CN107489754B - Even-transmission gear and its active designs method - Google Patents

Even-transmission gear and its active designs method Download PDF

Info

Publication number
CN107489754B
CN107489754B CN201710879115.6A CN201710879115A CN107489754B CN 107489754 B CN107489754 B CN 107489754B CN 201710879115 A CN201710879115 A CN 201710879115A CN 107489754 B CN107489754 B CN 107489754B
Authority
CN
China
Prior art keywords
gear
speed
acceleration
section
motion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN201710879115.6A
Other languages
Chinese (zh)
Other versions
CN107489754A (en
Inventor
王建
张�杰
冯勇
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nanjing Institute of Technology
Original Assignee
Nanjing Institute of Technology
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nanjing Institute of Technology filed Critical Nanjing Institute of Technology
Priority to CN201710879115.6A priority Critical patent/CN107489754B/en
Publication of CN107489754A publication Critical patent/CN107489754A/en
Application granted granted Critical
Publication of CN107489754B publication Critical patent/CN107489754B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/08—Profiling
    • F16H55/084—Non-circular rigid toothed member, e.g. elliptic gear
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H2057/0087—Computer aided design [CAD] specially adapted for gearing features ; Analysis of gear systems

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • General Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Theoretical Computer Science (AREA)
  • Computational Mathematics (AREA)
  • Mathematical Analysis (AREA)
  • Mathematical Optimization (AREA)
  • Pure & Applied Mathematics (AREA)
  • Computer Hardware Design (AREA)
  • Evolutionary Computation (AREA)
  • Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)
  • Gears, Cams (AREA)

Abstract

The invention discloses a kind of even-transmission gear and its active designs methods, belong to mechanical transmission fields.Even-the transmission gear is divided into I type, II type ... N-type.So-called I type is even-transmission gear, during referring to driving gear uniform rotation one week, driven gear also rotates a cycle, and make a constant speed, primary acceleration and a retarded motion, II type is even-during transmission gear refers to driving gear uniform rotation one week, driven gear also rotates a cycle, and make twice constant speed, accelerate twice and retarded motion twice, and so on can define other kinds of even-transmission gear；The present invention also provides the active designs methods: the angular speed and angular acceleration curve of driven gear in previously given a pair of non-circular gear, according to numerical computation method and the non-circular gear theory of engagement, the pitch curve of active designs non-circular gear, it realizes in the design phase, by changing the kinetic characteristic of driven gear, the pitch curve shape of non-circular gear directly, effectively control.

Description

Uniform-speed change gear and active design method thereof
Technical Field
The invention belongs to the technical field of mechanical transmission, and particularly relates to a uniform-speed change gear and an active design method thereof.
Background
In the transmission of a pair of conjugated non-circular gears, the driving gear generally rotates at a constant speed, the driven gear rotates at a variable speed, and the motion characteristic of the non-circular gears is determined by the pitch curve. At present, the design methods of the pitch curve of the non-circular gear mainly comprise two methods, namely designing the pitch curve according to a required transmission ratio function and designing the pitch curve according to a function reproduced according to requirements. Neither of these two design methods can achieve the following functions: 1) actively designing a pitch curve of the non-circular gear by giving an angular velocity curve and an angular acceleration curve of the non-circular gear; 2) during design, the pitch curve shape is actively controlled by changing the angular speed and angular acceleration curves of the non-circular gear.
Disclosure of Invention
The invention provides a uniform-speed gear and an active design method thereof, wherein the uniform-speed gear is divided into an I type and an II type … N type. The type I uniform-speed change gear refers to that the driven gear also rotates for a period and performs constant speed, acceleration and deceleration motions once in the process that the driving gear rotates for a circle at a constant speed, and the type II uniform-speed change gear refers to that the driven gear also rotates for a period and performs constant speed, acceleration and deceleration motions twice in the process that the driving gear rotates for a circle at a constant speed, and the rest can define other types of uniform-speed change gears.
The invention also discloses an active design method, which comprises the following steps: the method comprises the steps of presetting the angular velocity and angular acceleration curves of a driven gear in a pair of non-circular gears, actively designing the pitch curve of the non-circular gears according to a numerical calculation method and a non-circular gear meshing principle, and directly and effectively controlling the pitch curve shape of the non-circular gears by changing the motion characteristics of the driven gear in the design stage. An active design method for a level-shift gear comprising the steps of:
s1, the pitch curve equation for the driving gear and the driven gear of the non-circular gear can be expressed as:
wherein,is the corner of the driving gear and is provided with a gear wheel,is the angle of rotation of the driven gear, i12Is a transmission ratio;
s2, presetting the curve shapes of the angular acceleration and the angular speed of the driven gear, α2And ω2Angular acceleration and angular velocity of the driven gear, respectively. Segmenting a given curve into a constant-speed motion segment, an acceleration motion segment and a deceleration motion segment, and in one period,the section is a constant-speed motion section,the section is an acceleration motion section,the section is a deceleration movement section, the three sections respectively correspond to the constant-speed movement section AB, the acceleration movement section BC and the deceleration movement section CA of the non-circular gear, namely, the driven gear performs constant-speed, acceleration and deceleration movement once in the process of one rotation of the driving gear.
And S3, deriving expressions of angular speed, angular acceleration and transmission ratio of the constant velocity motion segment, the acceleration motion segment and the deceleration motion segment:
for constant velocity motion segment
Where k is a coefficient.
For the accelerated motion segmentThe angular acceleration, angular velocity and transmission ratio curves can be expressed by the following polynomials:
wherein, b0、b1、b2、b3、b4、b5Is a polynomial coefficient.
Likewise, for the deceleration movement sectionCan be expressed as:
wherein d is0、d1、d2、d3、d4、d5For the sake of distinction, the respective parameters of the constant velocity motion section, the acceleration motion section and the deceleration motion section are denoted by superscripts a, b and d, respectively.
S4, from the predetermined angular velocity and angular acceleration curves, the following constraint equation can be established:
due to the acceleration curve inTakes a maximum value of α2maxThen the following holds:
similarly, for the deceleration motion segment, the acceleration curve isTaking the minimum value, setting the minimum value as α2minIs obtained by
For the angular velocity profile, the following holds:
because the rotation periods of the driving gear and the driven gear are the same, when the driving gear rotates for one circle, the sum of the rotation angles of the constant-speed motion section, the acceleration motion section and the deceleration motion section of the corresponding driven gear is 2 pi, namely
Wherein,andthe rotation angles of the driven gear corresponding to the constant-speed motion section, the acceleration motion section and the deceleration motion section are respectively expressed as follows:
s5, substituting equations (3) to (11) into equations (12) to (17), and writing them in matrix form:
A·xT＝BT (18)
wherein, a, x and B may be represented as:
x＝[b0 b1 b2 b3 b4 b5 d0 d1 d2 d3 d4 d5]
B＝[0 0 αmax 0 kω1 0 0 αmin 0 kω1 0 2π-kθ1]
s6, using the matrix,presetting a central distance a and an angular speed omega of the rotation of the driving gear1Coefficient k, maximum value of angular acceleration α2maxMinimum value α2minAnd angle theta1、θ2、θ3、θ4、θ5The polynomial coefficient value can be obtained, and the polynomial coefficient value is substituted into the equations (1) and (2), and the pitch curve of each motion segment of the uniform-speed change gear can be obtained by using MATLAB software.
S7, the pitch curve length calculation formula of the driving gear in the I-shaped uniform-speed gear is as follows:
wherein r is1 a、r1 bAnd r1 dRespectively representing the pitch curve radial directions corresponding to the constant speed motion section, the acceleration motion section and the deceleration motion section.
In designing, the requirement that the pitch curve length is equally divided by the whole tooth form must be satisfied at the same time, and the pitch curve length of the I-type uniform-speed gear can also be expressed as follows:
L＝πmz (20)
wherein m is the number of gear teeth and z is the gear module.
From equations (1), (19) and (20), the center-to-center distance of the gears can be determined.
S8, designing the tooth shape of the uniform-speed gear by a reduced tooth shape method.
The uniform-speed change gear and the active design method thereof provided by the invention can effectively design the pitch curve of the non-circular gear with special requirements, and also can design the pitch curve of the non-circular gear with special motion rules when the non-circular gear is connected with other mechanisms such as a sliding block and the like in series, so that the pitch curve of the non-circular gear is directly and effectively controlled by changing the motion characteristic of the driven gear in the design stage.
Drawings
Fig. 1 is a graph of angular velocity and angular acceleration of a driven gear in a pre-defined type i soaking-shifting gear.
FIG. 2 is a schematic view of a type I soaking-shifting gear.
FIG. 3 is a pitch chart of a driving gear of the type I uniform variable speed gear.
FIG. 4 is a pitch graph of a type I soaking-shifting gear driven gear.
FIG. 5 is a graph of a type II uniform-ratio gear drive gear pitch.
FIG. 6 is a pitch graph of a type II step-up gear driven gear.
Fig. 7 is an assembly view of a type i step gear.
Fig. 8 is an assembly view of a type ii step gear.
Fig. 9 is a graph of the angular velocity and angular acceleration of a type i soaking dog-pinion driven gear.
Detailed Description
The invention is further illustrated by the following figures and examples. It is to be understood that the specific embodiments described herein are merely illustrative of the invention and are not limiting of the invention.
S1, the pitch curve equation for the driving gear and the driven gear of the non-circular gear can be expressed as:
wherein,is the corner of the driving gear and is provided with a gear wheel,is the angle of rotation of the driven gear, i12Is a transmission ratio;
s2, curve shapes of the angular acceleration and the angular velocity of the driven gear are preset, as shown in fig. 1. Wherein,angle of rotation of the driving gear, α2And ω2Angular acceleration and angular velocity of the driven gear, respectively. Segmenting a given curve into a constant-speed motion segment, an acceleration motion segment and a deceleration motion segment, and in one period,the section is a constant-speed motion section,the section is an acceleration motion section,the section is a deceleration movement section, the three sections respectively correspond to the constant-speed movement section, the acceleration movement section and the deceleration movement section of the non-circular gear, namely, the driven gear performs constant-speed, acceleration and deceleration movement once in the process of one rotation of the driving gear. The corresponding structural schematic diagram of the uniform-speed-changing gear is shown in fig. 2, wherein AB is a constant-speed motion section, BC is an acceleration motion section, and CA is a deceleration motion section.
And S3, deriving expressions of angular speed, angular acceleration and transmission ratio of the constant velocity motion segment, the acceleration motion segment and the deceleration motion segment:
for constant velocity motion segment
Where k is a coefficient.
For the accelerated motion segmentThe angular acceleration, angular velocity and transmission ratio curves can be expressed by the following polynomials:
wherein, b0、b1、b2、b3、b4、b5Is a polynomial coefficient.
Likewise, for the deceleration movement sectionCan be expressed as:
wherein d is0、d1、d2、d3、d4、d5For the sake of distinction, the parameters of the constant velocity motion segment, the acceleration motion segment and the deceleration motion segment are respectively denoted by the labels "a", "b" and "d".
S4, from the predetermined angular velocity and angular acceleration curves, the following constraint equation can be established
Due to the acceleration curve inTakes a maximum value of α2maxThen the following holds:
similarly, for the deceleration motion segment, the acceleration curve isTaking the minimum value, setting the minimum value as α2minIs obtained by
For the angular velocity profile, the following holds:
because the rotation periods of the driving gear and the driven gear are the same, when the driving gear rotates for one circle, the sum of the rotation angles of the constant-speed motion section, the acceleration motion section and the deceleration motion section of the corresponding driven gear is 2 pi, namely
Wherein,andthe rotation angles of the driven gear corresponding to the constant-speed motion section, the acceleration motion section and the deceleration motion section are respectively expressed as follows:
s5, substituting equations (3) to (11) into equations (12) to (17), and writing them in matrix form:
A·xT＝BT (18)
wherein, a, x and B may be represented as:
x＝[b0 b1 b2 b3 b4 b5 d0 d1 d2 d3 d4 d5]
B＝[0 0 αmax 0 kω1 0 0 αmin 0 kω1 0 2π-kθ1]
s6, using the matrix, presetting the center distance a and the angular speed omega of the rotation of the driving gear1Coefficient k, maximum value of angular acceleration α2maxMinimum value α2minAnd angle theta1、θ2、θ3、θ4、θ5The polynomial coefficient value can be obtained, and the polynomial coefficient value is substituted into the equations (1) and (2), and the pitch curve of each motion segment of the uniform-speed change gear can be obtained by using MATLAB software.
S7, the pitch curve length calculation formula of the driving gear in the I-shaped uniform-speed gear is as follows:
wherein r is1 a、r1 bAnd r1 dRespectively representing the pitch curve radial directions corresponding to the constant speed motion section, the acceleration motion section and the deceleration motion section.
In designing, the requirement that the pitch curve length is equally divided by the whole tooth form must be satisfied at the same time, and the pitch curve length of the I-type uniform-speed gear can also be expressed as:
L＝πmz (20)
wherein m is the number of gear teeth and z is the gear module.
From equations (1), (19) and (20), the center-to-center distance of the gears can be determined.
S8, designing the tooth shape of the uniform-speed gear by a reduced tooth shape method.
The present invention provides 1 group of design examples of I-type and II-type uniform-speed gears, respectively, and the initial data for constructing the pitch curve is shown in Table 1, wherein the angle of the II-type uniform-speed gear only provides data in a half period ([0, π ]), and the data in the other half period [ π,2 π ] is the same as the first half period.
TABLE 1 initial set of smooth-change gear data
According to the design principle, MATLAB software is utilized to establish a pitch curve of the uniform-speed change gear. The pitch curves for type i soaking gears obtained from the data in table 1 are shown in fig. 3 and 4, and the pitch curves for type ii soaking gears are shown in fig. 5 and 6. The involute tooth profile of the uniform-speed gear is generated by a reduced tooth profile method, the two pairs of gears are assembled, and the assembled drawings are shown in fig. 7 and 8 after verification that no meshing interference exists. Fig. 9 shows the angular velocity and angular acceleration curves of the type I step gear.
As can be seen from fig. 3 to 9:
(1) the curves of the angular velocity and the angular acceleration obtained by checking are consistent with the preset shapes, which shows that the design method is reasonable.
(2) By varying parameters of predetermined angular velocity and acceleration profiles, e.g. centre-to-centre distance a, angular velocity ω of rotation of the drive gear1Coefficient k, maximum value of angular acceleration α2maxMinimum value α2minThe tooth number and the modulus of the gear can control the pitch curve shape of the uniform-speed gear.
(3) By varying the angle theta1、θ2、θ3、θ4、θ5The value of the constant-speed gear can control the gear rotation angle corresponding to the constant speed, acceleration and deceleration motion sections of the constant-speed gear, and can also design a pitch curve of the constant-speed gear with any transmission rule in the working section according to other actual requirements.
(4) The active design method of the non-circular gear is designed through the angular velocity curve and the angular acceleration curve of the preset driven gear, the pitch curve of the non-circular gear with special requirements can be effectively designed according to actual requirements, the pitch curve of the non-circular gear with special motion rules can also be designed when the non-circular gear is connected with other mechanisms such as a sliding block and the like in series, the pitch curve of the non-circular gear is directly and effectively controlled by changing the motion characteristic of the driven gear in the design stage, and the design method has popularization and application prospects in main motion mechanisms with constant motion requirements such as a precision press machine and a gear shaper.
The foregoing is considered as illustrative of the preferred embodiments of the invention and technical principles employed. It will be understood by those skilled in the art that the present invention is not limited to the particular embodiments described herein, but is capable of various obvious changes, rearrangements and substitutions as will now become apparent to those skilled in the art without departing from the scope of the invention. Therefore, although the present invention has been described in greater detail by the above embodiments, the present invention is not limited to the above embodiments, and may include other equivalent embodiments without departing from the spirit of the present invention, and the scope of the present invention is determined by the scope of the appended claims.

Claims (2)

1. An active design method for a uniform-speed change gear is characterized by comprising the following steps:
s1, a pitch curve equation of a driving gear and a driven gear of the non-circular gear is given, and is expressed as follows:
wherein,is the corner of the driving gear and is provided with a gear wheel,is the angle of rotation of the driven gear, i12Is a transmission ratio;
s2, presetting the curve shapes of the angular acceleration and the angular speed of the driven gear, α2And ω2The angular acceleration and the angular velocity of the driven gear respectively; segmenting a given curve into a constant-speed motion segment, an acceleration motion segment and a deceleration motion segment, and in one period,the section is a constant-speed motion section,the section is an acceleration motion section,the section is a deceleration movement section, the three sections respectively correspond to a constant-speed movement section AB, an acceleration movement section BC and a deceleration movement section CA of the non-circular gear, namely, the driven gear performs constant-speed, acceleration and deceleration movement once in the process of one rotation of the driving gear;
and S3, deriving expressions of angular speed, angular acceleration and transmission ratio of the constant velocity motion segment, the acceleration motion segment and the deceleration motion segment:
for constant velocity motion segment
Wherein k is a coefficient;
for the accelerated motion segmentThe angular acceleration, angular velocity and transmission ratio curves can be expressed by the following polynomials:
wherein, b0、b1、b2、b3、b4、b5Is a polynomial coefficient;
likewise, for the deceleration movement sectionCan be expressed as:
wherein d is0、d1、d2、d3、d4、d5Representing each parameter of the constant velocity motion section, the acceleration motion section and the deceleration motion section by superscripts a, b and d respectively for polynomial coefficients;
s4, from the predetermined angular velocity and angular acceleration curves, the following constraint equation is established:
due to the acceleration curve inTakes a maximum value of α2maxThen the following holds:
similarly, for the deceleration motion segment, the acceleration curve isTaking the minimum value, setting the minimum value as α2minIs obtained by
For the angular velocity profile, the following holds:
because the rotation periods of the driving gear and the driven gear are the same, when the driving gear rotates for one circle, the sum of the rotation angles of the constant-speed motion section, the acceleration motion section and the deceleration motion section of the corresponding driven gear is 2 pi, namely
Wherein,andthe rotation angles of the driven gear corresponding to the constant-speed motion section, the acceleration motion section and the deceleration motion section are respectively expressed as follows:
s5, substituting equations (3) to (11) into equations (12) to (17), and writing them in matrix form:
A·xT＝BT (18)
wherein, a, x and B may be represented as:
x＝[b0 b1 b2 b3 b4 b5 d0 d1 d2 d3 d4 d5]
B＝[0 0 αmax 0 kω1 0 0 αmin 0 kω1 0 2π-kθ1]
s6, using the matrix, presetting the center distance a and the angular speed omega of the rotation of the driving gear1Coefficient k, maximum value of angular acceleration α2maxMinimum value α2minAnd angle theta1、θ2、θ3、θ4、θ5The polynomial coefficient value can be obtained, the polynomial coefficient value is substituted into the equations (1) and (2), and the pitch curve of each motion segment of the uniform-speed change gear can be obtained by using MATLAB software;
s7, the pitch curve length calculation formula of the driving gear in the I type uniform-speed gear is as follows:
wherein r is1 a、r1 bAnd r1 dRespectively representing pitch curve radial directions corresponding to the constant speed motion section, the acceleration motion section and the deceleration motion section;
in designing, the requirement that the pitch curve length is equally divided by the whole tooth form must be satisfied at the same time, and the pitch curve length of the I-type uniform-speed gear can also be expressed as follows:
L＝πmz (20)
wherein m is the number of gear teeth, and z is the gear module;
according to the formulas (1), (19) and (20), the center distance of the gears can be determined;
and S8, designing the tooth shape of the uniform-speed changing gear by a reduced tooth shape method, and finishing the design of the uniform-speed changing gear.
2. A smooth-variable gear designed by the method of claim 1, wherein: the driven gear also rotates for a period in the process of one circle of uniform rotation of the driving gear, and at least comprises a constant-speed motion section and a variable-speed motion section in the process of one circle of rotation.
CN201710879115.6A 2017-09-26 2017-09-26 Even-transmission gear and its active designs method Active CN107489754B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201710879115.6A CN107489754B (en) 2017-09-26 2017-09-26 Even-transmission gear and its active designs method

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201710879115.6A CN107489754B (en) 2017-09-26 2017-09-26 Even-transmission gear and its active designs method

Publications (2)

Publication Number Publication Date
CN107489754A CN107489754A (en) 2017-12-19
CN107489754B true CN107489754B (en) 2019-08-16

Family

ID=60652141

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201710879115.6A Active CN107489754B (en) 2017-09-26 2017-09-26 Even-transmission gear and its active designs method

Country Status (1)

Country Link
CN (1) CN107489754B (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021063202A1 (en) * 2019-09-30 2021-04-08 苏州向势机械技术有限公司 Double-piston lever efficient engine and acting control method therefor
CN113973585B (en) * 2021-09-24 2023-08-22 江苏大学 Threshing and cleaning device integrating inertia and electrostatic field and combine harvester
CN114876305B (en) * 2022-04-27 2023-06-02 上海工程技术大学 Side-opening type aircraft cabin door constant-moment electric lifting mechanism driven by non-circular gears

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5251507A (en) * 1989-04-11 1993-10-12 Mitsubishi Denki K.K. Non-circular gear pair
JP3486321B2 (en) * 1997-05-29 2004-01-13 三菱重工業株式会社 Non-circular gear drive
CN101463889A (en) * 2008-05-26 2009-06-24 北京锋源技术有限公司 Non-circular gear transmission and its transmission mechanism
CN104626829A (en) * 2014-12-08 2015-05-20 江西理工大学 Cam profile line generating instrument and generating method
CN106184448A (en) * 2016-09-29 2016-12-07 浙江工业职业技术学院 A kind of mechanism that leaps on one leg driven based on Pascal curve non-circular gear
CN206036137U (en) * 2016-06-21 2017-03-22 兰州理工大学 Non - round gear drive characteristic testing arrangement
CN107066678A (en) * 2017-01-22 2017-08-18 北京工业大学 Mesh impact model with base pitch error

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5251507A (en) * 1989-04-11 1993-10-12 Mitsubishi Denki K.K. Non-circular gear pair
JP3486321B2 (en) * 1997-05-29 2004-01-13 三菱重工業株式会社 Non-circular gear drive
CN101463889A (en) * 2008-05-26 2009-06-24 北京锋源技术有限公司 Non-circular gear transmission and its transmission mechanism
CN104626829A (en) * 2014-12-08 2015-05-20 江西理工大学 Cam profile line generating instrument and generating method
CN206036137U (en) * 2016-06-21 2017-03-22 兰州理工大学 Non - round gear drive characteristic testing arrangement
CN106184448A (en) * 2016-09-29 2016-12-07 浙江工业职业技术学院 A kind of mechanism that leaps on one leg driven based on Pascal curve non-circular gear
CN107066678A (en) * 2017-01-22 2017-08-18 北京工业大学 Mesh impact model with base pitch error

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
主从动轮具有相同形状的非圆齿轮副设计方法;张瑞，刘武发，吴序堂;《机械设计》;20110630;第28卷(第6期);第46-50页

Also Published As

Publication number Publication date
CN107489754A (en) 2017-12-19

Similar Documents

Publication Publication Date Title
CN107489754B (en) Even-transmission gear and its active designs method
CN107588177B (en) Cycloidal pin gear harmonic drive device
CN110879910B (en) Closed non-circular gear pair with transmission ratio of Fourier series
CN101251181B (en) Helical teeth elliptic gear as well as method for three-dimensional model-building accurately and entity shaping
CN104500654B (en) One kind subtracts the integrated face gear pair of speed change and its processing method
WO2017024749A1 (en) Line gear mechanism having variable transmission ratio
CN103443459B (en) For the method for profile of tooth of the inner ring and outer ring that produce gear ring machine and the gear ring that utilizes the method to produce
CN111120622B (en) Modified wave cam and design method thereof, wave generator and wave reducer
CN112392935B (en) Harmonic speed reducer
CN110848332B (en) Intersecting-axis non-circular-face gear transmission mechanism
CN106695023B (en) A kind of processing method of circulating ball type no-load voltage ratio diverter gear pair rack tooth profile
CN104819267A (en) Harmonic gear device adopting non-interference and wide range meshing tooth profile
CN105508521A (en) High-contact-ratio internal-gearing cycloidal gear mechanism
CN204985583U (en) Variable ratio line gear
KR100397640B1 (en) A booster combined with decelerator
CN107355524A (en) A kind of differential differential speed reducer
JP6936367B2 (en) High ratio differential reducer
JP4319344B2 (en) Speed reducer series
CN106541186B (en) A kind of processing method of circulating ball type no-load voltage ratio diverter gear pair tooth fan flank profil
CN105844078B (en) Active design method of low-pulsation gear pump
CN101963206B (en) Regular polygon axial distribution-based micro speed reducer
CN105605192A (en) Optimization method of two-stage straight tooth planet gear
CN205896052U (en) Elasticity does not have return difference 3Z planet gear
JP4811676B2 (en) Gear using gear teeth and gear transmission device
CN110671484B (en) Design method of variable-speed-ratio coaxial-surface non-circular-line gear

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant