RU2073147C1 - Multi-flow two-gearing transmission - Google Patents

Abstract

FIELD: mechanical engineering. SUBSTANCE: transmission has intermediate gears the numbers of teeth of which are multiple. Each gear is mounted on an individual support. The gears are interconnected via a spline spring the number of spline engaging driving and driven central gears. EFFECT: enhanced reliability. 1 dwg

Description

 The invention relates to mechanical engineering, namely to gearboxes that transmit large power for a long time.

 Known designs of gearboxes, in particular aircraft gearboxes, made in the form of multi-threaded gears with the separation of the power flow in stages / 1 /.

 A known design of the gear selected as a prototype / 2 /. In the main gearbox of the RV-EF of the Ka-25K helicopter, a multi-threaded scheme is used in the output stage, in which the number of teeth of the central wheels is not a multiple of the number of flows, and the blocks of intermediate gears have only two bearings.

 The disadvantage is the complexity of manufacturing the gearbox and the relatively low durability.

 The aim of the invention is to increase durability and reduce the complexity of the Assembly.

где β₁ угол наклона зубьев II ступени;
m₁ и m₂ модули шестерен I и II ступеней.The goal is achieved in that a uniform distribution of power between the flows is ensured, and the intermediate gears of the I and II stages with the numbers of teeth Z ₂ and Z ₃ that are multiples of each other, are each mounted on their bearings and are interconnected by a splined spring with the number of splines Z ₃ and are meshing, respectively, with the driving and driven central gears with the number of teeth Z ₂ and Z ₄ that are multiples of the number of threads K, and the gears of the second stage have oblique teeth, the angle of inclination of which is determined by the dependence

where β _{1 the} angle of inclination of the teeth of the II stage;
m ₁ and m ₂ gear modules of I and II steps.

где m₂ и m₃ модули шестерен исходной и заменяемой II ступени;
β₁ и β₂ углы наклона зубьев исходной и заменяемой II ступени;

число зубьев заменяемой II ступени, причем

.An additional feature is the ability to change the frequency of rotation of the output shaft of the transmission by replacing the gears of the second stage in fixed housings, the number and angle of inclination of the teeth of the replaced stage are given by the ratio:

where m ₂ and m ₃ gear modules of the original and replaceable II stage;
β ₁ and β _{2 the} angle of inclination of the teeth of the original and replaceable II stage;

the number of teeth of the replaceable stage II, and

.

 The drawing schematically shows the design of the transmission.

In the housing 1 on bearings 2 and 3 there is a drive shaft 4 with a drive gear 5 mounted on it with the number of teeth Z ₁ . The pinion gear 5 is coupled to several intermediate gears 6 of the first stage, the number of which is indicated by the symbol "K". Each of the gears 6 with the number of teeth Z _{2 is} placed in the housing 1 on bearings 7 and 8 and is connected by a spring 9 with an intermediate gear 10 of the II reduction stage having the number of teeth Z ₃ and the angle of inclination of the teeth β ₁ ..

The number of slots at both ends of the spring 9 is Z ₃ , and the gears 10 are placed in the housing 1 on bearings 11 and 12, one of which 11 - ball fixes the gear 10 in the axial direction.

и углом наклона зубьев β₂ изменять передаточное число передачи. Причем число зубьев ведомой шестерни 13 при смене II ступени сохраняется одинаковым.The intermediate gears of the II reduction stage are coupled to the driven gear 13 of the II reduction stage with the number of teeth Z ₄ and the angle of inclination of the teeth β ₁ .. The driven gear 13 of the II reduction stage is mounted on the driven shaft 14, supported through bearings 15 and 16 on the housing 1. In the design the possibility is provided by replacing gears 10 and 13 with the number of teeth Z ₃ and Z ₄ and the angle of inclination of the teeth β ₁ on gears with the number of teeth

and the angle of inclination of the teeth β ₂ to change the gear ratio of the gear. Moreover, the number of teeth of the driven gear 13 when changing stage II remains the same.

 The transfer works as follows. The power flow supplied from the drive shaft 4 to the drive gear 5 is divided into K flows and transmitted through the intermediate gears 8 of the spring 9 to the intermediate gears 10, from which the power is summed on the driven gear 13, which in turn transfers this power to the driven shaft 14.

ведущей 5 и ведомой 13 шестерен числу потоков К совмещение зубьев всех промежуточных шестерен с зубьями ведущей 13 шестерен возможно в любом их угловом положении. Для одновременности зацепления и последующего равномерного распределения нагрузки между всеми потоками первоначально вводятся в зацепление с ведущей шестерней 5 промежуточные шестерни 6 всех К потоков. Затем устанавливается ведомая шестерня 13 и рессоры 9 всех К потоков, вслед за чем, придвигая вдоль рессор 9 до касания с зубьями шестерни 13, устанавливаются промежуточные шестерни 10, после чего их осевое положение фиксируется регулировочными элементами шарикового подшипника 11. Равенство числа зубьев шлиц рессор 9 числу зубьев шестерни 10 обеспечивается быстрого подбора регулировочных элементов шарикового подшипника 11.Due to the multiplicity of the number of teeth Z ₁ , Z ₄ ,

the leading 5 and the driven 13 gears to the number of threads K the combination of the teeth of all the intermediate gears with the teeth of the leading 13 gears is possible in any of their angular position. For simultaneous engagement and subsequent uniform distribution of the load between all flows, the intermediate gears 6 of all K flows are initially brought into engagement with the drive gear 5. Then the driven gear 13 and the springs 9 of all K flows are installed, after which, moving along the springs 9 until they touch the teeth of the gear 13, the intermediate gears 10 are installed, after which their axial position is fixed by the adjusting elements of the ball bearing 11. The equality of the number of teeth of the springs 9 the number of teeth of the gear 10 provides a quick selection of the adjusting elements of the ball bearing 11.

 The distribution, and evenly, of the load on all gears involved in the power transmission ensures their high durability.

 The multiplicity of the number of teeth between each other and with respect to the number of threads ensures ease of assembly and the ability to produce it without special tools by an unskilled assembler.

 Placing each of the intermediate gears of the block on its bearings ensures high durability of the latter by reducing the load on them.

 It is possible to vary the gear ratio without replacing the housings and a number of basic parts.

Claims (1)

A multi-threaded two-stage gear transmission comprising a housing, drive, driven and intermediate shafts installed therein with driving, driven and intermediate gears meshed with each other, characterized in that the intermediate gears of the first and second stages with multiple teeth are installed in the housing, each on its bearings and interconnected by intermediate shafts, the intermediate shafts are slotted, the number of slots of which is equal to the number of teeth of the intermediate gears of the second stage, the number of bev driving and driven gears are multiples of the number of transmission streams, the second stage intermediate gear and the driven gear are made helical, and the angle β of inclination of the teeth is defined by the following expression:

where Z _{1 the} number of teeth of the pinion gear;
Z ₂ , Z _{3 the} number of teeth of the intermediate gears;
Z _{4 the} number of teeth of the driven gear;
m ₁ , m ₂ gear modules of the first and second stages.