SU67425A1 - Toothed couple - Google Patents

Description

This invention relates to mechanisms for the peri (a) length of a nyirer ii nzmensn; civOpocTeii slave :) 4iix elements3. Mechanisms for the same purpose and the form of cam mechanism, or} round gears, or in the form of a combination with planetary, lever and other mechanisms do not give a complete solution to the problem.

In addition to the complex arrangement, and often a large number of details, individual elements of such programs are not very reliable and very difficult to manufacture. The latter is particularly relevant for non-circular gears.

Krame this non-circular gears have another organically inherent non-asstatsk. Reducing their potential for use: the round gear could not be connected to the linearly moving Normal rail, so it was necessary to transfer the linear motion. would introduce additional items.

5l e1s only the tooth profile, built on the involute; Evo; 1b1: et 11th tooth profile of conventional i.ap for ne1) rotation speed c) {our .1 gear ratio is a special case of the profile built by the engine. indicated below the means; the tooth can be cut into teeth milling, gear-normal 1L11 gear-shaping tugs and special tools of fixed devices.

Wheel. Sn: sliced teeth, sliced, according to the pzobrgtenlyu. can be made like this. that it would theoretically be correct for it to engage with a normal wheel or a normal rail and, with its even rotation, inform the speed of an element linked to it on the hinge element, changing from time to time according to a predetermined law. It is also possible to properly engage two special Wheels with each other, the gearing of a normal wheel with a special rail and so on. You can also make not only other teeth, and helical special wheels.

Achi m in the form of wheels with cross inns wass.

The involute profile of the teeth of rounded gears is theoretically constructed by rolling: along their centroids, the machine-oval straight line making them the slats or the half-round machine circle. In elliptical wheels, the construction of a tooth involute is also known as a sweep of a confocal centroid of an ellipse. The tooth profile of the round gear wheels of the present invention is constructed differently; their evolyuta built on buttsO || the plane of the rotary wheel as an envelope of a family of straight lines that cut a non-circular center under the same angle to the radii; Conducted 13 centers of rotation of this needle, or as an envelope of the families of circumferences described by the radii from the centers of rotation of the matching element .

This allows the cutting of the wheels to the skirt on the benches, which, as compared with the usual ones, is only an additional device that ensures an unstable relative speed between the workpiece and the tool. At the same time, the initial tool profile runs in each. perpendicular to the axis, cut the workpiece in such a way that the TO over a given centroid of the workpiece rolls without sliding the tool centroid, corresponding to a constant distance along the normal between the rotation of the workpiece section and the path of a point of the original tool profile during movement rolling in the section plane.

In FIG. 1 and 2 depict pairs of toothed gear made according to the invention; FIG. 3 - construction of the wheel tooth profile for a given profile of the matched wheel; FIG. 4 depicts the contact of the conjugate teeth of the neodTgak form; FIG. 5 is a diagram for finding the 1-min total number of Lara teeth from undercutting conditions with a rake tool; FIG. 6- tooth profile at the location of the pole outside the wheel tooth; FIG. 7 diagram. Two consecutive wheel gears; FIG. 8. 9, 10- crr: out. depicting graphs of changes in the angular velocities of the wheels, built but with different given functional dependencies; FIG. II - the scheme of engagement of the maximum allowable in. П, drezu teeth with a rack and pinion tool; FIG. 12- construction of the wheel evolut manufactured by a rack and pinion tool; FIG. 13 - ps; the structure of the wheel evolute, manufactured by Yulb.

The well-known methods of constructing tooth profiles (Camus, Relo, Poncelet methods) are based on the Willis theorem on the absence of an abbreviation for the constant passage of a common normal to a profile m through a gear pole.

It does not matter whether the two wheels rotate or one remains stationary, while the second rolls around it.

Constructions are applied only to a particular case of a revision rotated by direct contacting bodies, and this is assumed to be. that the engagement pole invariably remains on the center line. At the same time, the polloids in relative motion are k-mete form of circles.

However, in the general case of the transfer of the Splint directly by the contacting bodies (teeth), the pole of the gearing changes its position in the other rotating bodies. The law of changing the position of the pole of an engagement can be any, and its choice determines the profiles of the interlocking bodies.

Pollovdy take the form of curves, more complex than the circle. For given polloids and the profile of one 1IZ teeth, it is possible in this general case to construct a conjugate profile (Fig. 3).

Poncelet Conduct a polloid arc defined by a given law.

--i- - f (t) (in the standard nocTpociKiH

and)"

Draw arcs of a circle); Let the profile rniin of the tooth of the wheel / and POLLOILY / - / and be given. On polloids / - / and 2-2 otkladivasm several equal segments and from the obtained points on the polloid / - / we draw normals to the mimi profile. From the points obtained in the 2-2 polloid, we draw arcs of circles with radii corresponding to the length normal to the given profile Wimi from the points of the polloids / - /.

The envelope of these arcs will present the desired profile of the second wheel. To finish building a tooth profile, one needs to: first, restrict (its height in height and, second, observe equality of steps along pollo curves / - / and 2-2.

It is not necessary that the polloids be located within the teeth. The engagement may be correct if the teeth do not intersect the polloid (Fig. 6).

Thus (the height of the teeth can be limited by a circle regardless of the location of the polloid and, therefore, circular gears with variable pitch can be obtained to transmit the rotation with a continuously variable 1 gear ratio. The larger the range of the periodic variation of the transfer number, the greater the ne1) The pole of engagement is metered and the largest and smallest steps, measured by this pitch circle, differ more.

Correct engagement of "small-sized teeth with" large hollows and, conversely, is fundamentally nothing. It does not differ from engagement in "normal gears with large mixing gears of the MI tool. -Casalia of the teeth may occur at points far removed from the middle of the height of the tooth (Fig. 4). Only compliance is required

the equality of the teeth of one wheel and the width of the depression of the other, measured by polloid curves.

The V.loe-shaped curves pass outside the teeth of the 1-wheel, then between the 5 teeth of one wheel and the trough of the other, with their relative symmetrical center position, a gap that does not prevent unstressed work, the gap means that the pole zatse 1len ;; there is a stump of the circumference of the vortex of one wheel and inside: O-LUGS. SHIDIN (FI1)).

11. such one-sided delay. which can also occur in conventional wheels, profi.T :: theoretically touch each other on its continuation beyond the teeth.

Actually. Touching the working profiles on the engagement line will be completely normal only on one side of the Lynch center;

Each | 1 vadipo one wheel to. -1jo; 1 correspond to the definition of a Hiii parsogs tooth wheel. Thus,; 6; i wheels have a special tooth profile, then the lack of numbers of teeth from more than one co-leg to less. (Average gear ratio) can be expressed as TOL1. LO with the first number. In order to demonstrate the possibility of manufacturing wheels according to the invention, the south is very briefly illuminated by 11p;: in. -production of wheels with variable .m step running by the method of using the 1H (Formuioi standardioioii form.

The tooth profiles will be sound in the most general sense of the word.

Indeed, the general normal to the point of contact of the teeth will not be fixed power lines of the center and therefore cannot be tangent to some constant main circle M. But since the change in the position of the normal is temporarily dependent only on the shape of the colloidal curves and on the shape teeth (required by law

- f (t) can be implemented.

If there is a countless number of different conjugated pairs of profiles, then the curves to which the general normal is upon rotation: the wheels will be all but tangent. the polondoms and the shape of the teeth are strictly defined.

Since any tangent to such a curve is normal to the profn; but the tooth of his “ole. This curve is the locus of the centers of curvature, i.e. the evolute tooth profile.

In order to obtain a round wheel, the distance between the axis of rotation of the workpiece and the tool must remain unchanged when cutting. If the tool (dolb) repeats in shape one of the made gear wheels, then the law of variation of the angular velocities between (the wheel and the tool are the same as the given law.

The tool is the normal Fellow hollow, but with the same number of teeth as the "normal wheel of the pair to be made. A pair consists of 1; from a single wheel with a “constant tag and another with“ variable. There is nothing paradoxical in this pet, since in reality the steps along the palloid curves will be the same and variable on both wheels.

Evolution of a "normal wheel" represents the main circle. and evolyu another wheel - pain complex curve. The tangents to both evoles change their position in the process of engagement, without remaining parallel.

FIG. 43 bs-kazano loluchenie evolyuty articulated with the “normal special Kc: ieca. Motley held by the method of reversed motion. The centroid of the special colgus remains motionless. (Vza.menu its rotation} 1 and moves the line of centers around Oj. H from any point of its intersection with the centroid, i.e. the engagement poles, is tangent to the corresponding position of the main circle. The envelope, the families of these are direct and is skom evolyu However, you can set a goal

get the same law - / (/)

1 | C1Shbrav such that their common tangent in the process of engagement. Moved progressively.

In this pair, none of the wheels will have permanently shaped teeth. A pair of gears with such evolutions (and, therefore, with defined tooth profiles) can be manufactured with a straight profile (a comb, a wrench).

In the event the machine engagement will not repeat valid. At the same time, the evolution of the evolyuts will change its own (; position, but due to the straightness of the teeth of the tool, the line will remain permanently on itself. Its reduction in each lument will be determined by rolling the pollondl reiki curve along the given

  fit)

the laws

Polloid 1,

KpiiBoii wheels. In contrast to “normal engagement, the rail will not have a polloid straight line, but a polloid curve.

The PaccTGoiHue between ;, the rail (inCTpyMCiiTOM) and the center of the workpiece remain unchanged during the running-in process.

It is clear that the teeth will be G;: MET (Other

profile than in the manufacture of ds 1b com, but by changing the wheels, the law of variation of the angular velocities may remain the same. By making both wheels with the same tool, each time providing a roll of a 1-POLOID rail curve along the lollide curve. Each of the wheels :, .. we reach that both wheels can glue without gaps (or with a constant gap) when rolling them, the polloid is non-slip.

will be quite pain. cut Z .. ,, we sew.

In addition, there is a need for a large angle of engagement a, which, in turn, can lead to sharpening of the teeth.

However, in order to practically carry out such a transfer with small dimensions and without sharpening, you can do simply, namely:

1. Use a rail with a possible height difference coefficient // "(//" should be taken several times smaller than the standard for wheels with a constant pitch).

2.To obtain sufficient overlap, it is necessary to make the helical gears.

With THIS. M you need to remember that (5

In our case, the coefficient of overlap is the value of the transducer, the change of ush s in the process of & panieiniH wheels, and the weight and calculation on the pole of the gearing in one of its extreme positions, appropriate (transfer ratio / check or

niin

Thus even one can achieve significant we.Schchin / c. To obtain very large variational numbers g, it is necessary to make several consecutive pairs.

FIG. 7 depicts two successive pairs: I, 2 and 3, 1; their variational number

four

"Ojw, in the drawing we have w,

ABOUT)

4 Ш1П

Zschah

W „

sh „

shah

4 niii

rJmax rchshp

(O. g. - w. Zyah imaxi

p2niin imia 3 min.

sh. . g (0 „. Jmin2min p4tah

./.

.h

-j n ;; ri

 iniax -m; rx. ch -Irnjx

ftfjfjff

  mill - tiiin -i nnii -liiiiii

  12 3-4 The total variational number when

(n + 1) consecutive pairs will be

“OL / L ;. : t.J./rf 2n H-1, 2n-2It is possible to indicate several typical cases of transmission during a pair of gears.

FIG. 8 depicts a pair with such a law of change / that when it is higher (PP1. Smaller .-. Scaffold with constant angular velocity more than several times per revolution, periodically repeats unevenly the same law.

According to FIG. 9 larger wheel per turn only changes once

speed c0). ,,., (0, „|„.

According to FIG. 10 at one m turn of a large wheel with a constant angular speed. A smaller one changes the angular speed from (, „, up to several revolutions.

Subject invention

Claims (1)

1. A pair of cogs with non-circular centronts defining the law of displacement of the engagement pole along the LITCHE of the zeitro component and its teeth profile, which is constructed from the evolute sweep, with the evolute no: : Tj) voeHa at the end of the 5th plane of the Bpa-uaicmerccH wheel as an envelope of the family of direct, intersecting a non-circular centroid with the same angle to the radius, drawn from cent) of the rotation of this element, and as an envelope of the family of tangent to a circle. m, written off by a given radius from the center of rotation of the conjugate evil . L. Zubchat couple according to claim 1, which differs from the fact that the step of engagement of the same p of the same element, which is measured along the center of the le, is marked by its ability to be E. 4. A tooth pair according to claim 1, except for; and with the fact that one of its wie.MOHTOBs can be performed with the volatile teeth of a constant tag. 5. Zubchat couple under item 1, from l and so that the tooth of its elements are inclined to the generator. 6. Zubchat), a pair according to item I, is different from P1 and the fact that the pox of its elements intersect. 7. Zubchat pair according to claim 1, the difference is that one of its elements is made in the form of a lath. The change law for HfinoSbif speeds / (half dkaipaffml FIG. 2 (Qnoud tt K iri8e Lines of Protrusions Reiki when processing when processing. 1 wheels -: 2 wheels -57 :: p |; a rsllr FIG. 3 Preset FIG. four Lineyentrob FIG. five Lo 67425 - 10 FIG. 6 centers FIG. 7