SU1270454A1 - Toothed gearing - Google Patents

Abstract

The invention relates to mechanical engineering and can be used in gears that convert a rotational movement into a rotational movement with the required change in the frequency of rotation and torque. The aim of the invention is to simplify the design, increase the bearing capacity and durability by reducing the contact stresses between the teeth, eliminating additional structural elements and interference of the teeth. The gear 1 engages with the wheel 2 through an intermediate gear element 3, made in the form of a rod, consisting of endless flexible links and associated teeth in the form of plates 4. The crowns of the pinion 1, the wheel 2 and the intermediate element 3 are divided by width, and their the teeth are parallel or inclined to the axis. In the engagement zone, the endless flexible links interact with the fixed guides 7 through the support rollers 6. A circumferential circumference establishes a connection between the thickness of the gear teeth, S wheels and plates in the face section. . 3 h. the item f., 1 tab., 8 ill. (Rsd about 4 cl 4:

Description

The invention relates to the machinebuilding |: iy and can be used in gears that convert rotational motion into rotational motion with the required change in the frequency of the rotation and torque.

The aim of the invention is to simplify the construction, enhance the ability and the ability of the abutment and to the fullness. By reducing the contact pads between the teeth, the lawsuit is a supplementary constructive: -; 1Tm and interference of the teeth.

Ma FIG. 1 shows gear teeth: 1 hour; pas figs. 2 - Pilot with sliding twin crowns and an intermediate link, section A-A in FIG. one; pas figs. 3 — gear with chevron teeth and a prome / cucot link, section A-. L. pas of FIG. one; pas figs. 4 shows a kinematic transmission scheme with an intermediate link equipped with supporting rollers; pas figs. 5 shows plots of the ratio of the transmitted mosquitoes, Nil, described by a transmission with straight teeth and a 45 ° yi-scrap, to the transmission of N power by conventional transmission (without intermediate link) at various values of the gear ratio i and hook angle; in fig. 6 shows the ratios of the magnitude of contact stresses 0 in a conventional gear with straight teeth at various gears of the transmission OTnoiLiennn i and the angle of engagement a to the value of the coptic stresses ai in the described direct transmission with a angle of 45 °; pas figs. 7 is a diagram for determining the thickness of a gear or wheel tooth using a pitch circle; in fig. 8 - - graphs OTHOHJC1P1I of the magnitude of the coptic stresses and in a conventional gear with straight teeth at different values of the gearing i and angle of engagement to the magnitude of the contact1x stresses of cgpc on the surfaces of the wheel teeth in the described gear with the teeth of and an engagement angle of 45 °.

A gear transmission contains rotation 1 installed on parallel axes 1 and Ko / ieco 2 (see Fig. 1) and a test: interconnection with them 3, made in the form of a double-sided rack, the teeth of which are made in the form of plates 4. Plates 4 are in contact with gear teeth 1 with one side, and gear 2 with teeth with the other side. Plates 3 of their extreme face sections are connected with endless flexible links 5.

Gear 1 and wheel 2 can be;) performed with separated and shifted; 5shch1.a.mi. They consist of two parts, one relative to the other in the half step. Odpa part consists of a ring gear of width ei, located in the middle of HjecTepHH 1 or wheel 2 (see

FIG. 2). The other part consists of two gear rims, located along the edges of gear 1 or wheel 2, and width B2 equal to half the width of the gear rim, located in the middle of the gear or wheel.

Intermediate link 3 contains three rows of plates 4. The lengths of the plates of the extreme rows are equal to half the length of the plates of the middle row.

Gear 1 and wheel 2 are made

chevron (see fig. o). Intermediate link 3 contains two rows of plates 4. The plates 4 form, in cross section, perpendicular to the line of the center distance, with a straight line parallel to the axis of rotation of the wheels, an angle equal to the angle of inclination p

5 gear teeth and wheels on dividing cylinders.

Intermediate link 3 (see Fig. 4) with infinite flexible links is located on supporting rollers 6. Sections of infinite flexible links of intermediate link 3 located close to the zone of engagement of the teeth of jaws 1 and Ko; iec 2 with plates 4 are located in stationary guides 7.

In the face m section, the thickness Si of the teeth of the p, single wheel and wheels along pitch circles, the thickness tt of the intermediate link plate, the angle cti of the engagement and the module mt of the engagement are related by the formula

ti

nmt

Si

Cosctt

a thickness ti of the plates is connected to the engagement module ITU by the relation tt (0.2-0.3) mt. The proposed gear transmission allows, other conditions being equal, to transmit more power than conventional involute transmission.

The magnitude of the contact stresses when the teeth are hooked into a conventional gear in the pole

meshing is determined by the Hertz formula

E.,

(1

where R is the magnitude of the reaction in the higher pair; EP-modulus of elasticity;

in-length contact line; }) n - the reduced radius of curvature of the contacting surfaces. The reaction R can be determined by the formula

R 2M., (2)

 d.cosa

where MI is the value of the moment applied

to gear; di diameter of pitch circle

c esterni; and - the angle of the hook.

The magnitude of the reduced radius p of curvature by direct contact of the gear and wheel in the engagement pole is determined from the equation

idisina

(3)

rp:

2 (i + r,

where i is the gear ratio of the transmission. The magnitude of the reduced radius rp of curvature for the case of contact of the teeth of the wheel 1 with the plates 4 (see Fig. 1) of the intermediate link 3 is determined in the same way as for the rack and pinion gear or by the formula (3), taking in it the gear ratio i equal to infinity

d: sina

(four)

After substituting equations (2) and (3) into equation (1), we obtain the formula for determining the contact stresses by direct contact of the gear and wheel teeth

P41 "./4M, EP (1+1) a 0.418V.,;. (5)

Substituting Eqs. (2) and (4) into Eq. (1), we obtain the formula for determining the contact stresses when the pinion contacts the intermediate plate

p l o. Mss

(6)

0-418-Vbclf cosocnsino a

0p

where M1n is the value of the moment applied to the gear in the described transmission;

“11 is the angle of gearing in the described gear.

Accepting that the values of contact stresses in a conventional transmission and described by an are equal to each other, all other conditions being equal. Suvi x, we obtain from equations (5) and (6)

Nn MigCbii (i-t-1) sin2an

(7) N M.i (f - sJrt2oC

where and nr

- values of powers transmitted by a conventional involute transmission and described. Having received in the described transmission, the angle of engagement equal to 45 °, we obtain

Mn Ct + i)

(8) Ni

If in the described conventional gear we take the same angle of engagement, then we have

(9)

FIG. 5 shows the plots of the power ratios Nn and N transmitted by the described gear with straight teeth and

an an engagement angle of 45 ° and a conventional transmission are, respectively. With the same transmitted power and other conditions being equal, the ratio of contact voltages in a conventional transmission to the magnitude of contact voltages in the described transmission with straight teeth and an engagement angle of 45 ° is determined by dividing equation (5) by equation (6) . We have

(ten)

ism2a

With the same angle of engagement 5 in the described and conventional transmissions, equation (10) takes the form

(eleven)

FIG. 6 shows the graphs of the ratios of the quantities a and the SUP for various values of the quantities i and a.

In the transmission with an intermediate link, the thickness St of the gear teeth and the wheel (see Fig. 7) is determined by the pitch circles in the face section.

tt

jimt

(12) 2

from about sat

where mt is the face module of the mesh; CXI -frame engagement angle; tt is the thickness of the plate 4 in the face

section.

With a hooking angle of 45 °, the height

teeth will be shortened. The height factor of the teeth head can be taken as

0.5 (h 0.5), radial coefficient

gap - 0.25 (with 0.25) and thickness ti

plates of 0.25 tonnes. The magnitude of the contact stresses of the optical components on the surface of the wheel teeth in the proposed gear will be less than the magnitude of the contact stresses of the gear, since the magnitude of the radius of curvature of the profiles when the wheel is in contact with the intermediate link plates is profile curvature by direct contact of gear and wheel teeth. From equations (1), (2), (3) and (4) in view of the above, we have

(13)

FIG. 8 built dependency graphs

(13) for different values of i and a.

If in the described and conventional gears

the hooking angle is the same, then we have

(TfI

(14)

1270454 56

The table shows the values of the values (11), (14) for the case when in describing my mine and volume transmissions the angle

-yy - computed by equations (9), the gearing is the same.

1 On Opk

Tz: i: i: i: n ::: zi ::; D :: iT: i: i

Equations (9), (11) and (14) are valid for helical and chevron wheels, if the described one is also compared with the direct contact of teeth that have the same end angles of engagement and the angles of inclination of the teeth.

The gear shown in (Fig. 1), in the end section, has an overlap ratio less than one, therefore the gear and the wheel with hidden teeth after; 1. There is a manufacture with separate rims, as shown in FIG. 2

Such a structure ensures a more relaxed operation of the gear, since equal forces acting on the teeth of the crowns located in the middle of the gear and wheel and on the teeth of the crowns located along the edges of the gear and the wheel will always be located in the same plane passing through the middle of the middle rim is perpendicular to the axis of the rotating gears and wheels.

The transmission works as follows.

When the gear 1 rotates, its tooth presses on the base 4 of the intermediate link 3, which receives movement at a speed V. The plates of the intermediate link 3 in turn relieve the pressure on the tooth. wheels 2, which receives rotational motion.

Claims (4)

1. A gear that contains a pinion, a wheel, and an intermediate gear element meshing with it, which, in order to simplify the design, increases the carrying capacity and durability, the intermediate gear element is made in the form of a lath consisting of infinite flexible links and plates connecting them with each other, which are teeth. 2. Transmission according to Claim 1, characterized in that the gear rims, wheels and plates are separated in width, and their teeth are parallel or inclined to the axes. 3. Transmission according to Claim 1, characterized in that it is provided with supporting rolling bodies and stationary guides located in the engagement zone interacting with infinitely flexible links. 4. Transmission according to claim 1, characterized in that its parameters are interconnected by ratio cosoci where St is the divisional thickness of the gear and wheel teeth in the face section; mt, at is the modulus and angle of engagement in the face section; tt- 0.2 ... 0.3 W - thickness of the plates in the end section. XI- / 1 1.6 X, and 1.2 / 1.0  Phage.6 2 five 7 / X x BUT LL 0,5Timb ui.l V  p 56 tg.d