CN103307211B - A kind of asymmetric involute worm worm gear pair - Google Patents

Abstract

The invention discloses a kind of asymmetric involute worm worm gear pair, comprise worm and worm wheel, the gear teeth both sides of worm screw have worm meshing side flank profil and the non-engagement side flank profil of worm screw respectively, the gear teeth both sides of worm gear have worm gear engagement side flank profil and the non-engagement side flank profil of worm gear respectively, wherein, the axial module of worm screw is m ₁, the transverse module of worm gear is m ₂, the pressure angle of worm meshing side flank profil is α ₁, the pressure angle of the non-engagement side flank profil of worm screw is α ₂, the pressure angle of worm gear engagement side flank profil is α ₃, the pressure angle of the non-engagement side flank profil of worm gear is α ₄, the addendum coefficient of worm meshing side flank profil is the addendum coefficient of the non-engagement side flank profil of worm screw is the tip clearance coefficient of worm meshing side flank profil is the tip clearance coefficient of the non-engagement side flank profil of worm screw is when worm screw, worm gear diaxon angle Σ=90 °, in order to ensure worm and worm gear energy correct engagement, meet the following conditions: a, α ₁> α ₂, α ₃> α ₄; B, work as m ₁=m ₂time, α ₁=α ₃, α ₂=α ₄; Work as m ₁≠ m ₂time, m ₁cos α ₁=m ₂cos α ₃, m ₁cos α ₂=m ₂cos α ₄deng.

Description

A kind of asymmetric involute worm worm gear pair

Technical field

The present invention relates to a kind of asymmetric involute worm worm gear pair, belong to worm and gear technical field of mechanical transmission.

Background technique

At present, because having, velocity ratio is large in worm drive, stable drive, vibration are little, low noise advantages, and is widely used.The quality of Worm and Worm Gear Driving performance and quality thereof has influence on the quality height of engineening goods the most at last, therefore, in order to meet the needs of the large production of modernization, requires that the transmission performance of worm and worm gear is continued to optimize.In recent years, in each side such as mesh theory, bearing capacity calculating, novel worm drive of worm and worm gear, very large development is all had.In worm drive process, the shape of the gear teeth not only can have influence on worm geared kinetic characteristic, but also can have influence on the power performance of Worm and Worm Gear Driving.In order to adapt to the development trend of the large production of modernization, people constantly probe into tooth profile profile of tooth, and non-equal modulus asymmetric involute worm Worm wheel transmission mechanism produces under this historical background.Under prior art, when transmission comparatively large bearing capacity time, the tooth root of worm gear easily fractures.

Summary of the invention

Technical problem to be solved by this invention is the defect overcoming prior art, provides a kind of asymmetric involute worm worm gear pair, and it can effectively avoid the tooth root of worm gear to rupture, shock resistance when improving its transmission and bearing capacity.

The present invention solves the problems of the technologies described above the technological scheme taked: a kind of asymmetric involute worm worm gear pair, comprise worm and worm wheel, the gear teeth both sides of worm screw have worm meshing side flank profil and the non-engagement side flank profil of worm screw respectively, the gear teeth both sides of worm gear have worm gear engagement side flank profil and the non-engagement side flank profil of worm gear respectively, wherein, the axial module of worm screw is m ₁, the transverse module of worm gear is m ₂, the pressure angle of worm meshing side flank profil is α ₁, the pressure angle of the non-engagement side flank profil of worm screw is α ₂, the pressure angle of worm gear engagement side flank profil is α ₃, the pressure angle of the non-engagement side flank profil of worm gear is α ₄, the addendum coefficient of worm meshing side flank profil is the addendum coefficient of the non-engagement side flank profil of worm screw is the tip clearance coefficient of worm meshing side flank profil is the tip clearance coefficient of the non-engagement side flank profil of worm screw is when worm screw, worm gear diaxon angle Σ=90 °, in order to ensure worm and worm gear energy correct engagement, meet following four conditions:

a、α ₁＞α ₂，α ₃＞α ₄；

B, work as m ₁=m ₂time, α ₁=α ₃, α ₂=α ₄; Work as m ₁≠ m ₂time, m ₁cos α ₁=m ₂cos α ₃, m ₁cos α ₂=m ₂cos α ₄;

c、 $h_{ad}^{*}=h_{ac}^{*}+c_c^{*}-(1-{\mathrm{sin\α}}_1)\frac{\frac{{\mathrm{\πm}}_1}{2}-({\mathrm{tan\α}}_2+{\mathrm{tan\α}}_1)(h_{ac}^{*}{m}_1+c_c^{*}{m}_1)}{{\mathrm{sec\α}}_2+{\mathrm{sec\α}}_1-{\mathrm{tan\α}}_2-{\mathrm{tan\α}}_1};$

d、 $c_d^{*}=(1-{\mathrm{sin\α}}_1)\frac{\frac{\mathrm{\π}}{2}-({\mathrm{tan\α}}_2+{\mathrm{tan\α}}_1)(h_{ac}^{*}+c_c^{*})}{{\mathrm{sec\α}}_2+{\mathrm{sec\α}}_1-{\mathrm{tan\α}}_2-{\mathrm{tan\α}}_1}.$

After have employed technique scheme, in the design of worm and worm gear, increase pressure angle and can improve tooth root bending-fatigue strength, thus improve its bearing capacity, for conventional symmetric involute worm Worm wheel transmission mechanism, if increase the pressure angle of gear teeth both sides simultaneously, worm gear tooth top will be caused thinning, strengthen the possibility of worm gear broken teeth, namely the shock resistance of worm gear teeth will decline, in worm-gears of the present invention, when worm drive, consider that the working surface of the gear teeth is different with the stressing conditions of non-working surface, the working flank of the gear teeth and the pressure angle of engagement side flank profil than the non-working flank of the gear teeth and the pressure angle of non-engagement side flank profil large, the both sides of the worm and worm wheel gear teeth are made all to produce asymmetric flank profil curved surface, such one side can improve the tooth root bending-fatigue strength of the gear teeth, increase its bearing capacity, can ensure that again the tooth top of worm gear has certain width simultaneously, avoid the phenomenon of gear teeth broken teeth, improve shock resistance during its transmission.The present invention compared with existing involute worm Worm wheel transmission mechanism, have bearing capacity large, rub little, heating less, the advantage such as the life-span is long.Be widely used in the industries such as household electrical appliances, automobile, instrument, Hoisting Machinery due to worm drive, wide market, the Social benefit and economic benefit of this invention is remarkable.

Accompanying drawing explanation

Fig. 1 is the structural representation of asymmetric involute worm worm gear pair of the present invention;

Fig. 2 is the structural representation of worm screw of the present invention;

Fig. 3 is the structural representation of worm gear of the present invention;

Fig. 4 is worm gear contrate tooth profile schematic diagram of the present invention.

Embodiment

In order to make content of the present invention more easily be clearly understood, below according to specific embodiment also by reference to the accompanying drawings, the present invention is further detailed explanation.

As shown in figures 1-4, a kind of asymmetric involute worm worm gear pair, comprise worm screw 1 and worm gear 2, the gear teeth both sides of worm screw 1 have worm meshing side flank profil 3 and the non-engagement side flank profil 4 of worm screw respectively, the gear teeth both sides of worm gear 2 have worm gear engagement side flank profil 5 and the non-engagement side flank profil 6 of worm gear respectively, wherein, the axial module of worm screw 1 is m ₁, the transverse module of worm gear 2 is m ₂, the pressure angle of worm meshing side flank profil 3 is α ₁, the pressure angle of the non-engagement side flank profil 4 of worm screw is α ₂, the pressure angle of worm gear engagement side flank profil 5 is α ₃, the pressure angle of the non-engagement side flank profil 6 of worm gear is α ₄, the addendum coefficient of worm meshing side flank profil 3 is the addendum coefficient of the non-engagement side flank profil 4 of worm screw is the tip clearance coefficient of worm meshing side flank profil 3 is the tip clearance coefficient of the non-engagement side flank profil 4 of worm screw is when worm screw 1, worm gear 2 diaxon angle Σ=90 °, in order to ensure worm and worm gear energy correct engagement, meet following four conditions:

a、α ₁＞α ₂，α ₃＞α ₄；

B, work as m ₁=m ₂time, α ₁=α ₃, α ₂=α ₄; Work as m ₁≠ m ₂time, m ₁cos α ₁=m ₂cos α ₃, m ₁cos α ₂=m ₂cos α ₄;

c、 $h_{ad}^{*}=h_{ac}^{*}+c_c^{*}-(1-{\mathrm{sin\α}}_1)\frac{\frac{{\mathrm{\πm}}_1}{2}-({\mathrm{tan\α}}_2+{\mathrm{tan\α}}_1)(h_{ac}^{*}{m}_1+c_c^{*}{m}_1)}{{\mathrm{sec\α}}_2+{\mathrm{sec\α}}_1-{\mathrm{tan\α}}_2-{\mathrm{tan\α}}_1};$

d、 $c_d^{*}=(1-{\mathrm{sin\α}}_1)\frac{\frac{\mathrm{\π}}{2}-({\mathrm{tan\α}}_2+{\mathrm{tan\α}}_1)(h_{ac}^{*}+c_c^{*})}{{\mathrm{sec\α}}_2+{\mathrm{sec\α}}_1-{\mathrm{tan\α}}_2-{\mathrm{tan\α}}_1}.$

The major parameter design of worm and worm gear of the present invention is as follows:

1) the axial module m of worm screw 1 ₁with the transverse module m of worm gear 2 ₂can equal (i.e. m ₁=m ₂), also can unequal (i.e. m ₁≠ m ₂), wherein m ₁, m ₂value size choose according to gear handbook or make by oneself as required;

2) flank profil of worm screw 1 gear teeth both sides is asymmetric, and the pressure angle getting worm meshing side flank profil 3 is α ₁the pressure angle of spending, getting the non-engagement side flank profil 4 of worm screw is α ₂degree, and α ₁> α ₂; Wherein α ₁, α ₂value size under the prerequisite not affecting gear teeth shock resistance, can according to user need make by oneself;

3) flank profil of worm gear 2 gear teeth both sides is asymmetric, and the pressure angle getting worm gear engagement side flank profil 5 is α ₃the pressure angle of spending, getting the non-engagement side flank profil 6 of worm gear is α ₄degree, and α ₃> α ₄; Wherein α ₃, α ₄value size under the prerequisite not affecting gear teeth shock resistance, can according to user need make by oneself;

4) m is worked as ₁=m ₂time, α ₁=α ₃, α ₂=α ₄;

5) m is worked as ₁≠ m ₂time, the pressure angle of engagement side meets m ₁cos α ₁=m ₂cos α ₃, the pressure angle of non-engagement side meets m ₁cos α ₂=m ₂cos α ₄;

6) head number, the diametral quotient of getting worm screw are respectively z ₁, q, wherein z ₁, q value can with reference to gear handbook, then reference circle of worm angle of lead degree, worm meshing side base lead angle γ _bd=arccos (cos γ cos α ₁) degree; Worm screw non-engagement side base lead angle γ _bc=arccos (cos γ cos α ₂) degree;

7) the standard pitch diameter d of worm screw is got ₁=m ₁q millimeter, worm meshing side base circle diameter (BCD) millimeter, the non-engagement side base circle diameter (BCD) of worm screw millimeter;

8) addendum coefficient getting worm meshing side flank profil is the addendum coefficient of the non-engagement side flank profil of worm screw is the tip clearance coefficient of worm meshing side flank profil is the tip clearance coefficient of the non-engagement side flank profil of worm screw is and meet:

$h_{ad}^{*}=h_{ac}^{*}+c_c^{*}-(1-{\mathrm{sin\α}}_1)\frac{\frac{{\mathrm{\πm}}_1}{2}-({\mathrm{tan\α}}_2+{\mathrm{tan\α}}_1)(h_{ac}^{*}{m}_1+c_c^{*}{m}_1)}{{\mathrm{sec\α}}_2+{\mathrm{sec\α}}_1-{\mathrm{tan\α}}_2-{\mathrm{tan\α}}_1},$

$c_d^{*}=(1-{\mathrm{sin\α}}_1)\frac{\frac{\mathrm{\π}}{2}-({\mathrm{tan\α}}_2+{\mathrm{tan\α}}_1)(h_{ac}^{*}+c_c^{*})}{{\mathrm{sec\α}}_2+{\mathrm{sec\α}}_1-{\mathrm{tan\α}}_2-{\mathrm{tan\α}}_1},$ Wherein value desirable $h_{ac}^{*}=1.0,$ also can need to make by oneself according to user, in formula, all the other each parameter meanings are the same;

9) d is got _a1for the tip diameter of worm screw, millimeter, in formula, each parameter meaning is the same;

10) d is got _a2for circle at root of gorge diameter, millimeter, in formula, each parameter meaning is the same;

11) r is got _g2for worm gear gorge rodius, millimeter, in formula, each parameter meaning is the same.

Working principle of the present invention is as follows:

In the design of worm and worm gear, increase pressure angle and can improve tooth root bending-fatigue strength, thus improve its bearing capacity, for conventional symmetric involute worm Worm wheel transmission mechanism, if increase the pressure angle of gear teeth both sides simultaneously, worm gear tooth top will be caused thinning, strengthen the possibility of worm gear broken teeth, namely the shock resistance of worm gear teeth will decline, in worm-gears of the present invention, when worm drive, consider that the working surface of the gear teeth is different with the stressing conditions of non-working surface, the working flank of the gear teeth and the pressure angle of engagement side flank profil than the non-working flank of the gear teeth and the pressure angle of non-engagement side flank profil large, the both sides of the worm and worm wheel gear teeth are made all to produce asymmetric flank profil curved surface, such one side can improve the tooth root bending-fatigue strength of the gear teeth, increase its bearing capacity, can ensure that again the tooth top of worm gear has certain width simultaneously, avoid the phenomenon of gear teeth broken teeth, improve shock resistance during its transmission.The present invention compared with existing involute worm Worm wheel transmission mechanism, have bearing capacity large, rub little, heating less, the advantage such as the life-span is long.Be widely used in the industries such as household electrical appliances, automobile, instrument, Hoisting Machinery due to worm drive, wide market, the Social benefit and economic benefit of this invention is remarkable.

Above-described specific embodiment; the technical problem of solution of the present invention, technological scheme and beneficial effect are further described; be understood that; the foregoing is only specific embodiments of the invention; be not limited to the present invention; within the spirit and principles in the present invention all, any amendment made, equivalent replacement, improvement etc., all should be included within protection scope of the present invention.

Claims (1)

1. an asymmetric involute worm worm gear pair, comprise worm screw (1) and worm gear (2), it is characterized in that: the gear teeth both sides of worm screw (1) have worm meshing side flank profil (3) and the non-engagement side flank profil (4) of worm screw respectively, the gear teeth both sides of worm gear (2) have worm gear engagement side flank profil (5) and the non-engagement side flank profil (6) of worm gear respectively, wherein, the axial module of worm screw (1) is m ₁, the transverse module of worm gear (2) is m ₂, the pressure angle of worm meshing side flank profil (3) is α ₁, the pressure angle of the non-engagement side flank profil (4) of worm screw is α ₂, the pressure angle of worm gear engagement side flank profil (5) is α ₃, the pressure angle of the non-engagement side flank profil (6) of worm gear is α ₄, the addendum coefficient of worm meshing side flank profil (3) is the addendum coefficient of the non-engagement side flank profil (4) of worm screw is the tip clearance coefficient of worm meshing side flank profil (3) is the tip clearance coefficient of the non-engagement side flank profil (4) of worm screw is when worm screw (1), worm gear (2) diaxon angle Σ=90 °, in order to ensure worm and worm gear energy correct engagement, meet following four conditions:

a、α ₁＞α ₂，α ₃＞α ₄；

B, work as m ₁=m ₂time, α ₁=α ₃, α ₂=α ₄; Work as m ₁≠ m ₂time, m ₁cos α ₁=m ₂cos α ₃, m ₁cos α ₂=m ₂cos α ₄;

c、 $h_{\mathrm{ad}}^{*}=h_{\mathrm{ac}}^{*}+c_c^{*}-(1-{\sin \mathrm{\α}}_1)\frac{\frac{{\mathrm{\πm}}_1}{2}-({\tan \mathrm{\α}}_2+{\tan \mathrm{\α}}_1)(h_{\mathrm{ac}}^{*}{m}_1+c_c^{*}{m}_1)}{{\sec \mathrm{\α}}_2+{\sec \mathrm{\α}}_1-{\tan \mathrm{\α}}_2-{\tan \mathrm{\α}}_1};$

d、 $c_d^{*}=(1-{\sin \mathrm{\α}}_1)\frac{\frac{\mathrm{\π}}{2}-({\tan \mathrm{\α}}_2+{\tan \mathrm{\α}}_1)(h_{\mathrm{ac}}^{*}+c_c^{*})}{{\sec \mathrm{\α}}_2+{\sec \mathrm{\α}}_1-{\tan \mathrm{\α}}_2-{\tan \mathrm{\α}}_1}.$