted as the pitch curve of the non-circular face gear. In the embodiment, the pitch curve of the non-circular face gear obtained by the first method is taken as an example to illustrate the reduction-speed change composite transmission of the transmission mechanism.
Connecting a small cylindrical gear 1 with a prime motor as an input component of the transmission mechanism, connecting a non-circular face gear 2 with a load as an output component of the transmission mechanism, and enabling a first-order transmission ratio of the transmission mechanism to be i21＝(1+εcos(nθ1/ij))/ijIn the formula, ijIs the reduction ratio of the non-circular face gear 2, epsilon is the eccentricity of the non-circular face gear pitch curve 4, n is the order of the non-circular face gear pitch curve 4, theta1Is the angle of rotation of the small cylindrical gear 1.
An imaginary straight-toothed spur gear is meshed with the non-circular-face gear 2 for transmission, the tooth number and the modulus of the imaginary straight-toothed spur gear are known, when the imaginary straight-toothed spur gear rotates for one circle, the angular speed of the non-circular-face gear 2 completes one period of change, and the speed reduction ratio i of the imaginary straight-toothed spur gear and the non-circular-face gear 2 is reducedj1, i.e. the transmission ratio of the imaginary spur gear to the non-circular face gear 2 is a transmission ratio ibThe gear ratio and the reduction ratio of the small cylindrical gear 1 and the non-circular face gear 2 are respectively ib＝r2/rbAnd ij＝rb/r1＝Z2/Z1In the formula, r2Is the radial direction of the projected curve of the pitch curve 4 of the non-circular face gear on the bottom surface of the pitch cone, r1Is the pitch cylinder radius, r, of the small cylindrical gear 1bThe radius of the imaginary cylindrical gear pitch cylinder is shown.
The change rule of the transmission ratio when the axes of the small cylindrical gear 1 and the non-circular face gear 2 are intersected is explained by comparing four groups of data
(1) Taking epsilon as 0.15, n as 1, m as 2mm, Z1＝17，Z2At 70, λ is 80 °. When the non-circular gear 2 rotates for one circle, the curve of the transmission ratio of the small cylindrical gear 1 and the non-circular gear 2 is shown as a single-period solid line in fig. 5, and the transmission ratio is divided into a reduction ratio ijAnd a speed change ratio ibAvailable gear ratio curves as in FIG. 6Shown in solid lines. The transmission ratio effect and the reduction ratio of the intersecting shaft non-circular surface gear pair are ijThe transmission effect of the 70/17 bevel gear pair and the transmission ratio is the same as that of the non-circular gear pair in series connection as shown by the solid line in fig. 6.
(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 gear pitch curve 4 as 2, keeping other parameters unchanged, and keeping Z as270, 0.15, 80. When the non-circular face gear rotates for one circle 2, the curve of the transmission ratio of the small cylindrical gear 1 and the non-circular face gear 2 is shown as a solid line with the period of 2 in fig. 5, and the transmission ratio i12The variation range of (a) is the same as the first set of data, the number of cycles of the transmission ratio becomes 2 with the number of cycles of the non-circular face gear pitch curve 4, and the reduction ratio ijThis means that the number of cycles of the non-circular pitch curve 4 in the transmission can control the transmission ratio ibThe number of cycles of (a).
(3) The small cylindrical gear 1 is kept unchanged, Z1 is taken as 17, m is taken as 2mm, the eccentricity epsilon of the non-circular face gear pitch curve 4 is changed as 0.2, other parameters are kept unchanged, and Z is taken as270, n1, λ 80 °. When the non-circular gear 2 rotates one circle, the curve of the gear ratio of the small cylindrical gear 1 and the non-circular gear 2 is shown by the dotted line in fig. 6, and the reduction ratio i is compared with the first set of datajWith constant period of speed ratio, speed ratio ibThe eccentricity of the non-circular gear pitch curve 4 in the transmission controls the transmission ratio ibThe range of (1).
(4) The pitch curve 4 of the non-circular face gear is not changed, epsilon is 0.15, n is 1, Z270 DEG, 80 DEG, and the number of teeth Z of the small cylindrical gear 1 is changed118, constant modulus, m 2 mm. When the non-circular gear 2 rotates for one circle, the transmission ratio of the small cylindrical gear 1 and the non-circular gear 2 is shown by a dotted line in fig. 5, compared with the first group of data, the period of the transmission ratio curve is unchanged, but the maximum value and the minimum value are changed, and the reduction ratio i of the two groups of data is calculatedjThe change in the ratio curve, which is caused by the change in the reduction ratio, is known from the change in the values, which means that in the transmission the reference circle radius of the small cylindrical gear 1 determines the reduction ratio i of the transmissionjThe size of (2).
When the pitch curve 4 of the non-circular face gear selects other forms of curves, and the included angle between two gear shafts is other values, the transmission ratio rule is the same as that of the non-circular face gear transmission mechanism with the first-order transmission ratio function: the change ratio i of the transmission mechanism can be controlled by changing the pitch curve 4 of the non-circular face gearbThe reduction ratio i of the transmission mechanism can be controlled by changing the number of teeth of the small cylindrical gear 1j. In summary, the intersecting axis closed non-circular face gear transmission mechanism composed of the ordinary straight-tooth small cylindrical gear 1 and the non-circular face gear 2 can realize the reduction-speed change composite transmission with any combination of the speed reduction ratio between intersecting axes, the speed change ratio period and the speed change ratio range according to practical application.
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.
Claims (5)
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 bkTo the transmission ratio coefficientThe transmission ratio coefficients are all 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.
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| CN114382839B (en) * | 2020-10-17 | 2024-03-22 | 杨文通 | Special-shaped gear pair with transmission ratio being piecewise continuous function |
| CN112883485B (en) * | 2021-01-22 | 2022-04-01 | 燕山大学 | Non-circular face gear limited slip differential and escaping operation method |
| CN112883513B (en) * | 2021-02-02 | 2024-03-12 | 上海三一重机股份有限公司 | Mounting point design method for telescopic piece |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102518756A (en) * | 2011-12-23 | 2012-06-27 | 重庆大学 | Compound transmission face gear pair with transmission ratio variable |
| CN102954152A (en) * | 2011-08-17 | 2013-03-06 | 通用汽车环球科技运作有限责任公司 | Double involute pinion-face gear drive system |
| CN104500654A (en) * | 2014-11-26 | 2015-04-08 | 燕山大学 | Deceleration and speed change integrated face gear pair and processing method thereof |
| CN108629120A (en) * | 2018-05-08 | 2018-10-09 | 武汉理工大学 | The prediction technique of not rounded stud wheel Gear Shaping cutting force |
| CN109993464A (en) * | 2019-04-24 | 2019-07-09 | 合肥工业大学 | Reduce the machining parameters optimization method of hypoid gear installation error susceptibility |
-
2019
- 2019-11-21 CN CN201911150818.0A patent/CN110848332B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102954152A (en) * | 2011-08-17 | 2013-03-06 | 通用汽车环球科技运作有限责任公司 | Double involute pinion-face gear drive system |
| CN102518756A (en) * | 2011-12-23 | 2012-06-27 | 重庆大学 | Compound transmission face gear pair with transmission ratio variable |
| CN104500654A (en) * | 2014-11-26 | 2015-04-08 | 燕山大学 | Deceleration and speed change integrated face gear pair and processing method thereof |
| CN108629120A (en) * | 2018-05-08 | 2018-10-09 | 武汉理工大学 | The prediction technique of not rounded stud wheel Gear Shaping cutting force |
| CN109993464A (en) * | 2019-04-24 | 2019-07-09 | 合肥工业大学 | Reduce the machining parameters optimization method of hypoid gear installation error susceptibility |
Non-Patent Citations (3)
| Title |
|---|
| "study on the design of non-circular gear and it"s equivalent gear train based on numerical method";Wu Yujuan等;《IEEE》;20100430;第1-4页 * |
| "减变速一体化齿轮的传动原理与接触特性";王国会;《中国优秀硕士学位论文全文数据库 工程科技第II辑》;20181231;C029-93页 * |
| "正交非圆面齿轮副的传动设计与特性分析";龚海;《中国优秀硕士学位论文全文数据库 工程科技第II辑》;20130331;C029-73页 * |
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