RU2614020C1 - Support of shaft rotor of low-pressure compressor of gas turbine engine (versions), body of shaft support and body of ball-bearing rotor shaft support - Google Patents

Abstract

FIELD: mechanical engineering.

SUBSTANCE: low-pressure compressor rotor shaft bearing is located in the intermediate casing of the engine and contains the embodiment of the ball bearing, dividing the support into the stator and rotor parts. The stator portion of the inner side is formed integrally with the outer ring of the ball bearing, and the outer perimeter is secured to the motor housing and the intermediate holder is provided with a labyrinth seal caps. Rotary part includes a pin of the reel disc component of the rotor shaft, which is detachably connected to the cylindrical part of the rotor shaft, through which the rotor part is supported on the inner ring of the ball bearing, and also contains a polyfunctional external coupling element in the form of circular cylindrical nut and the connecting element has a hollow bolt shape. The rotor and stator of the support are in the oil environment, which is usual for them. The support housing is equipped with additional holes for the oil change and removal of oil if necessary.

EFFECT: invention allows to adapt the low-pressure compressor, a part of the engine to be more sensitive to external mode proceeds airflow intensive work in fixed ground operation conditions.

13 cl, 3 dwg

Description

The invention relates to the field of production and operation of gas turbine engines (GTE), in particular to the structures and elements of their low pressure compressor (LPC).

Known support of the shaft of the rotor of the low-pressure compressor of the gas turbine engine, including a bearing located on the shaft connected to the support housing, a lubrication and cooling system for the bearing and sealing elements (A.A. Inozemtsev, M.A. Nikhamkin, V.L. Sandratsky "Gas turbine engines" . Aviadvigatel OJSC, Perm 2007, pp. 196-199, Fig. 4.4.7.1_2).

Known support of the rotor shaft of the low-pressure compressor of a gas turbine engine, including a bearing with a housing, connecting elements, seals and a lubrication and cooling system for the bearing (N.N. Sirotin, A.S. Novikov, A.G. Paykin, A.N. Sirotin. Fundamentals of designing the production and operation of aircraft gas turbine engines and power plants in the CALS technology system. Book 1. Moscow. Science 2011. Pages 762-763, Fig. 15.18, page 763).

The disadvantages of the known solutions are the low adaptation of the low pressure compressor to long-term continuous operation in a stationary external environment and the low maintainability of the support of the rotor shaft of the low pressure rotor due to the non-optimal arrangement of the connections.

The objective of the group of inventions, united by a single creative concept, is to increase the resource of a low-pressure compressor of a gas turbine engine (GTE), increase the wear resistance of the rear support of the rotor shaft of the low pressure valve due to the design solutions described below, improve the performance characteristics of the low pressure valve and, as a result, the entire engine in a stationary ground work and optimization of installation and dismantling processes in the operation of gas turbine engines.

профилем поперечного сечения, большее плечо которого образовано малой конической диафрагмой с углом отклонения образующей указанной диафрагмы от радиальной плоскости, нормальной к оси вала, при этом угол α₁ выполнен не менее чем в два раза меньшим аналогичного угла α₂ отклонения образующей силовой конической диафрагмы корпуса опоры, кроме того в радиальном интервале между указанным кольцевым элементом и внутренним силовым кольцом, которое принято одноплечим в поперечном сечении, контактирующим с торцевым элементом фланца наружного кольца шарикоподшипника, в указанной диафрагме выполнен кольцевой ряд отверстий для циркуляции масла и воздуха между фронтальной и тыльной частями масляной полости, причем количество указанных отверстий принято в виде числа N_од, определенного в диапазоне (17<N_од<31), а меньшее плечо элемента с

профилем выполнено в виде фланца, снабженного выполненными с угловой частотой γ_м отверстиями разъемного соединения с ответными фланцами кольцевых держателей крышек лабиринтных уплотнений, разделяющих полости наддува, суфлирования и масляной, определенной в диапазоне γ_м=(1,91÷3,98) [ед/рад]; роторная часть опоры включает выполненные заодно нижнюю часть конической диафрагмы и заднюю цапфу барабанно-дисковой составляющей вала ротора КНД, разъемно соединенную с цилиндрической составляющей вала на силовых шлицах, выполненных в каждом из указанных элементов, с угловой частотой, определенной в диапазоне γ_ш=(8,28÷8,92) [ед/рад], при этом цилиндрическая составляющая вала ротора КНД соединена на силовых шлицах с рессорой, посредством которой цилиндрическая составляющая вала ротора КНД соединена с валом ТНД с возможностью получения от турбины и пропуска через опору крутящего момента к барабанно-дисковой составляющей вала ротора КНД, кроме этого задняя цапфа и цилиндрическая составляющая вала ротора КНД взаимно разъемно соединены в осевом направлении установленным в полости вала соединительным элементом, выполненным в виде внутреннего полого стяжного болта, при этом на внешней посадочной поверхности фронтальной части цилиндрической составляющей вала ротора установлены разно удаленные от оси вала многогребешковые кольцевые элементы лабиринтных уплотнений и внутреннее кольцо шарикоподшипника, и кроме того на резьбе установлен поджимающий их к упорному кольцевому буртику указанной составляющей вала полифункциональный внешний стяжной элемент в виде круглой гайки, снабженной на свободном конце обращенным к валу кольцевым бортовым элементом с образованием открытого коллектора для сбора и напорной подачи смазочно-охлаждающей жидкости к телам качения шарикоподшипника и посредством каналов под внутренним кольцом шарикоподшипника подачи указанной жидкости к кольцевому элементу лабиринтного уплотнения с выходом в масляную полость.The problem is solved in that the shaft support of the rotor of a low-pressure compressor, including the connected drum-disk and cylindrical components of the rotor shaft of a gas turbine engine, and having a spline and shrink tube, as well as a spring connecting the low pressure turbine shaft and low pressure turbine (LP), according to the invention , made as a rear support for the rotor shaft of the low pressure rotor, located in the intermediate motor housing, contains a thrust ball bearing that separates the support into the stator and rotor parts, the stator part The article includes a support case in the form of a power conical diaphragm, made integral with the ball bearing housing and passing at the ends into internal and external power rings of different diameters, endowed with seats and flanges, including holes for fasteners of detachable joints made at the inner end of the diaphragm through a counter flange the outer ring of a ball bearing with an angular frequency γ _cache spacing holes for fasteners, defined in the range γ _cache = (1.27 ÷ 2.39) [units / rad], and at the outer end of the diaphragm ragma through the counter flange of the intermediate engine casing with an angular frequency γ _vke spacing of fasteners defined in the range γ _vke = (3.98 ÷ 5.73) [units / rad], and the conical diaphragm of the support casing in the area facing the inner power ring, on the front side it is provided with an annular element made integral with the diaphragm symmetrical with respect to the axis of the rotor shaft, for one-piece connection with the front annular element made with

a cross-sectional profile, the larger shoulder of which is formed by a small conical diaphragm with an angle of deviation of the generatrix of the specified diaphragm from the radial plane normal to the axis of the shaft, while the angle α _{1 is} made not less than two times smaller than the same angle α _{2 of the} deviation of the generatrix of the power conical diaphragm of the support body , in addition, in the radial interval between the specified ring element and the inner power ring, which is taken as a single-arm in cross section in contact with the end element of the outer flange to ring of the ball bearing, in the specified diaphragm there is an annular row of holes for the circulation of oil and air between the front and back parts of the oil cavity, the number of these holes being taken as the number N _od defined in the range (17 <N _od <31), and the smaller element arm from

the profile is made in the form of a flange equipped with openings made with an angular frequency γ _{m of} detachable connections with mating flanges of ring holders of labyrinth seal covers separating the cavities of boost, venting and oil, defined in the range of γ _m = (1.91 ÷ 3.98) [units /glad]; the rotor part of the support includes at the same time the lower part of the conical diaphragm and the rear trunnion of the drum-disk component of the rotor KND shaft, detachably connected to the cylindrical component of the shaft on power splines made in each of these elements, with an angular frequency defined in the range γ _w = (8 , 28 ÷ 8.92) [units / rad], while the cylindrical component of the shaft of the KND rotor is connected on the power slots with a spring, by which the cylindrical component of the shaft of the rotor of the KND is connected to the shaft of the KND with the possibility of obtaining turbines and passes through the torque support to the drum-disk component of the KND rotor shaft, in addition, the rear axle and the cylindrical component of the KND rotor shaft are mutually detachable axially mounted by a connecting element made in the shaft cavity, made in the form of an internal hollow coupling bolt, while of the outer landing surface of the frontal part of the cylindrical component of the rotor shaft, multistep ring elements of labyrinth seals and internal the lower ring of the ball bearing, and in addition, a multifunctional external clamping element in the form of a round nut equipped with an annular side element facing the shaft facing the shaft with the formation of an open manifold for collecting and pressure supply of the lubricant-cooling is installed on the thread on the thread fluid to the rolling elements of the ball bearing and through the channels under the inner ring of the ball bearing to supply the specified fluid to the annular element of the labyrinth smudges with access to the oil cavity.

In this case, the inner ring of the ball bearing can be made of two half rings, at the junction of which there are radial channels for supplying cutting fluid to the rolling elements of the ball bearing.

The inner hollow coupling bolt can be made with a front annular cap provided with an external annular collar for power engagement with the counter inner collar of the journal, and at the opposite end, the coupling bolt is provided with an external thread for connecting with the internal thread of the cylindrical shaft component, and into the cavity a tightening bolt a slotted pipe is inserted on the fixing slots, connected on the splines with a tightening pipe with the formation of a pressure channel for supplying air in the boost cavity for other supports.

An annular groove of the oil manifold can be made on the shaft seating surface, communicated on one side with an open manifold for collecting and pressure supply of cutting fluid by means of longitudinal channels made on the shaft, and on the other hand with channels for supplying cutting fluid to the rolling bodies ball bearing, and in addition, through part of the channels, which are prolonged to the adjacent multi-crest ring element of the labyrinth seal with the subsequent release of fluid into the oil floor spine.

профилем поперечного сечения, большее плечо которого выполнено в виде малой конической диафрагмы, с углом α₁ отклонения образующей указанной диафрагмы от радиальной плоскости, нормальной к оси вала, не менее, чем в два раза меньшим аналогичного угла α₂ отклонения образующей силовой конической диафрагмы корпуса опоры, а меньшее плечо выполнено в виде фланца, разъемно соединенного с ответными фланцами числом до трех кольцевых держателей крышек лабиринтного уплотнения, разделяющих полости наддува, суфлирования и масляную, кроме того в радиальном интервале между указанным кольцевым элементом и внутренним силовым кольцом, контактирующим с торцевым элементом фланца наружного кольца шарикоподшипника, в указанной диафрагме выполнен кольцевой ряд отверстий для циркуляции масла и воздуха между фронтальной и тыльной частями масляной полости, причем количество указанных отверстий принято в виде простого числа N_од, определенного в диапазоне (17<N_од<31), роторная часть опоры включает выполненную заодно с задней цапфой нижнюю часть конической диафрагмы барабанно-дисковой составляющей вала ротора КНД, разъемно соединенную с цилиндрической составляющей вала и через последнюю на силовых шлицах соединенную с рессорой, кроме этого задняя цапфа и цилиндрическая составляющая вала ротора КНД взаимно разъемно зафиксированы в осевом направлении с возможностью восприятия и передачи на опору осевых усилий установленным в полости вала соединительным элементом, выполненным в виде внутреннего полого стяжного болта, при этом на посадочной поверхности фронтальной части цилиндрической составляющей вала ротора установлены разно удаленные от оси вала многогребешковые кольцевые элементы лабиринтных уплотнений и внутреннее кольцо шарикоподшипника, а также поджимающий их к упорному кольцевому буртику установленный на резьбе полифункциональный внешний стяжной элемент в виде круглой гайки, снабженной на свободном конце кольцевым бортовым элементом с образованием открытого коллектора для сбора и напорной подачи смазочно-охлаждающей жидкости к телам качения шарикоподшипника и посредством каналов под внутренним кольцом шарикоподшипника подачи жидкости к многогребешковому кольцевому элементу лабиринтного уплотнения с выходом в масляную полость.The task of the second embodiment is solved in that the shaft support of the rotor of a low pressure compressor, including the connected drum-disk and cylindrical components of the rotor shaft of a gas turbine engine, and with spline and coupling pipes, as well as a spring connecting the low pressure valves and low pressure turbines, according to the invention , made as a back support for the rotor shaft of the low-pressure rotor, fixed in the intermediate housing of the engine, contains a thrust ball bearing that separates the support on the stator and rotor parts , the stator part includes a support housing in the form of a power conical diaphragm, made at the same time as the ball bearing housing and passing at the ends into the external and internal power rings and the front ring element extended over the internal power ring, the outer power ring being made one-armed and provided with a flange including holes for fasteners for detachable connection with the flange of the intermediate engine casing, as well as made alternating with the indicated and interconnected holes for passing of oil and air, holes for centering pins and holes for dismantling the bearing housing, the inner power ring is made of two shoulders and endowed with a flange for detachable connection with the mating flange of the outer ring of the ball bearing, while the flange of the power ring includes two groups of holes dispersed around the circumference - for fasteners and holes for the passage of oil and air, and a prolonged frontal annular element is made with

a cross-sectional profile, the larger shoulder of which is made in the form of a small conical diaphragm, with an angle α _{1 of} deviation of the generatrix of the specified diaphragm from the radial plane normal to the axis of the shaft, not less than two times smaller than the same angle α _{2 of the} deviation of the generatrix of the power conical diaphragm of the bearing housing and the smaller shoulder is made in the form of a flange detachably connected to mating flanges with a number of up to three annular holders of labyrinth seal covers separating the pressurization, venting and oil cavities, in addition to rad In the interval between the specified annular element and the inner ring of force in contact with the end element of the flange of the outer ring of the ball bearing, an annular row of holes for circulating oil and air between the front and back parts of the oil cavity is made in the diaphragm, the number of these holes being taken as a prime number N _odes certain range (17 <N _od <31), the rotor part comprises a support integral with the rear lower part tapered pin aperture drum-disk structure the rotor shaft of the KND rotor, detachably connected to the cylindrical component of the shaft and connected through the spring on the power splines, in addition, the rear axle and the cylindrical component of the rotor shaft of the KND are mutually detachable in the axial direction with the possibility of perception and transmission of axial forces to the support mounted in the shaft cavity a connecting element made in the form of an internal hollow coupling bolt, while on the landing surface of the frontal part of the cylindrical component of the rotor shaft are installed multistage ring elements of the labyrinth seals that are differently removed from the axis of the shaft and the inner ring of the ball bearing, as well as the multifunction external clamping element mounted on the thread in the form of a round nut, fitted to the threaded ring collar, provided with a ring side element at the free end to form an open collector for collection and pressure supply of cutting fluid to the rolling elements of the ball bearing and through the channels under the inner ring of the ball bearing leg-comb ring element of the labyrinth seal with access to the oil cavity.

In this case, the holes for the fasteners in the flange of the small conical diaphragm of the support housing can be made with an angular frequency determined in the range of γ _m = (1.91 ÷ 3.98) [units / rad].

Multi-crest rings mounted on the landing surface of the cylindrical component of the rotor shaft of the low pressure rotor coupled with mating seal mating covers can form movable seals of the boost, venting and oil cavities of the rear support, and the third front multi-crest ring element is located on the cylindrical surface of the annular collar in the lower part of the rear conical diaphragm drum-disk component of the shaft and together with the cover of the labyrinth seal movably closes with the front side cavity pressurization, and the ring holder of the first labyrinth seal cover comprises an additional annular element concentric relative to the cap holder in which are made at least two annular grooves disposed therein with sealing rings oil chamber.

The rear trunnion of the drum-disk component of the rotor shaft on the outer and inner cylindrical surfaces and the frontal part of the cylindrical component of the rotor shaft of the KND on the outer surface can be provided with annular flanges for mutual axial fixation of these components of the shaft through the trunnion with a connecting element in the form of a hollow internal coupling bolt, which at the opposite end, it is provided with an external thread for connection with a cylindrical composition provided with a mating internal thread at the same time, a splined pipe is inserted into the cavity of the coupling bolt on the fixing slots, which is connected on the splines with the coupling pipe with the formation of a pressure channel for supplying air to the pressurization cavity of other supports.

The external power ring may be provided with at least two annular grooves with seal rings installed in them.

The holes in the flange of the outer end of the power conical diaphragm of the support body can be made with an angular frequency defined in the range γ _vke = (3.98 ÷ 5.73) [units / rad].

The holes in the flange of the inner end of the power conical diaphragm of the support body can be made with an angular frequency γ _cache defined in the range γ _cache = (1.27 ÷ 2.39) [units / rad].

элементом, причем большее плечо указанного

элемента образовано конической диафрагмой с углом α₁ отклонения образующей диафрагмы от радиальной плоскости, нормальной к оси вала меньшим аналогичного угла α₂ отклонения образующей силовой конической диафрагмы корпуса опоры, а меньшее плечо образовано фланцем, имеющем отверстия под крепежные элементы разъемного соединения с ответными фланцами кольцевых держателей крышек лабиринтных уплотнений полостей наддува воздуха, суфлирования и масляной, при этом в силовой конической диафрагме корпуса опоры выполнен кольцевой ряд отверстий для циркуляции масла и воздуха между частями масляной полости в радиальном интервале между кольцевым элементом диафрагмы и внутренним силовым кольцом, которое выполнено одноплечим с посадочной поверхностью, контактирующей с торцевым элементом фланца наружного кольца шарикоподшипника, причем количество указанных отверстий принято в виде числа N_од, определенного в диапазоне (17<N_од<31), при этом отверстия во фланце внутреннего силового кольца диафрагмы под крепежные элементы с ответным фланцем наружного кольца шарикоподшипника выполнены с угловой частотой, определенной в диапазоне γ_кэш=(1,27÷2,39) [ед/рад], а отверстия во фланце внешнего силового кольца диафрагмы под крепежные элементы с ответным фланцем промежуточного корпуса двигателя выполнены с угловой частотой, определенной в диапазоне γ_вкэ=(3,98÷5,73) [ед/рад].The task in the part of the support housing is solved by the fact that the housing of the rotor shaft support, according to the invention, is included in the stator part of the rear support of the low pressure valve of the gas turbine engine and is made in the form of a power conical diaphragm, which goes into the internal and external power rings of different diameters, endowed with seats and flanges with holes for fasteners, and is equipped on the front side in the area near the internal power ring made in one piece with her ring element, which is inseparably connected to facing the drum claim component of the rotor shaft autonomous annular

element, with a larger shoulder specified

the element is formed by a conical diaphragm with an angle α _{1 of the} deviation of the generatric diaphragm from the radial plane normal to the axis of the shaft smaller than the angle α _{2 of the} deviation of the generatrix of the power conical diaphragm of the support housing, and the smaller shoulder is formed by a flange having holes for fasteners of detachable connection with mating flanges of the ring holders covers of labyrinth seals of cavities of pressurization, venting and oil, while an annular row of holes is made in the power conical diaphragm of the support housing for circulating oil and air between the parts of the oil cavity in the radial interval between the annular element of the diaphragm and the inner power ring, which is made single-armed with a seating surface in contact with the end element of the flange of the outer ring of the ball bearing, the number of these holes being taken as the number N _od defined in range (17 <N _od <31), the holes in the inner flange ring under the force of the diaphragm fastening elements with mating flange of the outer ring of the ball bearing is performed us with angular frequency determined in the range of _cache γ = (1,27 ÷ 2,39) [U / rad], and the holes in the flange of the diaphragm ring outer force for the fixing elements with mating flange intermediate motor housing formed with a corner frequency determined in range γ _vke = (3.98 ÷ 5.73) [units / rad].

элементом, при этом в силовой конической диафрагме корпуса опоры выполнен кольцевой ряд отверстий для циркуляции масла и воздуха между частями масляной полости в радиальном интервале между кольцевым элементом диафрагмы и внутренним силовым кольцом, которое выполнено одноплечим с посадочной поверхностью, контактирующей с торцевым элементом фланца наружного кольца шарикоподшипника, причем количество указанных отверстий принято в виде числа N_од, определенного в диапазоне (17<N_од<31), при этом отверстия во фланце внутреннего силового кольца диафрагмы под крепежные элементы с ответным фланцем наружного кольца шарикоподшипника выполнены с угловой частотой, определенной в диапазоне γ_кэш=(1,27÷2,39) [ед/рад], а отверстия во фланце внешнего силового кольца диафрагмы под крепежные элементы с ответным фланцем промежуточного корпуса двигателя выполнены с угловой частотой, определенной в диапазоне γ_вкэ=(3,98÷5,73) [ед/рад].The task in the part of the ball bearing housing is solved by the fact that the ball bearing housing of the rotor shaft support, according to the invention, is included in the stator part of the rear support of the low pressure valve and is made in the form of a power conical diaphragm, which goes into the inner and outer power rings of different diameters, endowed with landing in places and flanges with holes for fasteners, and is equipped on the front side in the area near the internal power ring made in one piece with her ring element, designed to I have an integral connection with an autonomous annular facing the drum-disk component of the rotor shaft

an element, while in the power conical diaphragm of the bearing housing there is made an annular row of holes for circulating oil and air between the parts of the oil cavity in the radial interval between the annular element of the diaphragm and the inner power ring, which is made single-armed with a seating surface in contact with the end element of the flange of the outer ring of the ball bearing wherein the number of said openings made in the form of N _odes certain range (17 _<od N <31), wherein the openings in the flange internal power count ca aperture for the fixing elements with mating flange of the outer ring of the ball bearing are made with angular frequency determined in the range of _cache γ = (1,27 ÷ 2,39) [U / rad], and the holes in the flange of the outer ring under the force of the diaphragm with reciprocal fixing elements the flange of the intermediate engine casing is made with an angular frequency determined in the range γ _vke = (3.98 ÷ 5.73) [units / rad].

The technical result is achieved by a set of features of each of the described objects and consists in adapting the low-pressure compressor, as part of the engine, more sensitive to the external air flow, intensive work in stationary conditions of ground operation, by optimizing the performance of the low-pressure rotor shaft support and its elements to these specific conditions, as well as to improving the possibilities of installation and dismantling works by semi-automatic or manual iemami, for example, in the field.

The invention is illustrated by drawings, which depict:

in FIG. 1 - the rear bearing of the rotor shaft of the low pressure rotor, a longitudinal section;

in FIG. 2 - housing of the rear support of the rotor shaft of the low pressure rotor, longitudinal section;

in FIG. 3 - ball bearing housing of the rear support of the rotor shaft of the low pressure rotor, a fragment of a longitudinal (along the axis of the shaft) section.

The low-pressure compressor includes the connected drum-disk and cylindrical components 1 and 2 of the rotor shaft 3 and has a spline pipe 4, a coupling pipe 5, and also a spring 6, which connects the low pressure valves and low pressure turbines. The rear bearing of the shaft 3 of the KND rotor is located in the intermediate housing of the engine and contains a ball bearing 7, made thrust, which separates the stator and rotor parts of the support.

The stator part includes a bearing housing in the form of a power conical diaphragm 8, made at the same time with the ball bearing housing 7 and passing at the ends into the internal power ring 9 and the external power ring 10, which have different diameters.

The inner power ring 9 is endowed with a seat 11 and a flange 12 for detachable connection with the mating flange 13 of the outer ring 14 of the ball bearing 7 at the inner end of the diaphragm 8.

For detachable connection of the flange 12 at the inner end of the diaphragm 8 with the counterflange 13 of the outer ring 14 of the ball bearing 7, the holes for the fasteners are made spaced around the perimeter with an angular frequency γ _cache , defined in the range

γ _cache = N _cache / 2π = (1.27 ÷ 2.39) [units / rad],

where N _cache is the number of holes for fasteners connecting flanges 12, 13.

The external power ring 10 is endowed with a seat 15 and a flange 16 for detachable connection with a counter flange of the intermediate housing (not shown) of the engine at the outer end of the diaphragm 8. For detachable connection of the flange 16 at the outer end of the diaphragm 8 with the flange of the intermediate motor of the hole 17 under fasteners are made spaced around the perimeter with an angular frequency γ _vke defined in the range

γ _vke = N _vke / 2π = (3.98 ÷ 5.73) [u / rad],

where N _vke - the number of holes for fasteners connecting these flanges.

If the angular frequency γ _cache <1.27 u / rad or γ _vke <3.98 u / rad, then the strength of the connection will be insufficient, if γ _cache > 2.39 u / rad or γ _vke > 5.73 u / rad , then this will lead to an unjustified increase in material consumption and laboriousness of compounds for providing strength.

профилем поперечного сечения. Большее плечо кольцевого элемента 19 образовано малой конической диафрагмой 20 с углом α₁ наклона образующей к условной радиальной плоскости, нормальной к оси вала ротора, составляющим не менее чем в два раза меньшим аналогичного угла α₂ наклона образующей силовой конической диафрагмы 8 корпуса опоры. Внутреннее силовое кольцо 9 выполнено одноплечим в поперечном сечении и контактирующим с торцевым элементом фланца 13 наружного кольца 14 шарикоподшипника 7. В радиальном интервале между кольцевым элементом 18 и внутренним силовым кольцом 9 в конической диафрагме 8 выполнен кольцевой ряд отверстий 21 для циркуляции масла и воздуха между фронтальной и тыльной частями масляной полости 22. Количество отверстий 21 принято составляющим (17<N_од<31). Число N_од отверстий 21 оптимально для масляного обмена между фронтальной и тыльной частями масляной полости 22 и необходимо для быстрого удаления масла из полости 22 остановленного двигателя. В вариантном исполнении опоры вала ротора КНД число N_од должно быть простым.The conical diaphragm 8 of the support housing in the area facing the inner power ring 9 is provided on the front side with an annular element 18, which is integral with the diaphragm, and is symmetrical about the axis of the rotor shaft. The annular element 18 is made for one-piece connection with the front annular element 19 made with

cross-sectional profile. The larger shoulder of the annular element 19 is formed by a small conical diaphragm 20 with an angle _of inclination α _{1 of the} generatrix to the conditional radial plane normal to the axis of the rotor shaft, which is at least two times smaller than the same angle α _{2 of the} inclination of the generatrix of the power conical diaphragm 8 of the support body. The inner power ring 9 is made single-armed in cross section and in contact with the end element of the flange 13 of the outer ring 14 of the ball bearing 7. In the radial interval between the annular element 18 and the inner power ring 9 in the conical diaphragm 8, an annular row of holes 21 for circulating oil and air between the front and the back of the oil cavity 22. The number of holes 21 is taken as component (17 <N _od <31). The number N _{od of} holes 21 is optimal for oil exchange between the front and back of the oil cavity 22 and is necessary for the rapid removal of oil from the cavity 22 of the stopped engine. In a variant design of the shaft support of the rotor KND, the number N _od should be simple.

The smaller shoulder of the annular element 19 is made in the form of a flange 23 for detachable connection with the mating flanges of the annular holder 24 of the cover of the first labyrinth seal 25 separating the oil cavity 22 and the vent cavity 26, the annular holder 27 of the cover of the second labyrinth seal 28 separating the vent cavity 26 and the cavity 29 pressurization, as well as an annular holder 30 of the cover of the third labyrinth seal 31, movably locking from the outside the cavity 29 of the pressurization.

For detachable connection of the flange 23 of the ring element 19 with the mating flanges of the ring holders 24, 27 and 30 of the labyrinth seal covers, the holes for the fasteners are spaced around the perimeter with an angular frequency γ _m defined in the range

γ _m = N _m / 2π = (1.91 ÷ 3.98) [units / rad],

where N _m - the number of holes for fasteners connecting these flanges. The angular frequency γ _m in the indicated range of values is sufficient and necessary from the point of view of strength and material _consumption , as well as the frequency ranges γ _cache and γ _wke .

The rotor part of the support includes the lower part of the conical diaphragm 32 of the drum-disk component 1, made integral with the rear axle 33 of the rotor shaft of the CPV. The drum-disc component 1 is detachably connected to the cylindrical component 2 of the shaft 3 on the power slots 34 located at an angular frequency

γ _W = N _W / 2π = (8.28 ÷ 8.92), [U / rad],

where N _w - the number of power splines. The angular frequency of the arrangement of the slots γ _w <8.28 u / rad impairs the adhesion of the axle 33 to the cylindrical component 2, and the frequency γ _w > 8.92 u / rad, due to the increase in the frequency, weakens the strength of the slots 34 themselves, when these slots will need to be performed smaller, which also impairs grip. Through the cylindrical component 2 by means of the spring 6, the rotor part is connected to the HPH shaft for receiving from the turbine and transmitting torque through the support to the drum-disk component 1 of the shaft 3 of the KND rotor.

The rear axle 33 and the cylindrical component 2 of the shaft 3 of the KND rotor are mutually detachable in the axial direction with the possibility of perception and transmission of axial forces to the support mounted in the cavity of the shaft by a connecting element made in the form of an internal hollow coupling bolt 35.

On the outer landing surface of the frontal part of the cylindrical component 2 of the rotor shaft 3, a multi-crest ring element 36 of the labyrinth seal 28 separating the boost cavity 29 and the venting cavity 26, a multi-crest annular element 37 of the labyrinth seal 25 separating the venting cavity 26 and the oil cavity 22, as well as the inner ring of the ball bearing 7, which is made of two half rings 38 and 39. At the same time, at the junction of the two half rings 38 and 39 of the inner ring, the ball The bearings 7 are radial passages 40 for supplying coolant to the rolling bodies 41 of the ball bearing 7.

A thread is made on the outer landing surface of the front part of the cylindrical component 2, on which is installed the compressive ring elements 36, 37 and the half rings 38 and 39 of the inner ring of the ball bearing 7 to the thrust ring collar 42 of the component 2, a multifunctional external coupling element 43 in the form of a round nut. The outer coupling member 43 has, on a free edge, an annular side member 44 facing the rotor shaft 3. Using the on-board element 44, an open manifold 45 is formed for collecting and pressure supply of cutting fluid to the rolling bodies 41 of the ball bearing 7, and through the channels 46 under the inner ring of the ball bearing 7, the fluid is supplied to the annular multi-crest element 37 of the labyrinth seal 28 with access to the oil cavity 22.

The inner clamping bolt 35 is made with a front annular tip equipped with an outer annular collar 47 for power engagement with the reciprocal inner collar 48 of the axle 33 and mutual axial fixation of the drum-disk and cylindrical components of the rotor shaft. At the opposite end, the coupling bolt 31 is in turn provided with an external thread for connection with a radial annular protrusion 49 of the cylindrical shaft component 2 provided with a mating thread. A slotted pipe 4 is inserted into the cavity of the coupling bolt 35 on the fixing slots 50 and connected to the coupling pipe 5 on the slots 51 to form a pressure channel 52 for supplying air to the pressurization cavity of other supports.

An annular groove 53 of the oil manifold is made on the landing surface of the shaft, communicated on the one hand with an open manifold 46 for collecting and pressurizing coolant through longitudinal channels 46 made on the shaft, and on the other hand with radial 40 coolant supply channels to the rolling bodies 41 of the ball bearing 7, and by means of a part of the channels 54, which are extended to the adjacent multi-row ring element 37 of the labyrinth seal 25 with the subsequent release of fluid into the oil cavity 22.

The multi-crest rings 37 and 36 mounted on the landing surface of the cylindrical component 2 of the rotor shaft of the low pressure rotor together with the mating covers of the labyrinth seals 25 and 28 form movable seals of the boost, venting and oil cavities of the rear support. The third front multi-scalloped annular element 55 is located on the cylindrical surface of the annular collar 56 in the lower part of the rear conical diaphragm 32 of the drum-disk component 1 of the shaft and together with the labyrinth seal cover movably closes the boost cavity 29 from the front side. The ring holder 24 of the cover of the labyrinth seal 25 is provided with an additional ring element 57 concentric with respect to the holder of the cover, in which at least two annular grooves 58 are made with oil seal rings placed therein. The outer power ring 10 is provided with at least two annular grooves 57 with seal rings installed therein.

кольцевого элемента 19 образовано малой конической диафрагмой 20 с углом α₁ наклона образующей к условной радиальной плоскости, нормальной к оси вала ротора, составляющим не менее чем в два раза меньшим аналогичного угла α₂ наклона образующей силовой конической диафрагмы 8 корпуса опоры. Меньшее плечо кольцевого элемента 19 выполнено в виде фланца 23 для разъемного соединения с ответными фланцами кольцевого держателя 24 крышки первого лабиринтного уплотнения 25, разделяющего масляную полость 22 и полость 26 суфлирования, кольцевого держателя 27 крышки второго лабиринтного уплотнения 28, разделяющего полость 26 суфлирования и полость 29 наддува, а также кольцевого держателя 30 крышки третьего лабиринтного уплотнения 31, подвижно запирающего с внешней стороны полость 29 наддува. В силовой конической диафрагме 8 корпуса опоры в радиальном интервале между кольцевым элементом 18 и внутренним силовым кольцом 9 выполнен кольцевой ряд отверстий 21 для циркуляции масла и воздуха между фронтальной и тыльной частями масляной полости 22. Количество отверстий 21 принято составляющим (17<N_од<31).The housing of the rear support of the rotor shaft of the low pressure valve of the gas turbine engine is included in the stator part of the support and is made in the form of a power conical diaphragm 8, which goes into the internal and external power rings 9 and 10 of different diameters, with a seating surface in contact with the end element of the flange of the outer ring of the ball bearing. Internal power the ring 9 is made single-armed and endowed with a seat 11 and a flange 12 with holes for fasteners for detachable connection with the flange 13 of the outer ring 14 of the ball bearing. The external power ring 10 is endowed with a seat 15 and a flange 16 with holes for fasteners. The conical diaphragm 8 is provided on the front side in the area near the internal power ring 9 with the annular element 18 made in one piece with it. The annular element 18 is inseparably connected with the autonomous annular V-shaped element 19 facing the drum-disk component 1 of the rotor shaft 19. The larger shoulder

the annular element 19 is formed by a small conical diaphragm 20 with an angle _of inclination α _{1 of the} generatrix to the conditional radial plane normal to the axis of the rotor shaft, which is no less than two times smaller than the same angle α _{2 of the} inclination of the generatrix of the power conical diaphragm 8 of the support body. The smaller shoulder of the annular element 19 is made in the form of a flange 23 for detachable connection with the mating flanges of the annular holder 24 of the cover of the first labyrinth seal 25 separating the oil cavity 22 and the vent cavity 26, the annular holder 27 of the cover of the second labyrinth seal 28 separating the vent cavity 26 and the cavity 29 pressurization, as well as an annular holder 30 of the cover of the third labyrinth seal 31, movably locking from the outside the cavity 29 of the pressurization. In the power conical diaphragm 8 of the support body in the radial interval between the annular element 18 and the inner power ring 9, an annular row of holes 21 is made for the circulation of oil and air between the front and rear parts of the oil cavity 22. The number of holes 21 is taken to be (17 <N _od <31 )

The holes in the flange 12 of the inner power ring 9 of the diaphragm 8 for fasteners for detachable connection with the mating flange 13 of the outer ring 14 of the ball bearing 7 are made with an angular frequency defined in the range

γ _cache = N _cache / 2π = (1.27 ÷ 2.39) [units / rad],

where N _cache is the number of holes for fasteners connecting flanges 12, 13.

The holes 17 in the flange 16 of the outer diaphragm power ring 10 for fasteners for detachable connection with the counter flange of the intermediate motor housing are made with an angular frequency defined in the range

γ _vke = N _vke / 2π = (3.98 ÷ 5.73) [u / rad],

_TBEV where N - number of holes for fasteners compound of said flanges.

The ball bearing housing of the rear support of the rotor shaft of the low pressure valve of the gas turbine engine is included in the stator part of the support and is made in the form of a power conical diaphragm 8, which goes into the inner and outer power rings 9 and 10 of different diameters. The inner power ring 9 is made single-armed and endowed with a seat 11 and a flange 12 with holes for fasteners for detachable connection with the flange 13 of the outer ring 14 of the ball bearing. The external power ring 10 is also endowed with a seat 15 and a flange 16 with holes for fasteners. The conical diaphragm 8 is provided on the front side in the area near the internal power ring 9, made in one piece with the annular element 18, designed for one-piece connection with the autonomous annular V-shaped element 19. In the power conical diaphragm 8 of the bearing housing in the radial interval between the annular element 18 and an inner power ring 9, an annular row of holes 21 is made for circulating oil and air between the front and rear parts of the oil cavity 22. The number of holes 21 is taken to be component (17 <N _od <31).

The holes in the flange 12 of the inner power ring 9 of the diaphragm 8 for fasteners for detachable connection with the mating flange 13 of the outer ring 14 of the ball bearing 7 are made with an angular frequency defined in the range

γ _cache = N _cache / 2π = (1.274 ÷ 2.39) [units / rad],

where N _cache is the number of holes for fasteners connecting flanges 12, 13.

The holes 17 in the flange 16 of the outer diaphragm power ring 10 for fasteners for detachable connection with the counter flange of the intermediate motor housing are made with an angular frequency defined in the range

γ _vke = N _vke / 2π = (3.98 ÷ 5.73) [u / rad],

where N _vke - the number of holes for fasteners connecting these flanges.

The shaft support of the KND rotor is mounted as follows.

On the small flange 23 of the support housing, a flange holder 24 of the cover of the labyrinth seal 25 separating the oil cavity 22 and the venting cavity 26 is flanged. Then, on the flange of the mounted holder 24 of the cover of the labyrinth seal, sequentially install the flanges of the holders 27 and 30 of the covers of the other labyrinth seals, after which the entire package of parts is tightened with fixing screws. On the cylindrical component 2 of the low pressure valve shaft, a rubber sealing ring, a multi-crest ring element 36 of the labyrinth seal 25, another rubber sealing ring, a second multi-crest ring element 37 of the labyrinth seal 28 are sequentially installed. Then, the previously assembled support body is lowered onto the shaft 3. After installing the bearing housing, the assembled ball bearing 7 is installed on the shaft, after which the package of parts installed on the shaft is tightened with an external coupling element 43 in the form of a nut. After tightening the nut, the fixing screws of the outer ball bearing ring 14 are installed. Next, a gear (not shown) of the drive of the speed sensor unit is mounted on the shaft and fixed on the shaft with its own nut. Subsequently, on the corresponding flanges of the support housing, a gear block of the drive of the speed sensors is mounted with an oil nozzle mounted on them (not shown), after which a drive spring 6 is installed in the inner cavity of the shaft, which is fixed from falling out of the shaft by a nut.

The shaft support of the rotor KND works as follows.

The stator part of the shaft support 3 of the KND rotor is fixed around the perimeter in the intermediate motor housing and through the ball bearing 7 ensures the stability of the rotor part when the shaft rotates relative to the axis of rotation of the shaft.

From the low-pressure turbine (HPH), the rotational force (torque) is transmitted through the cylindrical component 2 to the drum-disk part of the compressor. The torque from the pump through the spring 6 is transmitted to the cylindrical component 2. The cylindrical component 2 of the shaft and the coupling bolt 35 located inside it, the spline and coupling pipes 4 and 5 practically do not have elements asymmetrically located relative to the axis of rotation of the shaft, which allows them to avoid their own rotation fluctuations.

From the cylindrical component 2 through the slots 34, the torque is transmitted to the drum-disk component 1, which, among other things, interacts with the fixed stator part of the back support of the low pressure valve shaft through a labyrinth seal system 25, 28, 31. Labyrinth seals prevent oil particles from entering the oil cavity 22 into the working with air flow drum-disk part of the CPV.

Under the influence of centrifugal forces, oil from the open reservoir 45 is also supplied with a system of channels 46 made in the seating surface of the cylindrical component 2 of the shaft, and through the radial channels 40 between the half rings 38, 39 of the inner ring of the ball bearing 7, the cutting fluid flows to the rolling bodies 41. In the stator part of the oil cavity 22, holes 21 are made through the flange 12 of the diaphragm 8 and the flange 13 of the outer ring 14 of the ball bearing, allowing oil to communicate on both sides of the ball bearing 7. Thus, the stator and rotor parts of the support interact in a single oil medium, which as a result is subjected to intense mixing.

To optimize the static operation of the stator part of the support housing, the power conical diaphragm 8 is made with the guide deviating from the plane normal to the shaft axis by an angle α ₁ not exceeding 0.16 π rad, and the outer force ring 10 of the diaphragm 8 is equipped with seals.

Thus, the cascade of oil cavity seals, sequentially including three labyrinth seals, provides improved operation of the lubricating-cooling system of the rear support, increasing the efficiency and service life of the support and compressor as a whole.

Claims (13)

1. The shaft support of the rotor of the low-pressure compressor (KND), including the connected drum-disk and cylindrical components of the rotor shaft of a gas turbine engine (GTE) and having spline and coupling pipes, as well as the spring connecting the KND shafts and low pressure turbines (ТНД), characterized the fact that it is made as a back support for the rotor shaft of the low pressure rotor, is located in the intermediate motor housing, contains a thrust ball bearing that divides the support into the stator and rotor parts, the stator part includes an op housing ores in the form of a power conical diaphragm, made at the same time with the ball bearing housing and passing at the ends to the internal and external power rings of different diameters, endowed with seats and flanges, including holes for fasteners of detachable joints made at the inner end of the diaphragm through the counter flange of the outer ring of the ball bearing with an angular frequency γ _cache spacing holes for fasteners defined in the range γ _cache = (1.27 ÷ 2.39) [units / rad], and at the outer end of the diaphragm through the response flange of the intermediate engine casing with an angular frequency γ _vke spacing of fasteners defined in the range γ _vke = (3.98 ÷ 5.73) [units / rad], and the conical diaphragm of the support casing in the zone facing the inner power ring from the front side equipped with a ring element made integral with the diaphragm, symmetrical with respect to the axis of the rotor shaft, for one-piece connection with the front ring element made with

a cross-sectional profile, the larger shoulder of which is formed by a small conical diaphragm with an angle α _{1 of} deviation of the generatrix of the specified diaphragm from the radial plane normal to the axis of the shaft, while the angle α _{1 is} made not less than two times smaller than the same angle α _{2 of the} deviation of the generatrix of the power conical diaphragm the support body, in addition, in the radial interval between the specified annular element and the inner power ring, which is taken as a single-arm in cross section in contact with the end element of the flange outwardly of ball bearing rings in said diaphragm has an annular series of holes for the circulation of oil and air between the front and rear parts of the oil cavity, the number of said openings made in the form of N _odes certain range (17 <N _od <31), and minimal shoulder item with

the profile is made in the form of a flange equipped with openings made with an angular frequency γ _{m of} detachable connections with mating flanges of ring holders of labyrinth seal covers separating the cavities of boost, venting and oil, defined in the range of γ _m = (1.91 ÷ 3.98) [units /glad]; the rotor part of the support includes at the same time the lower part of the conical diaphragm and the rear trunnion of the drum-disk component of the rotor KND shaft, detachably connected to the cylindrical component of the shaft on power splines made in each of these elements, with an angular frequency defined in the range γ _w = (8 , 28 ÷ 8.92) [units / rad], while the cylindrical component of the shaft of the KND rotor is connected on the power slots with a spring, by which the cylindrical component of the shaft of the rotor of the KND is connected to the shaft of the KND with the possibility of obtaining turbines and passes through the torque support to the drum-disk component of the KND rotor shaft, in addition, the rear axle and the cylindrical component of the KND rotor shaft are mutually detachable axially mounted by a connecting element made in the shaft cavity, made in the form of an internal hollow coupling bolt, while of the outer landing surface of the frontal part of the cylindrical component of the rotor shaft, multistep ring elements of labyrinth seals and internal a lower ball bearing ring, and, in addition, a multifunctional external tightening element in the form of a round nut equipped with an annular side element facing the shaft on the free end to form an open manifold for collecting and pressure supply lubricating them to the thrust collar of the specified shaft component is mounted on the thread -cooling fluid to the rolling elements of the ball bearing and through the channels under the inner ring of the ball bearing to supply the specified fluid to the annular element of the labyrinth seal otneniya with access to the oil cavity. 2. The support of the rotor shaft of the low-pressure compressor according to claim 1, characterized in that the inner ring of the ball bearing is made up of two half rings, at the junction of which are made radial channels for supplying cutting fluid to the rolling elements of the ball bearing. 3. The shaft support of the rotor of the low-pressure compressor according to claim 1, characterized in that the inner hollow coupling bolt is made with a front annular tip equipped with an external annular collar for power engagement with the mating inner collar of the journal, and at the opposite end, the coupling bolt is provided with an external thread for connections with the internal element of the cylindrical shaft component provided with a reciprocal thread, while a splined pipe connected to the splines with the coupling pipe is inserted into the cavity of the coupling bolt on the fixing slots the formation of the pressure channel of the air supply in the boost cavity of other supports. 4. The shaft support of the rotor of the low-pressure compressor according to claim 2, characterized in that an annular groove of the oil manifold is made on the shaft seating surface, communicated on one side with an open manifold for collecting and pressure supply of cutting fluid through longitudinal channels made on the shaft and, on the other hand, with channels for supplying cutting fluid to the rolling elements of the ball bearing, and in addition, through part of the channels that are extended to the adjacent multi-row ring annular element of the lab rintnogo seal with further access fluid in the oil chamber. 5. The support of the rotor shaft of the low pressure compressor (KND), including the connected drum-disk and cylindrical components of the rotor shaft of a gas turbine engine (GTE), with spline and shrink pipes, as well as the spring connecting the KND shafts and low pressure turbines (LP), characterized the fact that it is made as a back support for the rotor shaft of the low pressure rotor, is fixed in the intermediate motor housing, contains a thrust ball bearing that separates the support into the stator and rotor parts, the stator part includes a support housing s in the form of a power conical diaphragm, made at the same time with the ball bearing housing and passing at the ends into the external and internal power rings and the front ring element extended over the internal power ring, while the external power ring is made single-armed and provided with a flange including holes for fasteners for detachable connections to the flange of the intermediate engine casing, as well as made alternating with the indicated and between the holes for the passage of oil and air, holes for the center the mounting pins and holes for dismantling the bearing housing, the inner power ring is made of two shoulders and endowed with a flange for detachable connection with the mating flange of the outer ring of the ball bearing, while the flange of the power ring includes two groups of holes dispersed around the circumference - for fasteners and holes for the passage of oil and air and the prolonged frontal annular element is made with

a cross-sectional profile, the larger shoulder of which is made in the form of a small conical diaphragm, with an angle α _{1 of} deviation of the generatrix of the specified diaphragm from the radial plane normal to the axis of the shaft, not less than two times smaller than the same angle α _{2 of the} deviation of the generatrix of the power conical diaphragm of the bearing housing and the smaller shoulder is made in the form of a flange detachably connected to mating flanges with a number of up to three annular holders of labyrinth seal covers separating the pressurization, venting and oil cavities, in addition to rad In the interval between the specified annular element and the inner ring of force in contact with the end element of the flange of the outer ring of the ball bearing, an annular row of holes for circulating oil and air between the front and back parts of the oil cavity is made in the diaphragm, the number of these holes being taken as a prime number N _odes certain range (17 <N _od <31), the rotor part comprises a support integral with the rear lower part tapered pin aperture drum-disk structure the rotor shaft of the KND rotor, detachably connected to the cylindrical component of the shaft and connected through the spring on the power splines, in addition, the rear axle and the cylindrical component of the rotor shaft of the KND are mutually detachable in the axial direction with the possibility of perception and transmission of axial forces to the support mounted in the shaft cavity a connecting element made in the form of an internal hollow coupling bolt, while on the landing surface of the frontal part of the cylindrical component of the rotor shaft are installed multistage ring elements of the labyrinth seals that are differently removed from the axis of the shaft and the inner ring of the ball bearing, as well as the multifunction external clamping element mounted on the thread in the form of a round nut, fitted to the threaded ring collar, provided with a ring side element at the free end to form an open collector for collection and pressure supply of cutting fluid to the rolling elements of the ball bearing and through the channels under the inner ring of the ball bearing leg-comb ring element of the labyrinth seal with access to the oil cavity. 6. The support of the rotor shaft of the low-pressure compressor according to claim 5, characterized in that the holes for the fasteners in the flange of the small conical diaphragm of the support housing are made with an angular frequency determined in the range γ _m = (1.91 ÷ 3.98) [unit /glad]. 7. The support of the rotor shaft of the low-pressure compressor according to claim 5, characterized in that the multi-row rings mounted on the seating surface of the cylindrical component of the rotor shaft of the low pressure rotor coupled with mating seal covers form movable seals of the boost cavities, venting and oil cavity of the rear support, and the third the front multi-scalloped annular element is located on the cylindrical surface of the annular collar in the lower part of the rear conical diaphragm of the drum-disk component of the shaft and the joint but with a lid movably labyrinth seal closes the front side of cavity pressurization, and the ring holder of the first labyrinth seal cover comprises an additional annular element concentric relative to the cap holder in which are made at least two annular grooves disposed therein with sealing rings oil chamber. 8. The support of the rotor shaft of the low-pressure compressor according to claim 5, characterized in that the rear axle of the drum-disk component of the rotor shaft on the outer and inner cylindrical surfaces and the front part of the cylindrical component of the rotor shaft of the low pressure rotor are provided with annular flanges for mutual axial fixing of the components of the shaft through the trunnion with a connecting element in the form of a hollow internal clamping bolt, which in turn is provided with an external thread from the opposite end for connection with nnym mating threaded cylindrical internal element of the shaft part, wherein the cavity of the clamping bolt incorporated in the fixing slots slotted tube, connected with slots for clamping the pipe to form a flow channel for supplying air into the cavity pressurization other supports. 9. The support of the rotor shaft of the low-pressure compressor according to claim 5, characterized in that the external power ring framing the power conical diaphragm of the support housing is provided with at least two annular grooves with seal rings installed therein. 10. The shaft support of the rotor of the low-pressure compressor according to claim 5, characterized in that the holes in the flange of the outer end of the power conical diaphragm of the support body are made with an angular frequency defined in the range γ _wke = (3.98 ÷ 5.73) [unit / glad]. 11. The support of the rotor shaft of the low-pressure compressor according to claim 5, characterized in that the holes in the flange of the inner end of the power conical diaphragm of the support body are made with an angular frequency γ _cache defined in the range γ _cache = (1.27 ÷ 2.39) [ units / glad]. 12. The housing of the support shaft of the rotor KND GTD, characterized in that it is included in the stator part of the rear support of the shaft of the rotor KND GTD and is made in the form of a power conical diaphragm, which goes into the inner and outer power rings of different diameters, endowed with seats and flanges with holes under the fasteners, and is equipped on the front side in the area near the internal power ring made in one piece with her ring element, which is inseparably connected to facing the drum-disk component of the rotor shaft autonomous ring

element, with a larger shoulder specified

the element is formed by a conical diaphragm with an angle α _{1 of the} deviation of the generatric diaphragm from the radial plane normal to the axis of the shaft smaller than the angle α _{2 of the} deviation of the generatrix of the power conical diaphragm of the bearing housing, and the smaller shoulder is formed by a flange having holes for fasteners of detachable connection with mating flanges of the ring holders covers of labyrinth seals of cavities of pressurization, venting and oil, while an annular row of holes is made in the power conical diaphragm of the support housing for circulating oil and air between the parts of the oil cavity in the radial interval between the annular element of the diaphragm and the inner power ring, which is made single-armed with a seating surface in contact with the end element of the flange of the outer ring of the ball bearing, the number of these holes being taken as the number N _od defined in range (17 <N _od <31), the holes in the inner flange ring under the force of the diaphragm fastening elements with mating flange of the outer ring of the ball bearing is performed us with angular frequency determined in the range of _cache γ = (1,27 ÷ 2,39) [U / rad], and the holes in the flange of the diaphragm ring outer force for the fixing elements with mating flange intermediate motor housing formed with a corner frequency determined in range γ _vke = (3.98 ÷ 5.73) [units / rad]. 13. The ball bearing housing of the support of the rotor shaft of the KND GTD, characterized in that it is included in the stator part of the rear support of the rotor shaft of the KND GTD and is made in the form of a power conical diaphragm, which goes into the internal and external power rings of different diameters, endowed with seats and flanges with holes for fasteners, and is equipped on the front side in the area near the internal power ring is made in one piece with her ring element, designed for one-piece connection with facing the drum -disk component of the rotor shaft autonomous annular

an element, while in the power conical diaphragm of the bearing housing there is made an annular row of holes for circulating oil and air between the parts of the oil cavity in the radial interval between the annular element of the diaphragm and the inner power ring, which is made single-armed with a seating surface in contact with the end element of the flange of the outer ring of the ball bearing wherein the number of said openings made in the form of N _odes certain range (17 _<od N <31), wherein the openings in the flange internal power count ca aperture for the fixing elements with mating flange of the outer ring of the ball bearing are made with angular frequency determined in the range of _cache γ = (1,27 ÷ 2,39) [U / rad], and the holes in the flange of the outer ring under the force of the diaphragm with reciprocal fixing elements the flange of the intermediate engine casing is made with an angular frequency determined in the range γ _vke = (3.98 ÷ 5.73) [units / rad].

Images