UA128112U - GEAR TOOTH GEAR WITH LINEAR AND FOUR-STATE TOOTH GEAR WITH "DEEP" PROFILE - Google Patents

Abstract

The gear train consists of four-pinion gears and wheels with circular gears in the circumferential direction of the second, third and fourth crowns and wheels relative to the first gear wheels and wheels with longitudinally modified oblique teeth. Contains linear contact of oblique teeth with a "deep" profile, in which the height of the teeth instead of EMBED Equation.3 increases to the height of EMBED Equation.3, and the angles of rotation of EMBED Equation.3, EMBED Equation.3, EMBED Equation.3 respectively of the second, third and the fourth gear wreaths in the circumferential direction, as well as the rotation angles EMBED Equation.3, EMBED Equation.3, EMBED Equation.3 second, third and fourth wheel rims in the specified direction, respectively equal.

Description

The utility model belongs to the field of mechanical engineering.

A gear transmission is known, consisting of a gear and a wheel with involute teeth located on them, which, in the process of meshing with each other, transmit the payload in the form of torque and rotation frequency (revolutions) from one shaft to another shaft of machines and mechanisms (1) : Kudryavtsev V.N., Derzhavets Yu.A., Glukharev E.G.

Designs and calculation of gears of reducers. - L.: Mashinostroenie, 1971. - 328 p.

The disadvantage of the known gear transmission is a relatively high level of vibration and noise during operation, which in many cases, for example on special purpose vessels, is unacceptable.

The closest in terms of technical essence to the proposed solution is a gear transmission with a point four-pair meshing system of oblique teeth (2). Patent Mo 251228 for a utility model. Ukraine. Gear transmission with a point and four-pair system of engagement of oblique teeth (Text) / O.P. Popov, L. O. Popova - i200913643; statement 28.12.2009; published 12.07.2010. Bul.

Mo 13.

The disadvantage of the specified gear transmission is the difficulty of manufacturing longitudinally modified oblique teeth using high-precision gear grinding machines of German production, such as "Pfauter - 600", which are currently available in two cities of Ukraine, as well as the insufficient use of the reserve of oblique tooth engagement in order to reduce the level of vibration and gear noise.

The task of the useful model is to significantly simplify the production of helical gears and reduce the level of vibration and noise.

To solve the given problem in a gear transmission consisting of a four-crown gear and a wheel with the second, third and fourth crowns of the gear and the wheel turned in the circumferential direction at certain angles relative to the first crowns of the gear and the wheel with longitudinally modified oblique teeth located on them, which differs those containing a linear contact of oblique teeth with a "flat" profile, in which the height of the teeth is instead of n- and n; - t n125t - 225t increases to the height of Pk Nas pu -125t nizt ZT and turning angles

Faish FZgsho Fazsh, respectively, of the second, third and fourth crowns of the gear in the circumferential direction, as well as the angles of rotation T2i, Fa, Fazk of the second, third and fourth crowns of the wheel in the indicated direction, respectively, are equal to each other, i.e. F2ish Z Fzash Z FaZsh | Faik Z Fzak Z FaZko at the same time Fgish Z M Fako,

Fzash Z PF | Fazsh ZMO Fazko, at the same time, the indicated angles of rotation of the gear rims are according to the formula I 2 2

Fsh Fach Physiology - 1802) tp Me 2 sp )sovvki -(2isovots) y gish Zash 43sh d Vp so5o 2 2

Me» 20 sp)sov VK. - (ho sovots) sovotsu yan 05 Ol 6 2 OO Oh (o 722 docs tt sozo so5 Vk de Pp, "g - height of traditional teeth and teeth with a "deep" profile; Ga po Mag -Mksluta . height of the head of traditional teeth and teeth with a "deep" profile; 7 9 Mk -(2B ksputa . height of the stem of traditional teeth and teeth with a "shallow" profile; tya - module in a normal section; Sp-025 . coefficient of growth of the height of teeth with a "deep" profile; M-22 / 2151. transmission ratio; 27, 22 - number of teeth of the gear and wheel; 7 7 Pi21/2c0590 .. radius of the dividing circle of the gear; m V. angle of engagement; Vk. reduced angle of inclination of the teeth; to bi ato /sovv) angle of the output contour in the end plane.

A comparative analysis with the prototype shows that in the proposed gear, instead of longitudinally modified traditional bevel teeth characterized by point contact, unmodified bevel teeth with a "deep" profile and linear engagement are used, while the height of the bevel teeth with a "shallow" profile and the angles of rotation of the second, third and fourth crowns of gears and wheels relative to their first crowns in the circumferential direction are determined according to the above dependencies.

A comparison of the claimed technical solution, not only with the prototype, but also with other technical solutions in this field of technology, did not reveal any features characteristic of the claimed technical solution, which allows us to conclude that the criterion "inventive level" is met.

In Fig. 1 shows a gear with a four-pair engagement of oblique teeth with a "deep" profile; in Fig. 2 shows a schematic representation of the dimensions of gear wheels and lines of engagement of teeth, and in Fig. Figures 4 and 4 show the location of the teeth of the gear crowns and the angles of rotation of the gear in the circumferential direction.

In accordance with Fig. 1-4 we have the following designations: 91, 22 - angular velocities of gears and wheels; bt- the width of the crown of the gear, equal to the width of the crown of the wheel; E is the width of the annular groove;

Boo. the width of the gear, which is equal to the width of the wheel; ! - the depth of the annular groove; 2 - the amount of displacement of the crowns of the gear (wheel) relative to each other in the circumferential direction; B. the angle of inclination of the teeth; Vk - the reduced angle of inclination of the teeth, taking into account their displacement in the circumferential direction; 721sh,

ФЗгш ФАЗш - angles of rotation of the teeth of the second, third and fourth crowns of the gear in the circumferential direction relative to the first crown of the gear; su 20 engagement angle; n, 2 - radii of the dividing circles of the gear and wheel; Groves, vo - radii of the circumferences of the protrusions (vertices) of the teeth of the gear and wheel; 71, 72 - radii of the circles of the depressions of the teeth of the gear and the wheel; 1, 2 - radii of the main circles of the gear and wheel; P, Pe. height of standard teeth and teeth with a "weak" profile; pa, Pag - head height of standard teeth and teeth with a "weak" profile; What? Pe height of the leg of standard teeth and teeth with a "weak" profile; MM - engagement line; MM" - the theoretical length of the engagement line; ar - working length of the engagement line of standard teeth; and. working length of the engagement line of teeth with a "deep" profile; 212 sr-re-er-A-afbi/ya the value of displacement of the crowns of the gear (wheel).

Gear transmission (Fig. 1) consists of a gear, which contains crowns 1, 2, C and 4 with teeth 5 located on them, as well as a wheel with crowns 6, 7, 8 and 9 and teeth 10 located on them.

Gear rings, like wheel rings, the width of each of which is equal to B, are separated from each other by annular grooves 11 with a width of 2 and a depth of !. At the same time, crowns 1, 3, and 4, as well as crowns 6, 8, and 9, are connected to the gear and the wheel, respectively, by tension and pins 12.

To ensure tension, the assembled crowns of gears and wheels are heated to a temperature of 220...260 C, and their installation is carried out with

With gear and wheel. Before collecting crowns, the landing surfaces of gears and wheels are covered with a thin layer of copper.

The generators of the lateral surfaces of the oblique teeth 5 of the gear, as well as the generators of the lateral surfaces of the oblique teeth 10 of the wheel, are rectilinear. At the same time, horizontal lines 13 and 14 coincide with the axes of rotation of the gear and the wheel.

Gearing works as follows.

During rotation of the engine, connected through the intermediate shaft to the gear of the reducer, the latter will begin to rotate with an angular velocity of "1. At the same time, the bevel teeth 5 of the four crowns of the gear act on the bevel teeth 10 of the four crowns of the wheel, which are engaged with them, in due to which the four-crown wheel acquires an angular velocity of 72, at the same time transmitting the useful load in the form of a torque to the actuator. At the same time, the angular velocity of the gear wheel 72 is less than the angular velocity of the gear 21 in. 9772721 times, and the torque on the wheel, on the contrary, is greater in 722771 times the torque on the gear, where U is the gear ratio; 71 and 72 are the number of teeth of the gear and wheel, respectively.

In the absence of a load, the bevel teeth of the gear and the wheels in the process of engagement touch their working surfaces along a line, and when the teeth are loaded, the contact line turns into a straight section of contact with a width of 2bo along the entire length of the tooth b,

In the process of operation of the gear under consideration, the bevel teeth of the gear roll over the bevel teeth of the wheel, moving at the same time along their height. When rolling the working surfaces of the teeth one by one, their peripheral speeds, with the exception of the engagement pole, are not equal to each other. At the same time, the difference between the peripheral velocities increases with the distance of the contact area from the engagement pole (point p, see Fig. 2) to the tops of the teeth and to their bases. From what has been said, it is obvious that the speed of sliding in the engagement pole is zero, and on the heads and legs of the teeth, that is, when the teeth enter and leave the engagement, the indicated speeds reach their maximum values.

In the proposed gear, due to the increase in the length of the working engagement line ab, compared to the engagement line ar of the traditional gear, the end overlap ratio of the teeth increases, which leads, as will be shown below, to an improvement in the vibroacoustic characteristics of this gear due to a decrease in the level of vibration and noise.

To confirm the effectiveness of the proposed gear from the point of view of significantly improving the vibroacoustic characteristics due to the reduction of the vibration and noise level, we will use a single-stage marine helical gear, in which: 71 -36. 225110. tb mm; pit 20. B-142, bu 215 mm; U-03. Poisson's ratio for steel; - 4105. . - 5 и -893-10 N - normal force acting on a coupled pair of teeth; E-217107 MDa - modulus of elasticity of the material for steel materials of gear wheels.

We will turn the specified gear into a gear with four pairs of meshing oblique teeth with a "weak" profile, for which we will take Sp -025, с-5 mm, then the width of each of the crowns will be equal to Bl (bu, -Сс)/4 -(215- 3:5)/4 50 cm,

To reduce the level of vibration and noise in decibels (dB) of the proposed gear transmission, we will use the dependence |Z) Popov A.P. Gear mechanism! with point contact of the teeth.

"Atoll" Publishing House, Mykolaiv: 2010. - 774 sb. li - zdidt in) gu) where n - the number of pinion crowns, equal in this case to 4, i.e. - n-4; Pi is a numerical coefficient.

When determining the coefficient 1, you should use the dependence n - ped ver with (n-1)pfolsh VIPVk. tt) azbi bag 7 dtsovo, ar de i - coefficient of end overlap of oblique teeth with a "flat" profile; 7171 - the length of the line of engagement of oblique teeth with a "weak" profile, equal to ar. - ID with 20 I-sp)sov VK - (dissovets) 2 so57 rk with Me» 21 sp)sov | - (ho sovod). - (24 22 )vipotsi (3) od - agsidy dos / so5V) ! more .

Zo - the angle of the output contour in the end plane; ev Bu vprk/hta angle of axial overlap of oblique teeth.

All of the above dependencies include the reduced angle of inclination of the teeth Vk, which is greater than the initial angle of inclination of the teeth B. i.e. Vk» B. The increase in the angle of inclination of the teeth from the value B to the value 7k is due to the fact that the gear teeth (wheels) of the second, third and fourth crowns are shifted relative to teeth of the first crowns in the circumferential direction.

To determine the angle Vk, we use Fig. 3, based on which we have vk - vs-iso

SOAV where all - AVlor-B, jur. so-25BA

Taking into account the expressions ВС and СО, the last equation will take the form

B, io8--25BA about - I told her;

n - A - ab / 4 Я тя 4 ry to determine the parameter, we will use the dependence (3), taking the angle

BB, With the specified equality of angles, the error in finding parameter A does not exceed 3 95, which is acceptable. with I atsoi - 41545 ' :

Thus, from equation (3) we will find mm, in connection with which the value in Z abi/4-41545/4-1086 in. Using the last expression for 2-10386 MM, we will find the value of the angle Vk. formulas we determine the angle o 20.67, Foish -Fzash Z Fizsh 5517. Foik Z Fzok Z Fazk Z Foish/ 0 18032, M 22/21 110736 - 3055. - - 4015. - я - . . god 203. er BO15 and 13,399. for the calculation, we will take "" 13. Formula (2) was used to determine the pi coefficient.

In accordance with the found value of "-13 according to formula (1) with a coefficient of pP-4, we will get the amount of reduction in the level of vibration and noise in the proposed gear transmission of 274 dB. The given amount of reduction in the level of vibration and noise has no analogues in the world of gearbox construction.

The economic effect of the implementation of the proposed technical solution is that in order to reduce the level of vibration and noise in gearboxes, there is no need to use noise-absorbing devices, which are characterized by great bulkiness and significant material costs.

The social benefit of the claimed technical solution consists in a significant improvement of industrial sanitation due to a reduction in the level of vibration and noise.

Claims (1)

FORMULA OF A USEFUL MODEL Gear transmission consisting of a four-crown gear and a wheel with the second, third and fourth crowns of the gear and the wheel rotated in the circumferential direction by certain angles relative to the first crowns of the gear and the wheel with longitudinally modified bevel teeth located on them, which differs in that containing a linear contact of oblique teeth with a "deep" profile, in which the height of the teeth instead of a khprutzhk veto esot increases to a height of Ge Pab lk Z got zt 25 and the angles of rotation T2ish Fzash Fazsh respectively, the third and fourth crowns are gears in the circumferential direction, as well as the turning angles 21, TZ, TFazk of the second, third and fourth crowns and, accordingly, are equal to each other, that is, faish - fa si Vik Goa peokyai viche Fo sov, Fzash Moz | Fazsh ZMoFazko at w 7 w 7 w 7 ! here are indicated angles of gear crowns Uy They are obtained by the formula 2 U -211-nsp)со5 -и22 со50 4 | 2 ( p) ve ( 2 in (in 22 )doc ov, so so5 Vk ZB de p, J o - the height of traditional teeth and teeth with a "deep" profile; La Ly, Mag -(Coptic . head height of traditional teeth and teeth with a "deep" profile; LZ 2bta Pe -DoByasp)ta . the height of the stem of traditional teeth and teeth with a "flat" profile; and - module in normal section; SP 025. growth rate of teeth with a "deep" profile; M722/ 2151. gear ratio; 21, 22 - the number of gear and wheel teeth; 7 7 Пи21/2с0590 .. the radius of the dividing circle of the gear; (m 580. angle of engagement; Vk - reduced angle of inclination of the teeth; o - agoifydyuvu / sov). the angle of the output contour in the end plane.