SU922358A2 - Straight-tooth cylindrical gearing - Google Patents

Description

(5) DIRECTLY CYLINDRICAL TRANSFER

I

The invention relates to machine tripling and can be used in gears with increased smoothness of operation.

According to the main auth. f is known spur cylindrical gear P1, containing gears meshing with each other, the outer surfaces of the gear rims of which are made with conical faces, arranged symmetrically with the mid-plane of the wheels,

Ste. „, COSdl“ WS “d4,. (

, llS, (f- for u / esteren; ah., OOSd4e WS "" 4% t |) (

, (i J "| leln4") (-dl wheels,

the circumference of the small bases of the cones of the chamfers of the gear wheels are located on the sections of the heads of the teeth, limited, on the one hand, by the upper boundary points of one-pair gearing, and by the other, by limiting points, with a coefficient of overlap equal to one when engaged with similar wheels, their diameters

10 wheels in gearing with a smaller overlap ratio according to dependencies where m is the gearing module; And - the angle of the original contour; d-w is the engagement angle; auj is the center distance of the engagement; c (an vi3aV.- diameters of the tops of the teeth of the gear and the wheel; Zxx m and a wV diameters of the initial circles of the gear and the wheel;. In addition, the transfer wheels can be made with a cylindrical section on the teeth of the teeth, the value of which is defined. Ti-b V Sa where 4 is the coefficient depending on the number of teeth and shear coefficient; b is the width of the ring gear; Sa is the cord thickness of the peaks. The disadvantage of this transfer is that when the tooth is dangerous, from the point of bending of the tooth, tooth apex coefficient taking into account the unevenness of races the load is divided by the width of the ring, is not equal to the minimum value, the distance is 1. Moreover, it is more difficult to break in the teeth, since the minimum possible length of contact lines cannot be less than b, and the total length of contact lines varies from b to (b + ba). The purpose of the invention is to provide accelerated teeth break-in, an increase in load capacity, reliability and durability of the transmission. To achieve this goal, flat cuts are made on the side surfaces of the teeth heads symmetrically to the mid-plane of the wheels This section passes through the extreme point of the arc of the circumference of the small base of the chamfer cone, the extreme point of the circular arc of the tops of the teeth located in the middle flatness of the wheels, and the extreme point of the arc of the circle of the large base of the chamfer cone, whose position is determined by the depth of the flat section in the section coinciding with the large axis (A new chamfer cone is equal to ac (0.705-1.0) K, 84 where 0.705-1.0 are the probable coefficients that take into account the mutual influence of manufacturing inaccuracies and the mounting of the wheels to the depth of cutsJ audio and mounting the gears, taking into account inaccuracies with regard to the one wheel. FIG. 1 shows the gears of a modified spur-shaped cylindrical involute transmission, axial section; in fig. 2 is a view A of FIG. 1 when performing non-reverse gear; in fig. 3 is a view of L in FIG. 1 when performing a reverse gear; in fig. C - gear ring gear, axial section; in fig. 5 is a section BB in FIG. in the plane of the large base of the conical chamfer in the case of reverse gear; in fig. 6 shows a section B-B in FIG. k in the plane of the large base of the conical fisc in the case of non-reversing gear; Fig. 7 shows a gear ring of a wheel with a cylindrical section on the tops of the teeth with a width equal to the width of the ring gear, an axial section. The cog gear is composed of modified cylindrical spur-like evolvent gears 1 and wheel 2. The outer surfaces of the gear rims of the gears and wheels are coned symmetrically relative to their middle plane 7 while the cylindrical sections 8 and 9 are kept on the tops of the teeth along the plane 7 of symmetry. In addition, flat sections 10 and 11 are made symmetrically to the middle plane 7 on the heads of the teeth. In the case of reversing gear, flat sections 10-13 are made on both sides of the heads of the teeth (FIG. 3 and 5), and irreversive - on one side only (FIG. .2 and 6). The width of the cylindrical sections 8 and 9 on the tops of the teeth is determined by the dependence of r .. gr & Mf- is the coefficient depending on the number of teeth and the coefficient of shear;

b is the width of the ring gear; SQ - chordal thickness of the tooth tip.

The circumferences of the 1J-17 small bases of the cones 3-6 are located in the face planes of the rims within the areas of the heads of the teeth and are limited, with

THncoscLtflw «« d4, .j (i «lL). (I | S.j. Fe) 4

dliws

 . for gear.

 - |. B .. m. () - ((%) Jr JT-muoSdc, m. (F for wheels ,, .. .. where m is the engagement module; di is the angle of the initial contour; cLw is the engagement angle; C (V (/ is the center meshing distance; dQrn, yoK - diameters of the tops of the gear and wheel teeth; dbm, 3bV-, - diameters of the main circles of the gear and the wheels j elNMW, (- diameters of the initial circles of the gear and the wheel. Circles 18-21 of the large bases of the cones 3-6 are the same with the circumferences of the heads of the teeth passing through the limit points of the cylindrical sections 8 and 9. Each of the flat cuts is made passing through three characteristic points on the corresponding The main part of the head of the tooth: the extreme point 22 of the arc is the circumference of the small base of the chamfer cone, the edge is up to the point 23 of the arc of the circle of the tips of the teeth located in the middle plane 7 and the extreme point 2 of the arc of the circle of the large base of the chamfer cone, the position of which is determined by the condition due to manufacturing and installation errors. The amount of error compensation for the manufacture and installation of gears, taking into account inaccuracies in relation to a gear or a wheel, is determined by the dependence It)) J-,

Claims (1)

one side; the upper boundary points of a one-pair link, and on the other, limit points with an overlap factor equal to one. The diameters of these circles are determined from the condition that the teeth enter into engagement with a smaller overlap ratio according to dependencies where Fjj is the tolerance for the error in the direction of the teeth; f) (- tolerance for non-parallelism f., - tolerance for misalignment of the axes; d, - angle of the initial contour equal to 20 °. I The recommended depth of flat cuts in sections of large bases of conical chamfers is determined by the dependence of ac (0.705-1.0 ) K, where 0.765-1.0 are likely coefficients, taking into account the mutual influence of manufacturing inaccuracies and mounting on the depth of cuts. In the case of reception, a cylindrical gear with teeth modified only by flat cuts on the heads is obtained (.g. 7) In the specified options of modification of profiles zub.ev wheels The blunt cylindrical involute transmission coefficient, which takes into account the distribution of the load across the width of the toothed curl Kpj, is equal to one, since the contact area at the top of the tooth is reduced to zero by flat cuts, as a result, during the transmission, firstly, at the entrance and exit teeth from engagement, the load is always applied at the top in the middle of the tooth, secondly, the stress at the base of the tooth decreases; thirdly, the probability of cutting off the tooth tops decreases, since in this case at the point contact of the teeth at the entrance their exit from the engagement, the cross-sectional area at the tips of the teeth is not zero, and as the teeth breaks in, the point contact becomes linear, and therefore the likelihood of cutting the tips of the teeth further decreases, fourthly, conditions for accelerated grinding of teeth are created. in zones of two-fold engagement. In addition, the proposed transmission is kept almost constant on the engagement stiffness at fractional values of the overlap coefficient. As a result, the transmission has a low vibroactivity. The use of the invention makes it possible to increase the reliability of the transmission by reducing the stresses at the base of the teeth at the time of their entry and exit from the engagement by approximately 20% compared with the basic invention. The reliability of operation also increases due to improved Transmission dynamics due to the accelerated running-in of the teeth of the wheels in the areas of two pair gears. The use of more advanced gears will improve the operational and economic performance of machines, machine tools, etc. Claims of the invention of the Mozub cylinder transmission according to the author. St. No. 769N9, about tl and 8 that, in order to ensure accelerated grinding of the teeth, increase the load capacity, reliability and durability of the transmission, flat cuts are made on the lateral surfaces of the heads of the teeth symmetrically to the mid-plane of the wheels, each the cut passes through the extreme point of the arc of a circle of the small base of the chamfer cone, the extreme point of the arc of the circle of the tips of the teeth located in the mid-plane of the wheels, and the extreme point of the arc of the circle of the large-base of the chamfer cone. the position of which is determined by the flat section depth in the section coinciding with the large base of the chamfer cone, equal to ac (0.705 1.0) K, where 0.705-1.0 are probable coefficients, taking into account the mutual influence of inaccuracies in the manufacture and mounting of the wheels to a depth cut; To the amount of compensation of errors in the manufacture and installation of gears, taking into account inaccuracies with respect to one wheel. Sources of information taken into account during the examination 1. USSR Author's Certificate No. 769149, cl. F 16 H 1/08, 1977 (prototype). one FIG 2 fig.Zo bo Fi.5 FIG. 6 B la