CN202048161U - Involute helical gear - Google Patents
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Abstract
本实用新型提供了既可提高齿根抗疲劳强度、又基本不影响其抗冲击性能的渐开线斜齿轮,其特点是:该渐开线斜齿轮的轮齿两侧的齿廓压力角不相等,且压力角较大的齿面为啮合面,压力角较小的齿面为非啮合面。该齿轮为变位的、轮齿两侧齿廓曲面压力角不等的渐开线斜齿轮,其根据渐开线斜齿圆柱齿轮齿廓曲面的生成特点,给出轮齿两侧齿廓曲面压力角不等的渐开线斜齿圆柱齿轮的设计思想,并推导出变位加工情况下,齿轮几何参数及尺寸的计算公式。相对于常规的渐开线斜齿圆柱齿轮,该新型渐开线斜齿圆柱齿轮具有承载能力大、体积小、质量轻、使用寿命长、噪声小等优点。
The utility model provides an involute helical gear which can improve the anti-fatigue strength of the dedendum and basically does not affect its anti-impact performance. The tooth surface with the larger pressure angle is the meshing surface, and the tooth surface with the smaller pressure angle is the non-meshing surface. The gear is an involute helical gear with displacement and different pressure angles on the tooth profile surface on both sides. According to the generation characteristics of the tooth profile surface of the involute helical cylindrical gear, the tooth profile surface on both sides of the tooth is given Design ideas of involute helical spur gears with different pressure angles, and deduce the calculation formulas of gear geometric parameters and dimensions in the case of displacement processing. Compared with conventional involute helical gears, the new involute helical gears have the advantages of large load capacity, small size, light weight, long service life and low noise.
Description
技术领域 technical field
本实用新型涉及齿轮设计的技术领域,具体是一种渐开线斜齿轮。The utility model relates to the technical field of gear design, in particular to an involute helical gear.
背景技术 Background technique
齿轮传动因具有功率大,效率高,寿命长等优点,而被广泛应用。其性能和质量的优劣最终影响到机器产品的质量高低,因此,为适应现代化大生产和科技的快速发展,要求齿轮传动的性能不断优化。尤其在近数十年以来,在齿轮的啮合理论、承载能力计算与试验、振动与噪声、新型齿轮传动等各方面,均有很大进展。Gear transmission is widely used because of its advantages of high power, high efficiency and long life. The pros and cons of its performance and quality ultimately affect the quality of machine products. Therefore, in order to adapt to the rapid development of modern mass production and technology, the performance of gear transmission is required to be continuously optimized. Especially in recent decades, great progress has been made in the meshing theory of gears, calculation and test of bearing capacity, vibration and noise, and new gear transmission.
轮齿形状不仅影响到齿轮副的运动特性,还影响到齿轮副的动力特性。为顺应现代化大生产的发展趋势,人们不断探究新型齿廓齿形。研究表明,增大齿轮的压力角可提高齿根弯曲疲劳强度。常用的渐开线斜齿圆柱齿轮,由于工作齿面、非工作齿面的承载情况和啮合状况的不同,如果同时增大齿轮两侧的压力角,将导致齿顶变薄,断齿的可能性增大,即轮齿的抗冲击性能将下降。The tooth shape not only affects the kinematic characteristics of the gear pair, but also affects the dynamic characteristics of the gear pair. In order to conform to the development trend of modern mass production, people continue to explore new tooth profiles. The research shows that increasing the pressure angle of the gear can improve the bending fatigue strength of the dedendum. Commonly used involute helical cylindrical gears, due to the difference in load and meshing conditions between the working tooth surface and the non-working tooth surface, if the pressure angle on both sides of the gear is increased at the same time, the tooth top will become thinner and the teeth may be broken. The resistance increases, that is, the impact resistance of the gear teeth will decrease.
实用新型内容 Utility model content
本实用新型所要解决的技术问题是提供一种既能提高齿根抗疲劳强度、又基本不影响其抗冲击性能的渐开线斜齿轮。The technical problem to be solved by the utility model is to provide an involute helical gear which can not only improve the anti-fatigue strength of the tooth root, but basically not affect its anti-shock performance.
为解决上述技术问题,本实用新型提供了一种渐开线斜齿轮,其特点是:该渐开线斜齿轮的轮齿两侧的齿廓压力角不相等,且压力角较大的齿面为啮合面,压力角较小的齿面为非啮合面。In order to solve the above technical problems, the utility model provides an involute helical gear, which is characterized in that: the tooth profile pressure angles on both sides of the teeth of the involute helical gear are not equal, and the tooth surface with a larger pressure angle The tooth surface with the smaller pressure angle is the non-engaging surface.
渐开线斜齿轮的非啮合侧齿廓曲面的形成:以线段rbc为半径画出渐开线斜齿轮的第一基圆柱面,且存在第一发生面Q与第一基圆柱面相切,第一发生面Q上的第一线段KK与第一基圆柱的轴线的夹角为βbc≠0,当第一发生面Q沿着第一基圆柱面做无滑动的纯滚动时,第一线段KK的轨迹即为渐开线斜齿轮的右侧齿面(非啮合侧齿廓曲面);The formation of the tooth profile surface on the non-meshing side of the involute helical gear: draw the first base cylinder surface of the involute helical gear with the line segment r bc as the radius, and there is a first occurrence surface Q that is tangent to the first base cylinder surface, The angle between the first line segment KK on the first occurrence surface Q and the axis of the first base cylinder is β bc ≠0, when the first occurrence surface Q performs pure rolling without sliding along the first base cylinder surface, the first base cylinder The trajectory of a line segment KK is the right tooth surface of the involute helical gear (the non-meshing side tooth profile surface);
渐开线斜齿轮的啮合侧齿廓曲面的形成:以线段rbd为半径做出渐开线斜齿轮的第二基圆柱面,其中,rbc/rbd=1~1.36;且存在第二发生面P与第二基圆柱面相切,第二发生面P上的第二线段MM与第二基圆柱的轴线的夹角为βbd≠0,当第二发生面P沿着第二基圆柱面做无滑动的纯滚动时,第二线段MM的轨迹即为渐开线斜齿轮的左侧齿面(啮合侧齿廓曲面)。The formation of the tooth profile surface on the meshing side of the involute helical gear: take the line segment r bd as the radius to make the second base cylindrical surface of the involute helical gear, where r bc /r bd = 1 ~ 1.36; and there is a second The occurrence surface P is tangent to the second base cylinder surface, the angle between the second line segment MM on the second occurrence surface P and the axis of the second base cylinder is β bd ≠0, when the second occurrence surface P is along the second base cylinder When the surface is doing pure rolling without sliding, the track of the second line segment MM is the left tooth surface of the involute helical gear (meshing side tooth profile surface).
本实用新型具有积极的效果:(1)本实用新型的齿轮为变位的、轮齿两侧齿廓曲面压力角不等的渐开线斜齿轮,根据渐开线斜齿圆柱齿轮齿廓曲面的生成特点,给出轮齿两侧齿廓曲面压力角不等的渐开线斜齿圆柱齿轮设计思想,并推导出变位加工情况下,齿轮几何参数及尺寸的计算公式。轮齿两侧齿廓压力角不等与现有技术相比,由图5可知,齿廓两边采用不等压力角时可减小齿轮的体积和重量。相对于常规的渐开线斜齿圆柱齿轮,该新型渐开线斜齿圆柱齿轮具有承载能力大、体积小、质量轻、使用寿命长、噪声小等优点。(2)本实用新型提出在斜齿轮轮齿的两侧使用压力角不等的齿廓曲面,并进行变位处理的方法。本实用新型的渐开线斜齿轮的特点是:通过使用不同直径大小的基圆柱,在渐开线斜齿圆柱齿轮的两侧生成不同压力角的齿廓曲面;并根据工作需要设计出变位齿轮的几何尺寸。The utility model has positive effects: (1) the gear of the utility model is an involute helical gear which is shifted and the pressure angle of the tooth profile surface on both sides of the gear tooth is not equal. According to the generation characteristics of the gear tooth, the design idea of the involute helical cylindrical gear with different pressure angles on the tooth profile surface on both sides is given, and the calculation formula of the geometric parameters and dimensions of the gear is deduced in the case of displacement processing. The tooth profile pressure angles on both sides of the tooth profile are not equal. Compared with the prior art, it can be seen from Fig. 5 that the volume and weight of the gear can be reduced when the tooth profile adopts unequal pressure angles on both sides. Compared with conventional involute helical gears, the new involute helical gears have the advantages of large load capacity, small size, light weight, long service life and low noise. (2) The utility model proposes a method of using tooth profile curved surfaces with unequal pressure angles on both sides of the helical gear teeth and performing displacement processing. The characteristic of the involute helical gear of the present utility model is: by using base cylinders of different diameters, tooth profile surfaces with different pressure angles are generated on both sides of the involute helical gear; and the displacement is designed according to the work needs Gear geometry.
附图说明 Description of drawings
图1为本实用新型的渐开线斜齿轮的结构示意图;Fig. 1 is the structural representation of the involute helical gear of the present utility model;
图2为图1中的渐开线斜齿轮的齿形图;图中的附图标记:1--齿顶圆,2--分度圆,3--第一基圆柱面,4--齿根圆,5--第二基圆柱面,6--左侧齿面,7--右侧齿面;Fig. 2 is the tooth shape diagram of the involute helical gear in Fig. 1; reference numerals in the figure: 1--addendum circle, 2--dividing circle, 3--the first base cylindrical surface, 4-- Root circle, 5--second base cylindrical surface, 6--left tooth surface, 7--right tooth surface;
图3为图2中的渐开线斜齿轮的啮合侧齿廓曲面(也即左侧渐开线齿廓)的生成示意图;Fig. 3 is the generating schematic diagram of the meshing side tooth profile surface (that is, the left involute tooth profile) of the involute helical gear in Fig. 2;
图4为图2中的渐开线斜齿轮的非啮合侧齿廓曲面(也即右侧渐开线齿廓)的生成示意图;Fig. 4 is a schematic diagram of generating the non-meshing side tooth profile surface (that is, the right involute tooth profile) of the involute helical gear in Fig. 2;
图5为现有技术中的渐开线斜齿轮的齿形8和本实用新型的渐开线斜齿轮的齿形9的对比示意图。Fig. 5 is a schematic diagram comparing the tooth profile 8 of the involute helical gear in the prior art and the tooth profile 9 of the involute helical gear of the present invention.
具体实施方式 Detailed ways
见图1-2,本实施例的渐开线斜齿轮的齿形主要包括齿顶1、第二个基圆柱5生成的左侧齿面6、第一个基圆柱3生成的右侧齿面7及齿根4。齿轮工作时,压力角大的左侧齿面6参与啮合,压力角小的右侧齿面7不参与啮合。As shown in Figure 1-2, the tooth shape of the involute helical gear in this embodiment mainly includes the tooth top 1, the left tooth surface 6 formed by the second base cylinder 5, and the right tooth surface formed by the first base cylinder 3 7 and
渐开线斜齿轮的非啮合侧齿廓曲面的形成:以线段rbc为半径画出渐开线斜齿轮的第一基圆柱面,且存在第一发生面Q与第一基圆柱面相切,第一发生面Q上的第一线段KK与第一基圆柱的轴线的夹角为βbc≠0,当第一发生面Q沿着第一基圆柱面做无滑动的纯滚动时,第一线段KK的轨迹即为渐开线斜齿轮的右侧齿面7(非啮合侧齿廓曲面);The formation of the tooth profile surface on the non-meshing side of the involute helical gear: draw the first base cylinder surface of the involute helical gear with the line segment r bc as the radius, and there is a first occurrence surface Q that is tangent to the first base cylinder surface, The angle between the first line segment KK on the first occurrence surface Q and the axis of the first base cylinder is β bc ≠0, when the first occurrence surface Q performs pure rolling without sliding along the first base cylinder surface, the first base cylinder The trajectory of a line segment KK is the right tooth surface 7 of the involute helical gear (the tooth profile surface on the non-meshing side);
渐开线斜齿轮的啮合侧齿廓曲面的形成:以线段rbd为半径做出渐开线斜齿轮的第二基圆柱面,其中,rbc/rbd=1~1.36;且存在第二发生面P与第二基圆柱面相切,第二发生面P上的第二线段MM与第二基圆柱的轴线的夹角为βbd≠0,当第二发生面P沿着第二基圆柱面做无滑动的纯滚动时,第二线段MM的轨迹即为渐开线斜齿轮的左侧齿面6(啮合侧齿廓曲面)。The formation of the tooth profile surface on the meshing side of the involute helical gear: take the line segment r bd as the radius to make the second base cylindrical surface of the involute helical gear, where r bc /r bd = 1 ~ 1.36; and there is a second The occurrence surface P is tangent to the second base cylinder surface, the angle between the second line segment MM on the second occurrence surface P and the axis of the second base cylinder is β bd ≠0, when the second occurrence surface P is along the second base cylinder When the surface is doing pure rolling without sliding, the track of the second line segment MM is the left tooth surface 6 of the involute helical gear (meshing side tooth profile surface).
渐开线斜齿轮的齿数、分度圆柱上的螺旋角、分度圆端面模数、分度圆法面模数、啮合侧分度圆端面压力角、非啮合侧分度圆端面压力角、啮合侧分度圆法面压力角、非啮合侧分度圆法面压力角分别为:z、β、mt、mn、αtd、αtc、αnd、αnc;The number of teeth of the involute helical gear, the helix angle on the indexing cylinder, the modulus of the end face of the indexing circle, the modulus of the normal face of the indexing circle, the pressure angle of the end face of the indexing circle on the meshing side, the pressure angle of the end face of the indexing circle on the non-meshing side, The normal surface pressure angle of the index circle on the meshing side and the pressure angle on the normal surface of the index circle on the non-engaged side are: z, β, m t , m n , α td , α tc , α nd , α nc ;
z的取值符合传动比要求及满足不根切原则;The value of z meets the transmission ratio requirements and meets the principle of non-undercutting;
β=8~20°;β=8~20°;
mn的取值大小根据《齿轮手册》(机械工业出版社,2004-2第2版,中国版本图书馆CIP数字核字(2000)第09768号)选定或根据需要自定;The value of m n is selected according to "Gear Handbook" (Machinery Industry Press, 2004-2 2nd Edition, China Edition Library CIP Digital Kernel (2000) No. 09768) or customized according to needs;
mt=mn/cosβ毫米;m t = m n / cos β mm;
αtd=atan(tanαnd/cosβ)度;α td = atan(tanα nd /cosβ) degrees;
αtc=atan(tanαnc/cosβ)度;α tc = atan(tanα nc /cosβ) degrees;
αnc=20°;α nc = 20°;
αnd在满足不根切和轮齿抗冲击性能的前提下,满足:45°>αnd>αnc>14°。α nd satisfies: 45° > α nd > α nc > 14° on the premise of satisfying no undercutting and gear tooth impact resistance.
所述第二基圆柱面的半径毫米,其中:d为渐开线斜齿轮的分度圆直径,毫米。The radius of the second base cylindrical surface mm, where: d is the pitch circle diameter of the involute helical gear, mm.
所述βbd=atan(tanβ·cosαtd)度,且0<βbd<90°。The β bd =atan(tanβ·cosα td ) degree, and 0<β bd <90°.
所述第一基圆柱面的半径毫米。The radius of the first base cylindrical surface mm.
所述βbc=atan(tanβ·cosαtc),且0<βbc<90°。The β bc =atan(tanβ·cosα tc ), and 0<β bc <90°.
所述啮合侧齿廓的法面齿顶高系数、非啮合侧齿廓的法面齿顶高系数、啮合侧齿廓的法面顶隙系数、非啮合侧齿廓的法面顶隙系数分别为 其中:The normal tooth top height coefficient of the meshing side tooth profile, the normal tooth top height coefficient of the non-meshing side tooth profile, the normal top clearance coefficient of the meshing side tooth profile, and the normal top clearance coefficient of the non-meshing side tooth profile are respectively for in:
渐开线斜齿轮的分度圆法面齿厚、端面齿厚分别为sn、st;The normal tooth thickness of the pitch circle and the end tooth thickness of the involute helical gear are s n , s t ;
则:
xn为渐开线斜齿轮的法面变位系数,xt为渐开线斜齿轮的端面变位系数,则xt=xn cosβ,且以防止斜齿轮产生根切。x n is the normal surface displacement coefficient of the involute helical gear, x t is the end surface displacement coefficient of the involute helical gear, then x t = x n cosβ, and To prevent undercutting of the helical gear.
渐开线斜齿轮的齿顶圆直径为da, The diameter of the addendum circle of the involute helical gear is d a ,
渐开线斜齿轮的齿根圆直径为df, The diameter of the dedendum circle of the involute helical gear is d f ,
与现有的渐开线斜齿圆柱齿轮相比,本实用新型的渐开线斜齿轮能显著提高承载能力(研究表明:采用大压力角做为啮合面、小压力角做为非啮合面的斜齿轮,可提高其承载能力。)、缩小体积、减轻重量(采用啮合面与非啮合面压力角不等的齿轮相对于啮合面与非啮合面压力角相等的的齿轮而言,其齿面变窄,体积和重量自然变小)、延长使用寿命(强度提高则寿命延长)、降低振动及噪声(由于啮合面与非啮合面压力角不等的齿轮传动时的振动位移和动载荷都较现有齿轮的小,因而齿轮传动时振动和噪声也就降低了),市场前景广阔,具有巨大的社会和经济效益。Compared with the existing involute helical gears, the involute helical gears of the present invention can significantly improve the carrying capacity (research shows: use a large pressure angle as the meshing surface and a small pressure angle as the non-meshing surface Helical gears can improve their load-carrying capacity.), reduce volume, and reduce weight (the gears with different pressure angles between the meshing surface and the non-meshing surface are compared to the gears with the same pressure angle between the meshing surface and the non-meshing surface. narrower, the volume and weight will naturally become smaller), prolong the service life (the strength increases and the life prolongs), reduce vibration and noise (due to the gear transmission with different pressure angles between the meshing surface and the non-meshing surface, the vibration displacement and dynamic load are relatively small. The existing gear is small, so the vibration and noise during gear transmission are also reduced), the market prospect is broad, and it has huge social and economic benefits.
显然,本实用新型的上述实施例仅仅是为清楚地说明本实用新型所作的举例,而并非是对本实用新型的实施方式的限定。对于所属领域的普通技术人员来说,在上述说明的基础上还可以做出其它不同形式的变化或变动。这里无需也无法对所有的实施方式予以穷举。而这些属于本实用新型的精神所引伸出的显而易见的变化或变动仍处于本实用新型的保护范围之中。Apparently, the above-mentioned embodiments of the present utility model are only examples for clearly illustrating the present utility model, rather than limiting the implementation manner of the present utility model. For those of ordinary skill in the art, other changes or changes in different forms can be made on the basis of the above description. It is not necessary and impossible to exhaustively list all the implementation manners here. And these obvious changes or variations derived from the spirit of the present utility model are still within the protection scope of the present utility model.
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