CN109764104A - A kind of dynamic design method for stopping the drive mechanism of non circular gear than can be changed - Google Patents
A kind of dynamic design method for stopping the drive mechanism of non circular gear than can be changed Download PDFInfo
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Abstract
Dynamic stop the design method than variable drive mechanism of non circular gear the invention discloses a kind of, comprising the following steps: S1, according to the modulus of the imagination of the driving wheel full all number of teeth and driven wheel calculates the full all numbers of teeth of imagination of driven wheel；S2, the registration that driving wheel and driven wheel are calculated according to driving wheel head tooth pressure angle and driven wheel tooth top pressure angle start to carry out step S3 if registration is greater than 1；Otherwise, the full all number of teeth values of imagination that S1 readjusts driving wheel are returned；S3, stop according to teeth section of corresponding center of circle angle each on driving wheel and with teeth section of corresponding move than determining center of circle angle value corresponding with described with teeth section adjacent active partial gear Locking arc；S4, with teeth section of number of driving wheel are equal with teeth section of number of driving wheel, and the difference of each with teeth section of number of teeth with teeth section of the number of teeth corresponding on driven wheel is 1 on driving wheel.The incomplete mechanism gear mechanism of the present invention program design is compact and design is easy.
Description
Technical Field
The invention relates to the technical field of transmission, in particular to a design method of an incomplete gear transmission mechanism with a variable dynamic-stop ratio.
Background
In various mechanical transmission processes, some components are usually required to realize periodic motion and pause, and a mechanism capable of converting the continuous motion of a driving part into the regular motion and pause of a driven part is called an intermittent motion mechanism. Common intermittent mechanisms include a ratchet mechanism, a sheave mechanism and an incomplete gear mechanism, wherein the incomplete gear mechanism is more flexible in design and easier to control the movement stop ratio of the incomplete gear mechanism compared with the ratchet mechanism and the sheave mechanism, and therefore, the incomplete gear mechanism is the most common intermittent mechanism. However, the conventional incomplete gear mechanism has a fixed stop ratio, which limits the application range. In order to overcome the defect, many students advocate that the driving wheel or the driven wheel is divided into two parts, then the two driving wheels or the two driven wheels are coaxially combined, and the relative position of the two driving wheels or the two driven wheels is changed to enable the dynamic-stop ratio of the mechanism to be variable. Although the mode realizes the variable dynamic-stop ratio, the design structure is more complex, the mechanism volume is larger, and the mechanism is not suitable for the application in small space. Based on this, it is significant to design an incomplete gear with a simple structure.
Disclosure of Invention
The technical problem to be solved by the invention is as follows: the design method of the incomplete gear transmission mechanism with the variable dynamic stop ratio is compact and simple in structure.
In order to solve the technical problems, the invention adopts the technical scheme that: a method of designing an incomplete gear transmission mechanism with a variable dynamic-to-stop ratio, the incomplete gear transmission mechanism comprising a driving wheel and a driven wheel, the method comprising the steps of:
s1, determining structural parameters of the driving wheel and the driven wheel: calculating the assumed full-circumference tooth number of the driven wheel according to the assumed full-circumference tooth number of the driving wheel and the modulus of the driven wheel;
s2, checking the contact ratio of the driving wheel and the driven wheel: calculating the contact ratio of the driving wheel and the driven wheel according to the head tooth pressure angle of the driving wheel and the tooth crest pressure angle of the driven wheel, and if the contact ratio is greater than 1, starting to perform step S3; otherwise, returning to S1 to readjust the virtual full-circle tooth number of the driving wheel until the contact ratio is greater than 1, and then proceeding to step S3;
s3, determining the locking arc central angle of the driving incomplete gear: determining a circle center included angle value corresponding to a locking arc of the driving incomplete gear adjacent to each toothed section according to a circle center included angle corresponding to each toothed section on the driving wheel and a dynamic-stop ratio corresponding to the toothed section;
s4, designing the tooth number of the driven incomplete gear with the tooth section: the number of the toothed sections of the driven wheel is equal to that of the toothed sections of the driving wheel, and the difference value between the number of teeth of each toothed section on the driving wheel and the number of teeth of the corresponding toothed section on the driven wheel is 1.
Further, the step S1 specifically includes the following steps: selecting the modulus m of the driven wheel and the supposed full-circle tooth number z 'of the driving wheel'1Calculating the addendum height coefficient h of the driving wheel according to the formula (1)* amLet 1-h* am→ min, to derive the driven wheel virtual tooth number z'2：
In the formula, h* a1Is a standard tooth crest height factor, h* a11 is ═ 1; the calculation formula of δ and γ is shown in the following formula (2):
α0angle of pressure, α020 degrees, K is the number of teeth spanned by the locking arc of the driven wheel, the value of the number is a design variable parameter, and the value of K isShould be selected to satisfy 1-h* amCondition No. → min. The value range of the K value is usually between 1 and 5 in the design process.
Further, in step S2, the specific calculation procedure of the gear contact ratio is that, first, the pressure angle α of the leading tooth of the driving wheel and the addendum circle of the driven wheel is calculated by the equations (3) and (4)1And α2Then substituted into the formula (5) to obtain the contact ratio epsilonα：
In the formula, h* a2Is the standard tooth crest coefficient of the driven gear, h* a2＝1。
Further, in the step S3, the included angle β is determined according to the circle center corresponding to the first toothed segment1The first section is provided with a first section locking arc between the toothed section and the toothed section of the second section, and the included angle of the circle center of the first section locking arc isAccording to β1Andthe satisfied relation (6) can be calculated
In the formula, k1Is a first set of stop-and-go ratios.
Further, step S3 includes calculating a central angle corresponding to the locking arc of the ith segment according to the central angle corresponding to the toothed segment of the ith segment and the ith group of stop ratios, where i is any natural number from 2 to N times of stop of the driving wheel per rotation.
Further, in step S4, the number of teeth of each toothed segment on the driven wheel is calculated according to the following formula (7), and the number of idle times per rotation of the driven wheel is N times as same as that of the driving wheel, and the number of teeth of each toothed segment on the driven wheel is calculated according to the following formula (7):
z2＝z1-1 (7)
furthermore, the locking arcs on the driving wheel and the locking arcs on the driven wheel are in concave-convex fit and have the same curvature radius.
Further, the step S1 further includes determining other structural parameters of the driving wheel and the driven wheel according to the assumed full-circumference tooth number and the module, where the other structural parameters include a reference circle radius, a tooth top circle radius, a tooth root circle radius, a center distance, a driving wheel locking arc radius, a meshing angle, and a meshing angle.
Further, the calculation formulas of the reference circle radius, the addendum circle radius, the dedendum circle radius, the center distance, the driving wheel locking arc radius, the engagement angle and the engagement angle are sequentially as follows:
radius of reference circle
Radius of addendum circle
Root circle radius
Center distance
Radius of locking arc of driving wheel
Angle of engagement
Angle of engagement
Wherein,z ' and an imaginary full-circumference tooth number z ' of the drive wheel '1Or imaginary full-cycle tooth number z 'of driven wheel'2Are equal.
The invention has the beneficial effects that: the design method of the invention realizes the variable dynamic-stopping ratio by skillfully designing the structure of the gear, and overcomes the technical problems that the dynamic-stopping ratio of the traditional incomplete gear cannot be changed, and the structure of a plurality of driving wheels or a plurality of driven wheels is complicated and is difficult to realize; the incomplete gear intermittent drive steering device composed of incomplete gears designed by the method has simple and compact structure and convenient processing and assembly, after the full-circumference tooth numbers of the two incomplete gears are calculated and set, the tooth numbers of the meshing section of the two gears and the arc length of the locking arc are configured, the intermittent drive with different stop ratios can be realized, a plurality of stop ratios are integrated on a pair of incomplete gear mechanisms, and the whole mechanism has compact structure and simpler and more convenient design.
Drawings
FIG. 1 is a schematic illustration of design parameters for an incomplete gear system designed according to an embodiment of the present invention;
fig. 2 is a schematic view of the overall geometry of a partial gear system designed according to an embodiment of this invention.
Detailed Description
In order to explain technical contents, achieved objects, and effects of the present invention in detail, the following description is made with reference to the accompanying drawings in combination with the embodiments.
The embodiment of the invention is as follows: a method for designing an incomplete gear transmission mechanism with variable dynamic-stop ratio, as shown in fig. 1, wherein the incomplete gear transmission mechanism comprises a driving wheel and a driven wheel, and the method comprises the following steps:
the method comprises the following steps: determination of two Gear full Ring tooth number z'1,z'2
Firstly, selecting the modulus m of a driving wheel and a driven wheel and the full circumferential tooth number z of the driving wheel'1Then substituting the obtained data into the following formula to obtain the tooth crest height coefficient h of the driving wheel* amLet 1-h* am→ min, to derive the driven wheel virtual tooth number z'2。
In the formula, h* a1Is a standard tooth crest height factor, h* a1＝1；α0Angle of pressure, α0＝20°。
The calculation formula of δ and γ is shown in the following formula (2):
，
k is the number of teeth spanned by the locking arc of the driven wheel.
Step two: checking the contact ratio epsilon of gearsα
In order to ensure that the two gears are normally meshed, the contact ratio must be more than 1, when the contact ratio is calculated, firstly, the addendum circle pressure angle α of the head tooth of the driving wheel and the driven wheel is calculated through the formula (3) and the formula (4)1And α2Then substituted into the formula (5) to obtain the contact ratio epsilonα：
In the formula, h* a2Is the standard tooth crest coefficient of the driven gear, h* a2＝1。
Step three: determination of locking arc central angle of incomplete driving gear
Determining the number N of stop times of each rotation of the driving wheel and the number z of teeth of the toothed section at the first section according to the actual motion requirement of the mechanism1aIts correspondent centre included angle is β1，z1aWith the next segment of the locking arc (the centre of the circle is at an angle of) Form a set of dynamic-to-stop ratios k1。
And designing a dynamic-stopping ratio as required, and configuring a central angle corresponding to a locking arc on the incomplete driving gear according to the determined dynamic-stopping ratio so as to determine the structure of the locking arc.
Similarly, the number of teeth z of the second toothed segment is set1b(the included angle of the circle center is β2) And the included angle with the second section of locking arc (the circle center is) Form a second set of stop-and-go ratios k2The calculation is shown in equation (6). If necessary, k can be appropriately arranged3、k4…。
Step four: the driven incomplete gear has tooth section tooth number and locks the structural design of the arc on the driven wheel:
the number of stop times of each rotation of the driven wheel is N times as same as that of the driving wheel, and the tooth number of each toothed section of the driven wheel is calculated according to the formula (7):
z2＝z1-1 (7)
the locking arc on the driving wheel is a locking convex arc, the locking arc on the driven wheel is a locking concave arc, and the curvature radius of the locking convex arc is equal to that of the locking concave arc.
Step five: determining other parameters of the two gears
Radius of reference circle
Radius of addendum circle
Root circle radius
Center distance
Radius of locking arc of driving wheel
Angle of engagement:
the angle of emergence:
specifically, the number of idle times per revolution N of the driving wheel and the driven wheel is 2, the modulus m is 1, and the number of teeth of the full circumference of the driving incomplete gear is 41.
Firstly, according to the formula (1) and the formula (2), the coefficient of the top height of the driving incomplete gear teeth is obtained to satisfy 1-h* amDriven wheel full-circle tooth number z → min'2: z'2When equal to 23, h* am0.94, meeting the requirements.
Then checking the contact ratio epsilonα: according to the formula (5), when the numbers of teeth of the primary pulley and the secondary pulley are 41 and 23, respectively,. epsilon.α＝1.61，εα>1 meets the design requirements.
Configuring a driving wheel-start-stop ratio: according to the movement requirement of the mechanism, the number of teeth at the first section of the driving wheel is set to be 9, the corresponding included angle of the circle center is 77 degrees, and the first stop ratio of the driving wheelThe included angle of the circle center of the first locking arc is 55 degrees. The number of teeth of the second section of the driving wheel is 10, the corresponding included angle of the circle centers is 86 degrees, and the included angle of the circle centers of the locking arcs of the second section is 142 degrees, so that
Designing a driven incomplete gear according to the fourth step: the number of teeth of the two sections of driven wheels is respectively 8 and 9, the included angles of the centers of the two sections of locking arcs are the same, and the curvature radiuses of the two sections of locking arcs are the same as the locking radius of the driving wheel.
Determining the geometric dimensions of two incomplete gears according to step five, as shown in fig. 2: the reference circle radius of two wheels is 20.5mm and 11.5mm respectively, the addendum circle radius is 21.5mm and 12.5mm respectively, the root circle radius is 19.25mm and 10.25mm respectively, the center distance is 32mm, the locking arc radius of the driving wheel is 19.88mm, the engagement angle is 0.190rad, and the engagement angle is 0.238 rad.
The scheme of the invention can be used for solving the limitation of single dynamic-stop ratio of the traditional incomplete gear mechanism, firstly parameters such as full-circumference tooth number, reference circle diameter, center distance, locking arc radius, engagement angle and the like of a driving wheel and a driven wheel are determined according to a design method of an incomplete gear, and then parameters such as the number of stop times per revolution of two incomplete gears and the tooth number design locking arc circle center included angle of a toothed segment are configured according to the actual dynamic-stop ratio demand.
The term "the corresponding tooth section on the driven wheel" in the invention means that the driving wheel and the driven wheel are numbered in sequence, and the tooth numerical value of the tooth section on the driving wheel and the driven wheel in the same sequence is different by 1. The terms "first and second … …" in the present invention are not intended to be limited to a sequence, but are merely different.
The above description is only an embodiment of the present invention, and not intended to limit the scope of the present invention, and all equivalent changes made by using the contents of the present specification and the drawings, or applied directly or indirectly to the related technical fields, are included in the scope of the present invention.
Claims (8)
1. A design method of an incomplete gear transmission mechanism with a variable dynamic-stop ratio is characterized in that: the incomplete gear transmission mechanism comprises a driving wheel and a driven wheel, and the design method comprises the following steps:
s1, determining structural parameters of the driving wheel and the driven wheel: calculating the assumed full-circumference tooth number of the driven wheel according to the assumed full-circumference tooth number of the driving wheel and the modulus of the driven wheel;
s2, checking the contact ratio of the driving wheel and the driven wheel: calculating the contact ratio of the driving wheel and the driven wheel according to the head tooth pressure angle of the driving wheel and the tooth crest pressure angle of the driven wheel, and if the contact ratio is greater than 1, starting to perform step S3; otherwise, returning to S1 to readjust the virtual full-circle tooth number of the driving wheel until the contact ratio is greater than 1, and then proceeding to step S3;
s3, determining the locking arc central angle of the driving incomplete gear: determining a circle center included angle value corresponding to a locking arc of the driving incomplete gear adjacent to each toothed section according to a circle center included angle corresponding to each toothed section on the driving wheel and a dynamic-stop ratio corresponding to the toothed section;
s4, designing the tooth number of the driven incomplete gear with the tooth section: the number of the toothed sections of the driven wheel is equal to that of the toothed sections of the driving wheel, and the difference value between the number of teeth of each toothed section on the driving wheel and the number of teeth of the corresponding toothed section on the driven wheel is 1.
2. The method of designing a variable stop-ratio incomplete gear transmission as set forth in claim 1, wherein: the step S1 specifically includes the following steps: selecting the modulus m of the driven wheel and the supposed full-circle tooth number z 'of the driving wheel'1Calculating the addendum height coefficient h of the driving wheel according to the formula (1)* amLet 1-h* am→ min, to derive the driven wheel virtual tooth number z'2：
In the formula, h* a1Is a standard tooth crest height factor, h* a11 is ═ 1; the calculation formula of δ and γ is shown in the following formula (2):
α0angle of pressure, α020 degrees, K is the number of teeth spanned by the locking arc of the driven wheel, the value is a design variable parameter, and the value of K is selected to satisfy 1-h* amCondition No. → min.
3. The dynamic stop of claim 2The design method of the incomplete gear transmission mechanism with variable ratio is characterized in that in the step S2, the specific calculation process of the gear contact ratio is as follows, firstly, the pressure angle α of the head tooth of the driving wheel and the addendum circle of the driven wheel is calculated through the formula (3) and the formula (4)1And α2Then substituted into the formula (5) to obtain the contact ratio epsilonα：
In the formula, h* a2Is the standard tooth crest coefficient of the driven gear, h* a2＝1。
4. The method for designing an incomplete gear transmission mechanism with variable dynamic-stop ratio as claimed in claim 1, wherein in step S3, the included angle β is determined according to the circle center corresponding to the first toothed segment1The first section is provided with a first section locking arc between the toothed section and the toothed section of the second section, and the included angle of the circle center of the first section locking arc isAccording to β1Andthe satisfied relation (6) can be calculated
In the formula, k1Is a first set of stop-and-go ratios.
5. The method of designing a variable stop-ratio incomplete gear transmission according to claim 4, characterized in that: step S3 further includes calculating a central angle corresponding to the locking arc of the ith segment according to the central angle corresponding to the toothed segment of the ith segment and the ith group of stop ratios, where i is any natural number from 2 to N times of stop per rotation of the driving wheel.
6. The design method of the incomplete gear transmission mechanism with variable dynamic stop ratio according to any one of claims 1 to 5, characterized in that: and the locking arc on the driving wheel is matched with the locking arc on the driven wheel in a concave-convex mode, and the curvature radius of the locking arc is equal to that of the locking arc on the driven wheel.
7. The design method of the incomplete gear transmission mechanism with variable dynamic stop ratio according to any one of claims 1 to 5, characterized in that: step S1 further includes determining other structural parameters of the driving wheel and the driven wheel according to the assumed full-circumference tooth number and the module, where the other structural parameters include a reference circle radius, a tooth top circle radius, a tooth root circle radius, a center distance, a driving wheel locking arc radius, a meshing angle, and a meshing angle.
8. The method of designing a variable stop-ratio incomplete gear transmission as set forth in claim 7, wherein: the calculation formulas of the reference circle radius, the addendum circle radius, the dedendum circle radius, the center distance, the driving wheel locking arc radius, the engagement angle and the engagement angle are as follows in sequence:
radius of reference circle
Radius of addendum circle
Root circle radius
Center distance
Radius of locking arc of driving wheel
Angle of engagement
Angle of engagement
Wherein,z ' and an imaginary full-circumference tooth number z ' of the drive wheel '1Or imaginary full-cycle tooth number z 'of driven wheel'2And the number of teeth spanned by the locking arc of the driven wheel is K, and the K is any natural number between 1 and 5.
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| CN201910142009.9A CN109764104A (en) | 2019-02-26 | 2019-02-26 | A kind of dynamic design method for stopping the drive mechanism of non circular gear than can be changed |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110274197A (en) * | 2019-06-21 | 2019-09-24 | 合肥流明新能源科技有限公司 | A kind of solar lawn lamp that can be used for irrigating |
| CN113027993A (en) * | 2021-03-19 | 2021-06-25 | 长沙理工大学 | Gear transmission chain layout optimization method |
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| JPS59187156A (en) * | 1983-04-07 | 1984-10-24 | Jukun Cho | Speed change gear |
| JPH0932908A (en) * | 1995-07-17 | 1997-02-07 | Nissan Motor Co Ltd | Designing of tooth profile of bevel gear |
| CN201190777Y (en) * | 2007-12-17 | 2009-02-04 | 宝钢集团苏州冶金机械厂 | Tooth depth-varying gear |
| CN106763606A (en) * | 2016-12-06 | 2017-05-31 | 昆明理工大学 | It is a kind of with multiple it is dynamic stop than outside geneva mechanism and its application method |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110274197A (en) * | 2019-06-21 | 2019-09-24 | 合肥流明新能源科技有限公司 | A kind of solar lawn lamp that can be used for irrigating |
| CN113027993A (en) * | 2021-03-19 | 2021-06-25 | 长沙理工大学 | Gear transmission chain layout optimization method |
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