CN104615800B - The design method and its transmission device of alternating axis non-circular gear - Google Patents

The design method and its transmission device of alternating axis non-circular gear Download PDF

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CN104615800B
CN104615800B CN201410707936.8A CN201410707936A CN104615800B CN 104615800 B CN104615800 B CN 104615800B CN 201410707936 A CN201410707936 A CN 201410707936A CN 104615800 B CN104615800 B CN 104615800B
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circular gear
alternating axis
axis non
cutter
alternating
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CN104615800A (en
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华林
郑方焱
韩星会
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Wuhan University of Technology WUT
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Wuhan University of Technology WUT
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Abstract

A kind of design method and its transmission device of alternating axis non-circular gear, according to space meshing principle and the method for relative motion, have obtained the design method of alternating axis non-circular gear, this method has the characteristics of simple and practical.Alternating axis non-circular gear drive device frame is provided with the input shaft and output shaft of spatial vertical interlaced arrangement, input alternating axis non-circular gear and output alternating axis non-circular gear, input alternating axis non-circular gear and the non-circular gear intermeshing of output alternating axis are fixed with by keyway respectively on input shaft and output shaft.One-level non-circular gear drive is use only, that is, realizes the variable ratio transmission between spatial intersecting axle, there is simple in construction, transmission efficiency, the features such as rigidity of support is good.

Description

The design method and its transmission device of alternating axis non-circular gear
Technical field
The present invention relates to a kind of design method of gear and mechanical driving device, more particularly to a kind of non-knuckle-tooth of alternating axis Take turns design method and its transmission device.
Background technology
Inside and outside engagement non-circular gear drive can transmit the gear ratio motion of parallel between centers, and not rounded bevel gear can transmit Gear ratio is moved between concurrent aces.If transmit the gear ratio motion of spatial intersecting axle, it is necessary to combine both above-mentioned, structure Into secondary transmission, it is driven chain length, and complicated, efficiency is low.
Meanwhile not rounded bevel gear is intersected due to the axis of gear, general gear will be installed in a cantilever fashion in structure, It gear shaft rigidity deficiency, perturbs the engagement of very big, the serious influence flank of tooth, produces shock and vibration, shadow in high-speed motion Ring High Speed Dynamics performance.
Alternating axis non-circular gear drive and its design principle can draw by spatial conjugate basic definition, but due to its mathematical modulo Type possesses suitable complexity, and its axode is space undeveloped curved surface, and the helical angle of the generation curved surface of its flank profil shows non- Often big is non-linear, and envelope cutter is difficult to build.
The content of the invention
The features such as it is an object of the invention to provide one kind to have simple in construction, transmission efficiency, and rigidity of support is good is interlocked The design method of axle non-circular gear.
The step of its design method, is as follows：
First, input alternating axis non-circular gear is obtained according to space meshing principle and exports the instantaneous axis of alternating axis non-circular gear Face；
2nd, according to the spiral situation of axode, the profile geometry of envelope cutter is determined；
3rd, the movement velocity of cutter is solved；
4th, modulus of the cutter on footpath not in the same direction is determined；
5th, the envelope solution of alternating axis non-circular gear tooth profile is obtained with above-mentioned cutter model envelope；
6th, with numerical method, the flank profil of alternating axis non-circular gear is solved；
7th, according to flank profil data, three-dimensional modeling, analysis, and production and processing are carried out.
It is specifically by such scheme, the step of described design method：
The first step, input the axode equation and output alternating axis non-circular gear axode equation point of alternating axis non-circular gear It is not：
In formula：
A is the length of the axis minimum common vertical line section of two alternating axis non-circular gears, i.e. wheelbase.
Σ is the folded acute angle of the axis of two alternating axis non-circular gears, i.e. crossed axis angle.
T be axode to footpath parameter, axode can regard the set that instantaneous axis line is formed under footpath not in the same direction as.
To input the corner of alternating axis non-circular gear, in the range of 0~2 π.
For transmission ratio function, the velocity variations relation of wheel for inputting and output wheel is characterized, it is wheel for inputting corner's Function, its form can be SIN functions, exponential function, direct proportion function.
To export the corner of alternating axis non-circular gear, it isFunction, in the range of 0~2 π.Its calculating formula is such as Under：
Second step, the helix parameter of axode are
3rd step, the movement velocity of cutter are：
In formula,For the movement velocity of axode,For axode and the common movement velocity of cutter.
WhenWhen,
4th step, modulus of the cutter on footpath not in the same direction are：
S in formulatTotal arc length that (2 π, t) are passed through by cutter, can be obtained by arc integral formula：
Z is the number of teeth of gear, and by intensity, registration synthesis determines.
5th step, input alternating axis non-circular gear, the envelope solution of output alternating axis non-circular gear tooth profile are respectively：
In formula：raFor the cutter tooth-profile of above-mentioned solution. For each corresponding transformation matrix.
6th step, with numerical method, solve the flank profil of alternating axis non-circular gear.
For the numerical method based on the solution to mesh equation, mesh equation shows as the normal vector n of the cutter flank of tootha(s) and Movement velocity of the flank of tooth with respect to cutterWhereinBased on the derivation to Envelope equation：
In alternating axis non-circular gear is inputted：
In alternating axis non-circular gear is exported：
The performance of mesh equation：Wheel for inputting：
Output wheel：
The coordinate data of the flank of tooth is can obtain by solution of the numerical method to mesh equation.
7th step, according to flank profil data, carry out three-dimensional modeling, analysis, and production and processing.
It is non-the present invention also aims to provide a kind of alternating axis of the design method design using alternating axis non-circular gear Knuckle-tooth wheel transmission device, it can be driven by one-stage gear and realize that the gear ratio of spatial intersecting between centers moves transmission, there is knot The features such as structure is simple, transmission efficiency, and rigidity of support is good.
The present invention realizes that the technical scheme of above-mentioned purpose is：Including a frame, it is characterised in that：Frame is provided with sky Between the vertical interlaced input shaft and output shaft arranged, it is non-that input alternating axis is fixed with by keyway respectively on input shaft and output shaft Knucle-gear and output alternating axis non-circular gear, input alternating axis non-circular gear and the non-circular gear intermeshing of output alternating axis.
By such scheme, the length velocity relation of described input shaft and output shaft meets specific transmission ratio function；Power drives Driven input shaft uniform rotation, by one-level alternating axis non-circular gear drive, obtaining specific transmission ratio function on output shaft will The movement output asked.
Beneficial effects of the present invention：According to space meshing principle and the method for relative motion, the non-knuckle-tooth of alternating axis has been obtained The design method of wheel, this method have the characteristics of simple and practical.It is not rounded that alternating axis non-circular gear drive device use only one-level Gear drive, that is, the variable ratio transmission between spatial intersecting axle is realized, there is simple in construction, transmission efficiency, rigidity of support The features such as good；
Brief description of the drawings
Fig. 1 is the structural representation of the alternating axis non-circular gear drive device of the present invention.
Fig. 2 is the transmission ratio function of alternating axis non-circular gear of the present invention.
Fig. 3 is the axode schematic diagram of present invention input alternating axis non-circular gear.
Fig. 4 is the axode schematic diagram of present invention output alternating axis non-circular gear.
Fig. 5 is the sinusoidal instrument rack end surface shape schematic diagram of the present invention.
The envelope solution schematic diagram of alternating axis non-circular gear tooth profile is inputted when Fig. 6 is t=35 of the present invention.
The envelope solution schematic diagram of alternating axis non-circular gear tooth profile is exported when Fig. 7 is t=35 of the present invention.
The threedimensional model schematic diagram of Fig. 8 present invention input alternating axis non-circular gears.
The threedimensional model schematic diagram of Fig. 9 present invention output alternating axis non-circular gears.
Embodiment
The design method of alternating axis non-circular gear comprises the following steps：With transmission ratio function Crossed axis angleExemplified by centre-to-centre spacing a=10.
First, derive input alternating axis non-circular gear using above-mentioned formula, export the axode of alternating axis non-circular gear, obtain Final equation is as follows：
Drawn by numerical integration.
2nd, according to the spiral situation of axode, determine the profile geometry of envelope cutter, herein using sinusoidal instrument rack as Example.
3rd, the movement velocity of cutter is solved, its equation is as follows：
4th, modulus of the cutter on footpath not in the same direction is determined, it is z=24 to take the number of teeth
Drawn by numerical integration.
5th, the envelope solution of alternating axis non-circular gear tooth profile is obtained with above-mentioned cutter model envelope.
R in formulaaFor the cutter tooth-profile of above-mentioned solution. It is corresponding as follows for each corresponding transformation matrix：
6th, with numerical method, the flank profil of alternating axis non-circular gear is solved.
The numerical method shows as the normal vector of the cutter flank of tooth based on the solution to mesh equation, in this example mesh equation na(s) and the flank of tooth with respect to cutter movement velocityWhereinBased on the derivation to Envelope equation：
In alternating axis non-circular gear is inputted：
In alternating axis non-circular gear is exported：
The performance of mesh equation：Wheel for inputting：
Output wheel：
The coordinate data of the flank of tooth is can obtain by solution of the numerical method to mesh equation.
7th, according to flank profil data, three-dimensional modeling, analysis, and production and processing are carried out.
The alternating axis non-circular gear drive device designed using the design method of alternating axis non-circular gear includes a frame 0, it is characterised in that：There are the input shaft 1 and output shaft 2 of space vertical interlaced arrangement in frame 0, divide on input shaft 1 and output shaft 2 Input alternating axis non-circular gear 3 and output alternating axis non-circular gear 4, input alternating axis non-circular gear 3 are not fixed with by keyway It is intermeshed with output alternating axis non-circular gear 4.
The uniform rotation of power drive input shaft 1, by one-level alternating axis non-circular gear drive, spy is obtained on output shaft 2 Determine the movement output of function requirements.

Claims (3)

  1. A kind of 1. design method of alternating axis non-circular gear, it is characterised in that：Its step is as follows：
    First, input alternating axis non-circular gear is obtained according to space meshing principle and exports the axode of alternating axis non-circular gear；
    2nd, according to the spiral situation of axode, the profile geometry of envelope cutter is determined；
    3rd, the movement velocity of cutter is solved；
    4th, modulus of the cutter on footpath not in the same direction is determined；
    5th, the envelope solution of alternating axis non-circular gear tooth profile is obtained with above-mentioned cutter model envelope；
    6th, with numerical method, the flank profil of alternating axis non-circular gear is solved；
    7th, according to flank profil data, three-dimensional modeling, analysis, and production and processing are carried out；
    Described step is specifically：
    The first step, input the axode equation and output alternating axis non-circular gear axode equation difference of alternating axis non-circular gear For：
    In formula：
    A is the length of the axis minimum common vertical line section of two alternating axis non-circular gears, i.e. wheelbase；
    Σ is the folded acute angle of the axis of two alternating axis non-circular gears, i.e. crossed axis angle；
    T be axode to footpath parameter, axode can regard the set that instantaneous axis line is formed under footpath not in the same direction as；
    To input the corner of alternating axis non-circular gear, in the range of 0~2 π；
    For transmission ratio function, the velocity variations relation of wheel for inputting and output wheel is characterized, it is wheel for inputting cornerLetter Number, its form can be SIN functions, exponential function, direct proportion function；
    To export the corner of alternating axis non-circular gear, it isFunction, in the range of 0~2 π；Its calculating formula is as follows：
    Second step, the helix parameter of axode are
    3rd step, the movement velocity of cutter are：
    In formula,For the movement velocity of axode,For axode and the common movement velocity of cutter；
    WhenWhen,
    4th step, modulus of the cutter on footpath not in the same direction are：
    S in formulatTotal arc length that (2 π, t) are passed through by cutter, can be obtained by arc integral formula：
    Z is the number of teeth of gear, and by intensity, registration synthesis determines；
    5th step, input alternating axis non-circular gear, the envelope solution of output alternating axis non-circular gear tooth profile are respectively：
    In formula：raFor the cutter tooth-profile of above-mentioned solution； For each corresponding transformation matrix；
    6th step, with numerical method, solve the flank profil of alternating axis non-circular gear；
    For the numerical method based on the solution to mesh equation, mesh equation shows as the normal vector n of the cutter flank of toothaAnd flank of tooth phase (s) To the movement velocity of cutterWhereinBased on the derivation to Envelope equation：
    In alternating axis non-circular gear is inputted：
    In alternating axis non-circular gear is exported：
    The performance of mesh equation：Wheel for inputting：
    Output wheel：
    The coordinate data of the flank of tooth is can obtain by solution of the numerical method to mesh equation；
    7th step, according to flank profil data, carry out three-dimensional modeling, analysis, and production and processing.
  2. 2. a kind of usage right requires the alternating axis non-circular gear drive dress of the design method design of the 1 alternating axis non-circular gear Put, it is characterised in that：Including a frame (0), it is characterised in that：There is the input shaft of space vertical interlaced arrangement in frame (0) (1) input alternating axis non-circular gear (3) and output shaft (2), is fixed with by keyway respectively on input shaft (1) and output shaft (2) With output alternating axis non-circular gear (4), input alternating axis non-circular gear (3) and output alternating axis non-circular gear (4) intermeshing.
  3. 3. usage right according to claim 2 requires interlocking for the design method design of the 1 alternating axis non-circular gear Axle non-circular gear drive device, it is characterised in that：The length velocity relation of described input shaft (1) and output shaft (2) meets specific Transmission ratio function；Power drive input shaft (1) uniform rotation, by one-level alternating axis non-circular gear drive, it is on output shaft (2) Obtain the movement output of specific transmission ratio function requirement.
CN201410707936.8A 2014-11-28 2014-11-28 The design method and its transmission device of alternating axis non-circular gear Active CN104615800B (en)

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CN104985260B (en) * 2015-08-10 2017-06-13 武汉理工大学 The continuous Rolling-cut shear method of straight bevel gear
CN110929429A (en) * 2019-12-26 2020-03-27 江苏大学 Modeling simulation method based on ADAMS staggered shaft friction wheel mechanism transmission

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1738644A1 (en) * 2003-08-27 2007-01-03 Shimano Inc. Spinning reel oscillating device
CN102979855A (en) * 2012-12-19 2013-03-20 重庆大学 Involute tooth-thickness variable non-circular gear transmission

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1738644A1 (en) * 2003-08-27 2007-01-03 Shimano Inc. Spinning reel oscillating device
CN102979855A (en) * 2012-12-19 2013-03-20 重庆大学 Involute tooth-thickness variable non-circular gear transmission

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
Optimal design of nonlinear profile of gear ratio using non-circular gear for jumping robot;Okada M 等;《IEEE International Conference on Robotics and Automation》;20120628;第1958-1963页 *
渐开线锥形非圆齿轮的啮合原理与仿真模型;宋洪舟 等;《北京理工大学学报》;20130831;第33卷(第8期);第788-793页 *

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