WO2017030471A1

WO2017030471A1 - Bi-directional pin-cycloidal gearing of two wheels and a mechanism with gear wheels

Info

Publication number: WO2017030471A1
Application number: PCT/RU2016/050026
Authority: WO
Inventors: Анатолий ТОКАРЬ
Original assignee: Анатолий ТОКАРЬ
Priority date: 2015-08-14
Filing date: 2016-08-11
Publication date: 2017-02-23
Also published as: RU2015136203A

Abstract

A bi-directional pin-cycloidal gearing of two wheels is characterised in that the addendums of each wheel have a round convex profile, and the dedendums of each wheel have a trochoidal concave profile, which is tangentially connected to the profile of the addendums. In internal gear sets with a small tooth differential, the first point of contact appears in the middle of the depth of the tooth, in the region of the bending of the curvature of the profiles, with an infinitely large relative radius of curvature, and during subsequent rotation, two diverging points of contact are formed on one tooth - one on the dedendum, and a second on the addendum - which diverge, one towards the root of the tooth, and the second towards the tip, while maintaining the convexo-concave contacts and forming two lines of engagement. The resultant sliding velocity in the case of two such lines of engagement is less than in the case of one, and a ratio of mesh greater than one can easily be provided. Reduction gear mechanisms are also proposed, in which a plurality of profiles, having a different number of teeth, can be constructed on a single gear wheel, said profiles being coupled with the same second wheel, with the same unchanged profile of teeth on the second wheel and an unchanged centre-to-centre spacing. The use of such gear wheels during the engineering of new reduction gears leads to a simplification in the design and a reduction in the weight of said reduction gears.

Description

Title of invention

Bilateral gear-cycloidal gearing of two wheels and a mechanism with gears.

Technical field

The invention relates to mechanical gears for conversion

rotational motion using gearing of the wheels with a tooth profile containing in combination circular and cycloidal sections, and can find

application in various gears that previously used gearing with involute and other tooth profiles.

In the description and claims, the term “elongated epi- or hypotrochoid” should be understood to mean cycloidal curves that do not have self-intersections, and the term “shortened epi- or hypotrochoid” should be understood as curves having self-intersection in the form of loops at the vertices.

State of the art

A planetary gear is known in which the tooth profile of one of the wheels is formed by an equidistant loop of a shortened epitrochoid, and the teeth of the second wheel have a convex circular profile. In this invention, a profile based on a shortened epitrochoid loop was used instead of the elongated epitrochoid, which was previously used in such devices, which made it possible to increase transmission service life, reduce rotation unevenness and reduce noise. (U.S. Patent 5,707,310; 01/13/1998)

The disadvantage of this transmission is that only the tooth heads (lugs) work on one wheel, and only the legs (interdental cavities) on the other and

The opportunity of using additional interacting profiles located on the same wheels in between the teeth was used.

Also known is a cycloidal gearing of two wheels, in which the first wheel contains a plurality of lugs evenly distributed around the circumference, and the second wheel has a plurality of teeths made in the form of cavities having a trochoidal profile. In this invention, the inventor most fully revealed the possibilities of chain-cycloidal engagement with the illustration of various options

trochoidal profiles. Using such profiles eliminates

interference between the mating elements regardless of the size of the teeth, which allows the construction of more compact and more durable gears. (U.S. Patent 7,086,304 of January 7, 2005) (Prototype for the first n.a.

The disadvantage of this transmission is that only the tooth heads (lugs) work on one wheel, and only the legs (interdental cavities) on the other and The opportunity of using additional interacting profiles located on the same wheels in between the teeth was used.

A known planetary gear mechanism in which at least one satellite has simultaneous engagement with two coaxial central wheels. (Book: Maslennikov M. M., Rapiport M. S. “Aircraft piston engines”, ed. “Oborongiz”, M. 1951, pp. 603 - 614, Fig. 341) (Prototype for the second n. p-that f-ly).

The disadvantage of this mechanism is that when using cylindrical gears with known tooth profiles, it is impossible to obtain the same number of teeth on two coaxial central wheels with a single-shaft satellite.

Disclosure of invention

The first objective of the invention is the creation of double-sided chain-cycloidal gearing, which differs from the known, one-sided, in that the tooth heads of the first wheel have a circular profile, which is paired with

the interdental cavities of the second wheel having a trochoidal profile, and at the same time, the tooth heads of the second wheel located between the cavities also have a circular profile, which is likewise mated to the interdental cavities of the first wheel, which are located between the circular heads. Moreover, the profiles of the interdental cavities on both wheels are tangentially connected to the circular profiles of the tooth heads and are thus the profiles of the tooth legs on each of the wheels.

The technical result. With such tooth profiling, an increased load capacity can be obtained by increasing the reduced radius of the contacting surfaces and increasing the number of points of simultaneous contact in engagement. In addition, with such profiling, it is possible, with the same centroids and the same number of teeth, to smoothly vary the radius of the heads, the height and thickness of the teeth, which represents a certain flexibility in the design, for example, to select the necessary tooth rigidity or a given necessary coefficient end overlap.

The trochoidal profile of the tooth legs of each wheel in the present invention for all variants is constructed using one general mathematical formula defining a trochoidal (cycloidal) curve, the equidistant of which will be the profile of the tooth legs. The main and sufficient initial parameters that are introduced into this formula are:

Aw - center distance;

rl and r2 are the centroid radii of the first and second wheels, respectively; RUKI AND RUK2 are the radii of the circles on which the centers of the profile circles of the tooth heads of the first and second wheels are located, respectively.

This mathematical formula (the equation of a trochoidal curve in rectangular coordinates) has the form:

x = Aw * cos t +/- Yatsk * cos (k * t)

y = Aw * sin t - Yatsk * sin (k * t)

Where:

“+/-” - means that to get hypotrochoid you need to take the “+” sign, and to get epitrochoid you need to take the “-” sign;

"*" - a sign of multiplication;

x, y are the Cartesian coordinates of the points of the epi- or hyprochoid;

t - variable (argument) - angle of rotation of the center of the rolling circle

(a centroid rolling over without sliding along another centroid, and a point connected with it (a drawing point) located at a distance from Yatsk from the center of the rolling centroid draws a trochoidal curve);

k is the coefficient at the angle of rotation, which is a single-valued function of the centroid radii rl and r2.

To obtain the value of the coefficient "k" four different versions of the equations are used:

1) For the epitrochoid of the tooth legs of the second wheel with external gearing:

k = Aw / rl = (r2 + rl) / rl, (value Jack = Jack1)

2) For the epitrochoid of the tooth legs of the first wheel with external gearing:

k = Aw / r2 = (rl + r2) / r2, (value Jack = Jack2)

3) For the hyprochoid of the legs of the teeth of the second wheel with internal gearing: k = Aw / rl = (r2 - rl) / rl, (value Yatsk = Rind)

4) For the epitrochoid of the legs of the teeth of the first wheel with internal gearing: k = Aw / r2 = (r2 - rl) / r2, (value Yatsk = Yatsk2)

To obtain real profiles of the tooth legs, we take equidistant curves from these obtained trochoidal curves with the values of Hs1 and Hats2.

Hats1 and Hats2 are the values of the radii of the profile circles of the tooth heads of the first and second wheels, respectively.

A second object of the invention is to provide mechanisms with gears, in which at least one first gear has a simultaneous or alternate engagement with at least two other gears. Moreover, all first wheels are the same and the center distance of each first gear the wheels with each of the other gears are the same, but, in contrast to the known mechanisms, the number of teeth in each of the other gears can be set different, any selected from a certain acceptable range, depending on the trochoidal curves used, which are used to profile the teeth of the remaining wheels starting from the maximum allowable shortened trochoidal curves, to the maximum allowable elongated. Moreover, the tooth profile of each of the remaining gears containing trochoidal sections, with a different number of teeth, remains mated to the same tooth profile of the first wheels containing circular sections. The technical result is to simplify the design and reduce the weight of the mechanisms created by this invention.

In particular, to obtain a differential planetary mechanism with two output shafts of opposite rotation, to transmit the same power to each output shaft at the same speed of rotation, a planetary mechanism with single-pinion satellites is used, in which one output shaft is connected to the central external gearing wheel (solar) and the second output shaft is connected with the central wheel of the internal gearing, the carrier is fixed freely rotationally around the central axis. In the proposed planetary differential gearbox, both central wheels have an equal number of teeth. When the carrier is fixed, this mechanism provides equal speeds of rotation of the output shafts in opposite directions, regardless of the power on the output shafts.

The second particular embodiment of this invention is a planetary gearbox with three central wheels. The technical result in this case is to obtain a gear ratio, significantly greater than what can be obtained from one stage of the known planetary gearbox without increasing its size. The problem was solved in that a second central gear wheel was added to the planetary gearbox with a different number of teeth than the number of teeth in the first central gear wheel. These two internal gear wheels are engaged with the same satellites, each on its own part of the width of the gear rims. The first internal gear is fixed, and the second is connected to the output shaft. The gear ratio of such a gearbox is calculated as in the David mechanism, which is described below, in the description of FIG. 12.

Another particular case of the invention is a planetary gear with four central wheels, one of which is an external gear wheel, and the other three are internal gear wheels. The technical result in this case is to obtain both a large gear ratio and the receipt of two coaxial output shafts rotating in different directions. The problem was solved by the fact that the planetary gearbox used three internal gearing wheels with a different number of teeth, each of which engages with the same satellites, each on its own part of the width of the gear rims. In this case, the external gear wheel is connected to the input shaft, one internal gear wheel having an average number of teeth is fixed motionless, and the other two internal gear wheels are connected to two coaxial output shafts and have: one of them, more teeth than in motionless a fixed wheel, and a second, fewer teeth than a fixed wheel.

Brief Description of the Drawings

Figure 1 shows the principle of constructing the profiles of the wheels of the external gearing. In FIG. 2 shows the principle of constructing tooth profiles.

In FIG. 3 the profiles of the external gear wheels in FIG. 2 and 3 in finished form. In FIG. 4 construction of an internal gear wheel for a pair of external gear wheels.

In FIG. 5 pair of gears of internal gearing with gear

ratio of more than two.

In FIG. 6 construction of two wheels of internal gearing for a pair of wheels of external gearing.

In FIG. 7 a pair of internal gear wheels with a gear ratio of two. In FIG. 8 profiles of internal gear wheels with a small tooth difference.

In FIG. 9 is a fragment of the gearing of the wheels in FIG. 8, with twice the number of teeth.

In FIG. 10 is a profile of wheels, a fragment of which is depicted in FIG. 9.

In FIG. 11 the wheel profile in FIG. 8, but with an increased number of teeth.

In FIG. 12 kinematic diagram of the planetary gear of David and the profile of the second pair of wheels for him, as well as the kinematic diagram of the planetary gear with three central wheels.

In FIG. 13 wheel planetary gear profiles.

In FIG. 14 kinematic diagram of a planetary differential gear and a planetary gear with four central wheels and wheel profiles for them.

In FIG. 15 gear profiles for gear shifting.

In FIG. 16 shows a gear profile obtained from a profile such as in FIG. 8, by doubling the number of teeth and their trimming. In FIG. 17 shows a kinematic diagram and gear profiles in a gear assembly with a gear ratio of 2, 18.

In FIG. 18 shows the types of construction of the gearbox assembled by

kinematic diagram and with gear profiles in FIG. 17.

In FIG. 19 shows the types of construction of the gearbox assembled by

the kinematic diagram of FIG. 17 with a gear ratio of 12.46.

In FIG. 20 shows the types of construction of the gearbox assembled by

the kinematic diagram of FIG. 12 upper left, with a gear ratio of 82.

Embodiments of the invention

Figure 1 and Figure 2 shows the principle of constructing the profiles of the wheels of the external gearing of the present invention. In this example, the dimensions of the transmission are taken in relation to the existing differential planetary gearbox for a turboprop aircraft engine: Aw = 121.5; rl = 67.5; r2 = 54; Z1 = 20; Z2 = 16. For simplicity, the profile circumferences of the tooth heads will be called “lobes”. The procedure for obtaining wheel profiles is as follows:

1) To obtain the profile of the tooth leg (interdental hollow) on the second wheel based on the loop of a shortened epitrochoid, first we build the epitrochoid itself: we set the spacing of the first wheel relative to the centroid: el = 4 mm, while Yatsk1 = rl + el = 67.5 + 4 = 71.5 mm.

2) We set the radius of the foregrip of the first wheel: Riil = 5.5 mm (the selection of this radius is made so that the gaps between the sprockets on the circumference of the Yack are approximately equal to the diameter of the foregrip).

3) We calculate the coefficient k = Aw / rl = 121.5 / 67.5 = 1.8

4) We enter the obtained initial parameters in the equation of the trochoidal curve given in the section "Disclosure of the invention". To simplify the entries, instead of rewriting the whole formula each time, we will write only the initial parameters in a standard form in the following form:

{Aw - Yatsk - k} for an epitrochoid;

{Aw +/- Yatsk - k} for a hyprochoid.

For our desired epitrochoid (1), the initial parameters will be:

{121.5 - 71.5 - 1.8}.

5) To obtain the profile of the interdental cavity of the second wheel, we take

equidistant with Hats1 = 5.5 mm from the loop of the epitrochoid (1) and we obtain the desired profile (2).

6) Copy the profile (2) with rotation by one angular step: 360 / Z2 = 360/16 = 22.5 degrees. 7) We have two profiles (2) symmetrically to the horizontal axis (3), in the same figure (see the right in Fig. 1) we display two sprockets (4) of the first wheel in their places, they

automatically occupy a tangent position with profiles (2) of interdental cavities.

8) We determine the initial parameters for the epitrochoid of the tooth leg of the first wheel:

Aw = 121.5;

k = Aw / g2 = 121.5 / 54 = 2.25.

Here we do not know only the “e2” value, the loop width of the desired epitrochoid depends on the choice of the “e2” value; therefore, we need to choose this value so that the desired epitrochoid (5) ensures that the profile of the tooth leg (6) of the first wheel touches the pin (4) . In this example, the “e2” value was obtained graphically by the method of successive approximations, which is illustrated in FIG. 2.

9) We initially set the value of e2 = 3.2 mm, determine Yatsk2 = r2 + e2 = 54 + 3.2 = 57.2; we place the forearm (7) of the second wheel on the horizontal axis (3) with a spacing e2 = 3.2 mm, draw the circumference of the forearm so that it touches the profiles (2) and measure its radius, which turned out to be equal to Ax2 = 4.884 mm.

10) Enter these initial parameters in the equation: {121.5 - 57.2 - 2.25}. As a result of solving this equation, we obtain curve (5) and, after taking the equidistant with a value of Нc2 = 4.884 mm, we obtain profile (6), which in this case turned out to be short-lived before pin (4) (see Fig. 2, Fig. To the left) .

1 1) Increase the value: e2 = 4.5 mm and repeat steps 9) and 10), as a result we get overlap (see Fig. 2, Fig. To the right).

As a result of subsequent successive approximations, we obtain the contact of the profile (6) with the bores (4) (see the figure on the right in Fig. 1) and we obtain the exact values: e2 = 3.7593 mm; Hats2 = 5.0855 mm; Yatsk2 = 54 + 3.75593 = 57.7593 mm. For our desired epitrochoid (5) (Fig. To the right in Fig. 1), the initial parameters will be: {121.5 - 57.7593 - 2.25}. These are the parameters of the epitrochoidal curve in which the profile (6) of the tooth legs of the first wheel will be tangent with two profiles (4) of two tooth heads of the same wheel.

In FIG. 3, the top left shows a finished pair of wheel profiles (8) created in FIG. 1 and FIG. 2 in a 13-degree rotation position of the first wheel, in which one tooth (9) comes into contact and the second tooth ( 10) is close to getting out of contact. The figure at the bottom left (1 1) shows the possibility of doubling the number of teeth while maintaining the shape of the profiles and the reduced radius of the contacting surfaces by turning the original profiles (8) by half a step, followed by mutual cutting. The number of points of the leading contact (12) in this case doubles, as can be seen in the enlarged view "A".

In FIG. 4 shows that for the first external gear wheel of a pair of wheels (8) shown in FIG. 3, there is a single third internal gear wheel whose profile is mated to this wheel. The parameters of this wheel clearly depend on the parameters of the initial pair of wheels: the first wheel remains unchanged with its profile, Zl = 20; Yatsk1 = 71.5; Hats1 = 5.5 mm. The centroids, gear ratio and other parameters of the new pair will be different, they depend on the parameters of the original pair:

NKZ = Aw = 121.5 mm;

Aw3 = Yatsk2 = 57.7593 mm;

k3 = r2 / rl = 54 / 67.5 = 0.8;

NAC3 = NAC2 = 5.0855 mm;

Z3 = Zl * Aw / rl = 20 * 121.5 / 67.5 = 36.

To build a hypotrochoid (13), on the basis of which we obtain the profile (14) of the interdental hollow of the third internal gear wheel, we have all the initial parameters that are inserted into the equation of the trochoidal curve:

{57.7593 +/- 71.5 - 0.8}. In FIG. 4 also shows a view “A” - an enlarged fragment of the engagement of the first wheel with the third. The arrow (15) shows the direction of rotation of the first wheel. Small circles in this view display three points of the leading contact. It is characteristic in this view that the teeth above the line (3) at similar points have a braking contact (not shown). View "B" is an enlarged fragment of the engagement of the first wheel with the second. It shows two points of the lead contact, above and below the line (3).

In FIG. 5 shows a pair of gears of internal gearing. The given initial data are as follows: Aw = 50; rl = 40; g2 = 90; e1 = 0.4mm; Yatsk1 = 40.4; Yats1 = 3.2mm; e2 = 5, 2725 mm, - the value of “e2” was obtained in the same way of successive approximations as for the pair in FIG. 1. For the second wheel of internal gearing Yatsk2 = r2 - e2 = 90 - 5.2725 = 84.7275mm; Haz2 = 2.70805 mm - this value was obtained in the same way as for the pair in FIG. 1. Calculate the "k" for the hyprochoid (13) of the tooth legs of the second wheel: k = Aw / rl = 50/40 = 1.25. For the hypothyroid of the tooth legs of the second wheel, the initial parameters will be: {50 +/- 40.4 - 1.25}. We calculate the “k” for the epitrochoid (5) of the teeth of the first wheel: k = Aw / r2 = 50/90 = 5/9 (this is a simple fraction, and it is possible to insert it instead of the decimal in the equation). For

epitrochoid of the legs of the first wheel, the initial parameters will be: {50 - 84.7275 - 5/9}. View "A" - a fragment of the formation of the teeth of the second wheel, view "B" - the same for the first wheels. “C” shows an enlarged fragment of the engagement of the first wheel with the second, the two leading points of contact from the tooth legs are above the line (3) and the two leading points of contact from the tooth heads are below the line (3). It should be noted that the location of the touch points in this view is different from that of the “A” view in FIG. 4, where all points of contact are located below line (3) and there are two points of contact per tooth, from the leg and from the head. The difference is that the location of the points of tangency depends on what gear ratio between the wheels: when the gear ratio is less than two and the plot point inside the rolling circles, epitrochoid and hypotrochoid

shortened and leading contact points are located on one tooth, as shown in FIG. 4 and FIG. 8.

In FIG. 6 shows the possibility of creating two more wheels on the basis of one pair of wheels. For each finished external gear wheel, it is possible to create a single internal gear or external gear coupled to it if a pair of internal gear wheels was originally created. The wheels of the invention can only be created in pairs. In this case, for the pair of internal gear wheels in FIG. 5, one external gearing wheel (16) was created, and an internal gearing wheel (17) was created for this wheel (16). It is not necessary to repeat the construction method, since it is the same as for FIG. 4. The dimensions indicated on the drawing allow an analysis of the features of the ratios and obtain

relevant findings. You can pay attention to the fact that the profiles of the legs of the fourth wheel (17) were made on the basis of the section of the shortened hypocycloid, and since the gear ratio is less than two and the drawing point is inside the rolling circle (Yatsk3 = 50 mm, and z = 50.5 mm) then the arrangement of the contact points will be as seen in the description of FIG. 5, i.e. two points of contact on one tooth.

In FIG. 7 shows three options for pairs of gear wheels with

gear ratios equal to two. With this gear ratio and “el” equal to zero, the hypocycloid is a straight line (18). The tooth leg profile (19) of the second internal gear wheel, as an equidistant from a straight line, is two parallel straight lines. Two gears, on the left and in the center of this figure, differ only in the value of “e2”. In the transmission on the right, the drawing point is inside the rolling circle (negative “e2”), the hyprochoid (20) is curved, although without a loop, but the location of the contact points in this case is two for one tooth. And even with a gear ratio of less than two, all trochoids, when the plotting point is located inside the centroid, are shortened, have loops. In FIG. 8 shows a pair of internal gears with a small tooth difference. The initial data for calculating this pair are as follows: AW = 4MM; rl = 40; G2 = 44; Zl = 20; Z2 = 22. To get a shortened hypotrochoid (21) for profiling the tooth leg of the second wheel, we take el = 6, while Yatsk1 = rl - el = 40 - 6 = 34. There is such a feature: to get a shortened hypotrochoid with a gear ratio of less than two, the drawing point should be inside the centroid, if it is outside, we get an elongated hyprochoid. We select Hats1 = 2.7 mm. We calculate k = Aw / rl = 4/40 = 0.1. For the hyprochoid (21) of the tooth legs of the second wheel, the initial parameters will be: {4 +/- 34 - 0.1}. We get the profile (22) of the tooth legs of the second wheel as an equidistant with Hats1 = 2.7 mm. Then we calculate “k” for the epitrochoid (23) of the tooth legs of the first wheel: k = Aw / r2 = 4/44 = 1/11. We select e2 = 6.5 (the selection of “e2” with a gear ratio of less than two does not consist in the profiles of the legs passing tangentially to the heads, because the touch remains at the same gear ratio for different “e2”, but in order to eliminate tooth interference before the entrance of the tooth into the cavity); we get Yaq2 = 2.418263 by measuring (see step 9 for Fig. 2), we calculate Yaq2 = r2 - e2 = 44 - 6.5 = 37.5 mm. For the epitrochoid (23) of the tooth legs of the first wheel, the initial parameters will be: {4 - 37.5 - 1/11}. We get the profile (24) of the tooth legs of the first wheel as an equidistant with Yats1 = 2.418263mm. The enlarged view “A” shows two contact points (25) from the head and legs of one tooth.

In FIG. 9 shows an enlarged view “B” in FIG. 10. This is a fragment of the engagement of the first and second wheels with profiles obtained from the profiles of FIG. 8, by turning the original profiles by half a step and their subsequent mutual trimming. As a result, twice as many teeth and contact points were obtained without changing the shape of the contacting profiles and the reduced radius of the contacting surfaces.

In FIG. 10 shows a complete view of the transmission, a fragment of which is shown in FIG. 9.

In FIG. 11 shows a gear with the same centroids as in FIG. 8, only with an increased number of teeth doubled. Initial data: Aw, rl, r2 and "k" are the same as in the transmission in Fig. 8, only new Zl = 40 and Z2 = 44 are taken. To obtain sufficient gaps between the interdental cavities for placing the heads on the second wheel, it is necessary to reduce the value el = 3 mm (to narrow the loops). The missing new source data are as follows: Yats1 = 1.4mm (set); e2 = 3.65mm (picked up);

Yats2 = 1.418397mm (measured); Yatsk 1 = 40-3 = 37 mm; Yatsk2 = 44-3.65 = 40.35mm. The initial parameters for the equations will be the following - for the hypothyroid of the tooth leg of the second wheel: {4 +/- 37 - 0,1}, - for the epitrochoid of the tooth leg of the first wheel: {4 - 40.35 - 1/11}. On the view "A" shows an enlarged fragment of the gearing of this gear. Amount of points contact is increased compared to the profiles in FIG. 8, but the reduced radius of the contacting surfaces decreased.

In FIG. 12 the top left shows the well-known kinematic diagram of David's planetary gear with internal gearing. The first pair of gears shown in FIG. 8 with Zl = 20 and Z2 = 22, and the profile of the second pair is designed and presented in FIG. 12 to the right, having the number of teeth Z3 = 26 and Z4 = 24. The initial data for this pair is as follows: AW = 4MM; rl = 48; G2 = 52; el = 7; e2 = 7; Yatsk1 = 41; Yatsk2 = 45; for hypotrochoid k = 4/48 = 1/12; for epitrochoid k = 4/52 = 1/13. The initial parameters for the equations will be the following - for the hypothyroid of the tooth leg of the second wheel (Z3): {4 +/- 41 - 1/12}, - for the epitrochoid of the tooth leg of the first wheel (Z4): {4 - 45 - 1/13}. The gear ratio of this mechanism is calculated by the formula:

Z1 * Z3 / (Z1 * Z3 - Z2 * Z4) = 20 * 26 / (20 * 26 - 22 * 24) = -65.

In FIG. 12 the bottom left shows the kinematic diagram of a planetary gearbox with three central wheels. For this gearbox, gear profiles developed and presented in FIG. 13. In this gearbox, one central external gear wheel (Z2 = 31) engages with the satellites (Z1 = 29) in the same way as in the known planetary gearboxes, and the two internal gear wheels (Z3 = 89 and Z4 = 84) have different the number of teeth, their gear rims are located adjacent to each other, and they mesh with the same set of satellites, the width of the gear rims of which is not less than the sum of the gear rims of the internal gear wheels (Z3 = 89 and Z4 = 84). Satellites (Z1 = 29) are mounted on a freely rotating carrier. The first internal gear gear (Z3 = 89) is fixedly mounted, and the second internal gear gear (Z4 = 84), the profile of which (26) is shown in FIG. 13 is connected to the output shaft. This gearbox works similarly to the work of the David mechanism, if we assume in the David mechanism that Z4 = Z1. The gear ratio of this gearbox is calculated by the formula:

(Z3 / Zl + 1) * Z4 / (Z4 - Z3) = (89/29 + 1) * 84 / (84 - 89) = - 68.35862069

In FIG. 13 shows the wheel profiles of the planetary gearbox with Zl = 31, Z2 = 29, Z3 = 89. The profile of the central internal gear wheel (Z3 = 89) consists only of trochoidal interdental cavities, because it is impossible to obtain a working circular head with such a radius of the wheel. The enlarged view “A” (first column) shows two options for engaging the first and second wheels: at the top with e 1 = 3 mm, at the bottom with e1 = 4 mm. On the view "B" (second column), corresponding to these options, the engagement of the second wheel with the Central wheel of the internal gearing is shown. From these images it can be seen that if you smoothly change the value of "el", you can smoothly adjust the geometric dimensions of the teeth. One more feature can be added: according to the second independent claim, the third wheel can be replaced with wheels with a different number of teeth: Z3 = 84 or Z3 = 94, without changing the first central wheel and satellites. Samples of the profiles of these wheels are shown: (26) and (27), respectively.

In FIG. 14 top left shows the kinematic diagram of the planetary

differential gearbox (28) with single-pinion satellites (Z1) and an equal number of teeth on the central wheels of the external (Z2) and internal (Z4) gears. This gearbox can be used, for example, to drive two counter-rotation coaxial propellers. In the center is shown a fragment (29) of the engagement of the satellite profiles (Z1) with the central wheels (Z2) and (Z4). The profiling of the gears in this example is as follows. Initial data for a pair of wheels of external gearing: Zl = 10; Z2 = 80; AW = 126MM; G1 = 14MM; e1 = 2mm; RHK1 = 16MM;

g2 = 112mm; e2 = 3, 1626mm; Yatsk2 = 115.1626mm; Yats1 = 2.3mm; Hats2 = 1, 97693mm;

k2 = Aw / r 1 = 126/14 = 9; kl = Aw / r2 = 126 / l 12 = 1.125. The initial parameters for the equations will be as follows - for the epitrochoid of the tooth leg of the second wheel (Z2): {126 - 16 - 9}, - for the epitrochoid of the tooth leg of the first wheel (Z1): {126 - 115.1626 - 1.125}. To calculate the profile of the central internal gear wheel (Z4), the initial data are as follows: Zl = 10; Z4 = 80; AW = 126MM; NCC1 = 16MM; calculate rl = Aw * Zl / (Z4 - Zl) = 126 * 10 / (80-10) = 18mm; r2 =

k4 = Aw / rl = 126/18 = 7. Initial parameters for the equations of the hypotrochoid of the internal gear wheel (Z4): {126 + / - 16 - 7}. The engagement poles of the profiles (29) show the engagement poles (P1) and (P2).

In FIG. 14, the bottom left shows the kinematic diagram (30) of a planetary gearbox with four central wheels. In this gearbox, the profiles of the central external gear wheel (Z2), satellite (Z1) and internal gear wheel (Z4) used the same as in the planetary differential gear according to the scheme (28). The profiles of the two additional internal gears (Z3 and Z5) are constructed in the same way as the wheel (Z4). The number of teeth in these wheels: Z3 = 88; Z5 = 96. A fragment of the gearing of the wheels (Z1 and Z3) is shown at the top right (31), and a fragment of the gearing of the wheels (Z1 and Z5) is shown at the bottom right (32). The gear ratio of this gearbox (30) is calculated by the formula:

for the wheel (Z5): (Z3 / Z2 + 1) * Z5 / (Z5-Z3) = (88/80 + 1) * 96 / (96-88) = 25.2

for a wheel (Z4): (Z3 / Z2 + 1) * Z4 / (Z4-Z3) = (88/80 + 1) ^ 80 / (80-88) = -21

In FIG. 15 shows wheel profiles of a gear shift mechanism that was designed for a bicycle. The gearing here is one-sided chain-cycloidal (bilaterally possible to make only for one of the wheels). Preset Source data: AW = 60MM; RHK = 80MM; RH = 2MM; Z2 = 40; six wheels with Zl = (13; 12; 11; 10; 9; 8).

The coefficient "k" for each wheel is calculated by the formula: k = Aw / r2 = (Z2-Z1) / Z2. As a result of the calculations, six “k” values were obtained: kl = 0.6; k2 = 0.7; k3 = 0.725; k4 = 0.75; k5 = 0.775; k6 = 0.8. The initial parameters for constructing the epitrochoidal profile of each wheel can be expressed as follows: {60 - 80 - k}. Substituting the equations for each wheel of its “k”, we get an epitrochoid, on the basis of which the tooth profile of this wheel is built. The enlarged view “A” shows the principle of the formation of a tooth profile of an external gear wheel based on the equidistant of a section of a shortened epitrochoid.

Industrial applicability

The above examples of the invention are given to a greater extent to understand the theory of constructing a new gearing, without optimizing the gearing parameters. Below will be given some examples of the practical application of the invention.

In FIG. 16 shows a gear profile obtained from a profile such as in FIG. 8, by doubling the number of teeth and cutting them around the circumferences of the depressions and peaks. On the view "A" shows two lines of engagement, the coefficient of mechanical overlap along the line of shorter length is 1.1.

In FIG. 17 shows a kinematic diagram and gear profiles in a gear assembly with a gear ratio of 2, 18, designed for conversion

automobile engine in aviation.

In FIG. 18 shows the types of construction of the gearbox assembled by

kinematic diagram and with gear profiles in FIG. 17.

In FIG. 19 shows the types of construction of the gearbox assembled by

the kinematic diagram of FIG. 17 with a gear ratio of 12.46. Such a gearbox can be used, for example, in a turboprop aircraft engine.

In FIG. 20 shows the types of construction of the gearbox assembled by

the kinematic diagram of FIG. 12 at the top left, with a gear ratio of 82 and the number of teeth of the first pair Z1 = 40, Z2 = 45, the second pair Z3 = 41, Z4 = 36 (the profile of this second pair is shown in Fig. 16). Such a gearbox can be used, for example, in a drive system for changing the sweep of a wing in airplanes with variable wing geometry.

Claims

Claim

1. Two-sided gear-cycloidal gearing of two wheels, comprising a first wheel having a plurality of gears evenly distributed around a circle, the center of which is located on the axis of rotation of the first wheel, and a second wheel gearing with the first wheel, the teeth of which are made in the form of cavities, having trochoidal profiles, paired with circular profiles of the first wheel fores, characterized in that on the first wheel the gaps between two adjacent forends are made in the form of depressions having a trochoidal profile, which is outlined the equidistant loop of the shortened epitrochoid, the sides of which extend tangentially to the circular profiles of two adjacent sprockets of the first wheel, thus forming trochoidal profiles of the tooth legs of the first wheel, and the parts of the circular profiles of the sprockets of the first wheel remaining after the touch points form circular profiles of the teeth of the first wheel, and on the second wheel, the gaps between the adjacent lateral sides of the said depressions having a trochoidal profile are made in the form of circular heads of the teeth of the second wheel, circular ofil which is an arc of a circle tangent connecting said adjacent sides, and the center of which is located at a distance from the second wheel rotation axis, wherein the profile leg of the first trochoidal tooth wheel, coupled with

profiles of the heads of the teeth of the second wheel, runs tangentially to the circular profiles of the heads of the teeth of the first wheel.

2. A gear with gears, comprising at least three gears, in which at least one first gear has a simultaneous or alternate engagement with at least two other gears, all the first wheels being the same and the center distance of each first gear with each of the remaining gears has the same value, characterized in that the number of teeth in each of the remaining gears can be set different, any selected from a certain tolerance range depending on the applied trochoidal curves, which are used to profile the teeth of the remaining wheels, starting from the maximum allowable

shortened trochoidal curves to the maximum allowable elongated, while the tooth profile of each of the remaining gears containing trochoidal sections, with a different number of teeth, remains paired with the same tooth profile of the first wheels containing circular sections.

3. The mechanism according to p. 2, characterized in that at least one first gear has simultaneous engagement with the other two coaxial gears, one of which is an external gear and the second is an internal gear and the number of teeth in these other wheels can be set equal.

4. The mechanism according to p. 3, made in the form of a differential planetary gearbox, characterized in that at least one first gear is a satellite and has simultaneous engagement with two central gears, one of which is an external gear and the second , the internal gear wheel, and the number of teeth in these central wheels can be set equal.

5. The mechanism according to p. 2, made in the form of a planetary gear, characterized in that at least one first gear, which is a satellite, has simultaneous engagement with three central gears, one of which is an external gear and two others - internal gearing wheels, these internal gearing wheels have a different number of teeth, and the engagement of each internal gearing wheel with the first wheels occurs on its part of the width of the gear rims of the first wheels, while the external gear wheel prisoner is connected to the input shaft, a first internal gear wheel is fixedly secured, and the second internal gear wheel is connected to the output shaft.

6. The mechanism according to p. 2, made in the form of a planetary gear, characterized in that at least one first gear, which is a satellite, has a simultaneous engagement with four central gears, one of which is an external gear and three others - internal gear wheels, these internal gear wheels have a different number of teeth, and the engagement of each internal gear wheel with the first wheels occurs on its part of the width of the gear rims of the first wheels, while the external wheel the clutch is connected to the input shaft, one internal gear wheel having an average number of teeths is fixed motionless, and the other two internal gear wheels having one, more teeth than the fixed wheel and the second, fewer teeth than the fixed fixed wheel connected to two coaxial output shafts.

7. The mechanism according to p. 2, characterized in that one first gear connected to the first shaft has an alternate engagement with each of the remaining gears connected to the second shaft.