RU2630928C1 - Operation method for propulsion motor gearbox (pmg) of twin-shaft double-flow turbojet engine (tje); operation method of tje pmg plunger pump and plunger pump implementing this method; operation method of engine tje pmg centrifugal pump and engine centrifugal pump implementing this method; operation method of tje pmg oil pump block and oil pump block, implementing this method - Google Patents

Abstract

FIELD: engine devices and pumps.

SUBSTANCE: group of inventions refers to propulsion motor gearboxes (PMG) of aviation turbojet engines (TJE) and operation methods for propulsion motors. The complex of THE PMG propulsion motors has coaxial shafts of high-pressure rotors (HPR), low-pressure rotor (LPR), central conical drive (CCD), propulsion motor gearbox (PMG) and a remote accessory gearbox (RAG). The working torque during the operation of the engine is taken from the HPR shaft and is successively sent through the main conical gear pair of the CCD, through the spring communicating the CCD with the conical gear pair of the PMG main conical drive (MCD). Through the PMG, installed on the MCD input shaft, a driven bevel gear is fed to the main distribution spur gear, communicated by torque over at least two spur pinions, contacting with it, forming two head gear pairs of multi-stage gearboxes, which divide the share streams of the working torque into two groups according to the number of motors. One of these groups is transferred by a multistage gearbox via a flexible torque shaft to the aircraft accessory of the remote accessory gearbox (RAG). Another group transports share streams of the torque via the PMG propulsion motor multi-stage gearboxes, combined in it.

EFFECT: complex increase of the engine efficiency, increase of the drive gearbox life with lower energy losses and lower wear of the gear ring.

13 cl, 2 dwg

Description

The group of inventions relates to the field of aircraft engine manufacturing, namely, to the boxes of engine assemblies (KDA) of aircraft turbojet engines (TRD) and methods of operation of engine assemblies.

From the existing level of technology, a box of propulsion units of an aircraft turbojet engine is known, including a housing with a set of propulsion units mounted on it and a drive gear system with the ability to transmit operating and starting torques to the units (see, e.g., Inozemtsev A.A. et al., Gas turbine engines, Aviadvigatel OJSC, 2007, pp. 631-644).

The box of propulsion units of an aircraft turbojet engine is known from the existing level of technology (NN Sirotin, AS Novikov, AG Paykin, AN Sirotin. Fundamentals of designing the production and operation of aircraft gas turbine engines and power plants in the CALS system technologies. Book 1. Moscow. Science 2011, SS 805-832).

The disadvantages of the known technical solutions include the lack of development of a system for selecting the set of necessary parameters and torque transmission units for turbojet engines, non-adaptation specifically to technical solutions of a twin-shaft, dual-circuit aircraft turbojet engine, the difficulty of obtaining a compromise combination of increased values of efficiency and engine life with a simultaneous increase in compactness while reducing material and energy intensity of the torque transmission mechanism.

The problem to be solved by a group of inventions related by a single creative idea is to develop a box of engine units and a method of operating the engine units of a twin-shaft twin-turbojet engine complex in an engine operating mode with improved structural and operational characteristics, providing increased efficiency, resource and reliability of the engine KDA, ease of installation and efficiency in the operation and maintenance of the engine.

The set task in terms of the method of operation of the complex of motor units of the box of motor units (KDA) in the operation mode of a twin-shaft double-circuit turbojet engine (TRD) having coaxial shafts of high pressure rotors (RVD), low pressure (RND), central conical drive (TsKP), box engine units (KDA) and the remote box of aircraft units (RCA), is solved by the fact that, according to the invention, the working torque in the process of engine operation is taken from the WFD shaft and sequentially directed through the head a conical gear pair of a central conical drive (CCP), a spring informing the CCP in terms of torque with a conical gear pair of the main conical drive (GPC) of the KDA, and, through the installed on the input shaft of the GPC KDA, the driven conical gear is fed in one piece with the input shaft KDA and having a gear ring with an angular frequency of teeth

γ _c.c.in. = (2.87 ÷ 4.30) [unit / rad]

the main cylindrical gear, communicated by torque not less than two cylindrical gears in contact with it with the formation of two head gear pairs of multi-stage gearboxes, one of which is made with a reduction gear ratio defined in the range

i _shp1vv = (0.62 ÷ 0.88),

and the other is made with a gear ratio defined in the range

i _sp2vv = (1.03 ÷ 1.25);

moreover, these gear pairs are made dividing the share flows of working torque into two groups according to the number of units of the final recipients of the share flows of working torque, while the first of these groups transports the share flows of working torque through the combined multi-stage gearboxes of at least five motor KDA units, and the other transmits shared torque flows with a multi-stage gearbox consisting of no more than two stages of cylindrical gears gears to at least one of the KDA engine units, as well as the two-stage section of the other gearbox located in the KDA, provides the possibility of transmitting through the flexible shaft of the working torque to the aircraft units of the external gearbox (RCA); moreover, from the KDA input shaft, the shared working torques are distributed between the motor units in accordance with the power consumed by them and the rotation speeds of the aggregate shafts relative to the rotation speed of the KDA input shaft.

At the same time, from the input shaft of the KDA, the shared working torques are distributed between the engine units in accordance with the power consumed by them and the speeds of rotation of the shafts of the units, expressed relative to the speed of rotation of the HPH shaft by two groups of gear ratios, the first of which is determined by the ranges of values

n _int.rvd : i _nr : i _ts : i _np : i _dtsn : i _ma = (1) :( 0.39 ÷ 0.55) :( 0.79 ÷ 0.99) :( 0.28 ÷ 0 , 39) :( 0.47 ÷ 0.66) :( 0.47 ÷ 0.66), where

Where

n _{BB RVD} - the relative number of revolutions of the RVD shaft, taken as a unit;

i _nr is the gear ratio of the gearbox of the pump regulator relative to the shaft of the HPP;

i _cs - the same as a centrifugal prompter gearbox;

i _np - the same as a plunger pump gearbox;

i _dtsn - the same gear motor centrifugal pump;

i _ma - the same, gear unit;

the second group combines ratios of gear ratios, which are defined by ranges of values

n _{BB RVD} : i _NF : i _m.v. = (1) :( 1.75 ÷ 2.46) :( 0.61 ÷ 0.85),

Where

n _{BB RVD} - the relative number of revolutions of the RVD shaft, taken as a unit;

i _n.ph. - the gear ratio of the afterburner gearbox relative to the HPH shaft;

i _onwards - the same, the internal section of the gearbox in the KDA, which supplies the shared working torque to the flexible shaft for the VKA units.

The task in terms of the method of operation of the complex of motor units of the box of motor units (KDA) according to claim 1, is solved by the fact that, according to the invention, the box of motor units is made in the form of a prefabricated spatial shell, the KDA motor units included in the complex of motor units are mounted on the bottom of the box body: an engine centrifugal fuel priming pump, a plunger pump, a centrifugal prompter, and also an end bellows-hinged assembly of a flexible shaft is brought to the box from the bottom of the housing; and an oil aggregate, a fuel pump-regulator and an afterburner are mounted on the box lid, and the working torque is transmitted to the motor units through the branched gear system of multi-stage gearboxes installed in the internal volume of the KDA.

The set task in terms of the method of operation of the pump of the plunger box of motor units (KDA) in the operation mode of a twin-shaft double-circuit turbojet engine (TRD) having a high-pressure rotor shaft (HPH), a central conical drive (CCP), a box of motor units, including a pump regulator, a plunger pump, and a remote box of aircraft units (RCA), is solved by the fact that, according to the invention, the plunger pump performs the working function of supplying high pressure fluid to the engine control system using I power running torque produced unit during operation of the engine from the rotating shaft RVD; at the same time, during the operation of the engine, the working torque is taken from the high pressure hoses shaft and sequentially through a spline sleeve coaxial with the shaft, endowed with two rows of external front-end slots with an angular frequency of the splines

γ _b.w. = (12.4 ÷ 20.1) [unit / rad]

and further, through the main bevel gear pair of the central bevel gear (CCP) and the spring informing the CCP in torque with the bevel gear pair of the main bevel gear (GPC) of the KDA, and the driven bevel gear mounted on the input shaft of the GPC KDA, feed the indicated KDA to the input shaft of the KDA to made in one piece with it, having a ring gear with an angular frequency of teeth

γ _c.c.in. = (2.87 ÷ 4.30) [unit / rad]

the main cylindrical gear wheel, from which the working torque is supplied to the plunger pump through a three-stage gear section made of sequentially arranged cylindrical gear pairs with lower gear ratios i _{gear 1vv} , i _{gear 2} and i _{gear 4} as part of a common multi-stage gear pump plunger transmitting a shared working torque to said shaft assembly by RVD, to form the overall gear ratio i _np obtained as the product received from ratio Range mesons gear ratios of said gear stages, counting from the RVD shaft

n _r.vrvd : i _hkp : i _{hpc kda} : i _dl1vv : i _dlp2 : i _dlp4 = (1) :( 1.01 ÷ 1.43) :( 0.71 ÷ 0.99) :( 0.62 ÷ 0.88) :( 0.48 ÷ 0.68) :( 0.58 ÷ 0.83), where

n _{century rvd} - the relative number of revolutions of the shaft of the _{high pressure hitch} , taken as a unit;

i _CCL - gear ratio of the main bevel gear pair of CCL;

i _{gpk kda} - the same, of the main bevel gear pair of _{gas-condensing apparatus of the kda} ;

i _Шп1вв - the same, of the first cylindrical gear pair formed by the leading main distributing spur gear and the first spur gear of the intermediate shaft of the three-stage section of the plunger pump gearbox;

i _sp2 - the same, of the second cylindrical gear pair formed by the second cylindrical gear wheel of the intermediate shaft and the driven gear of the drive shaft of the plunger pump;

i _sp4 - the same, of a third cylindrical gear pair formed by a leading cylindrical gear located on the drive shaft of the regulator pump and a driven gear located on the drive shaft of the plunger pump;

and defined in the range of values relative to the shaft

i _np = (0.28 ÷ 0.39).

At the same time, the plunger pump is installed on the cover of the KDA housing, in communication with the automatic control and regulation system (SAUiR), as well as with the fuel and oil system and in working torque through the multi-stage gearbox of the drive is communicated with the high pressure hitch shaft.

The task in terms of the execution of the pump of the plunger box of the motor units (KDA) of the twin-shaft double-circuit turbojet engine (TRD), is solved by the fact that, according to the invention, it contains a housing with a cover, a spring connected to a shaft endowed with a spring, plungers and an inclined washer that provides the possibility of axial movements of the rod end of the plungers in the cylinder block, concentrically spaced in the pump casing around the unit shaft with an angular frequency

γ _square = (1.20 ÷ 1.72) [units / rad],

with alternating phases of suction and discharge of the working fluid - fuel in each revolution of the shaft; moreover, the pump is made of the axial type with adjustable flow and end distribution of the working fluid with the possibility of implementing the working function of supplying high pressure fluid to the engine control system using the energy of the working torque received by the unit from the WFD shaft during the operation of the engine, performed in this way.

The set task in terms of the method of operation of the engine centrifugal fuel priming pump of the box of motor units (KDA) in the operation mode of a twin-shaft double-circuit turbojet engine (turbojet engine) having a high-pressure rotor shaft (HPH), a central conical drive (CCP), a box of motor units, a pump regulator , the plunger pump and the remote box of aircraft units (RCA), is solved by the fact that, according to the invention, the motor centrifugal fuel-priming pump has a housing with a working body etaniya fuel and performs the function of increasing the working pressure in the fuel system of the engine, using for this operating torque energy received by the unit during operation of the engine from the rotating shaft RVD; in this case, the working torque is taken from the RVD shaft and sequentially through a spline sleeve coaxial with the shaft, endowed with two rows of external front-end splines with the angular frequency of the splines

γ _b.w. = (12.4 ÷ 20.1) [unit / rad]

and then, through the main bevel gear pair of the central bevel drive (CCL), the torque is transmitted to the bevel gear pair of the main bevel drive (GPC) of the KDA, and accordingly, the driven bevel gear mounted on the input shaft of the GPC KDA, then fed to the completed input shaft of the KDA in one piece with it, having a ring gear with an angular frequency of teeth

γ _c.c.in. = (2.87 ÷ 4.30) [unit / rad]

the main cylindrical gear wheel, from which the working torque is supplied to the engine centrifugal fuel priming pump, through no more than a five-stage gear section made of successive cylindrical gear pairs having gear ratios i gear 1, gear ₄ , _{gear 4} , _{gear 5} and _{gear 6} included in the overall gear ratio i _DCN working multistage reducer, transmitting shared operating torque from the shaft RVD priming pump, said overall gear Num i of _DCN obtained as the product received from ratio ranges of gear ratios of all stages of a multistage gear, measured from the shaft RVD

n _r.vrvd : i _gkp : i _{gkp kda} : i _dl1vv : i _dlp2 : i _dlp4 : i _dlp5 : i _dlp6 = (1) :( 1.01 ÷ 1.43) :( 0.71 ÷ 0.99) : (0.62 ÷ 0.88) :( 0.48 ÷ 0.68) :( 0.58 ÷ 0.83) :( 1.23 ÷ 1.75) :( 1.03 ÷ 1.46) where

n _{century rvd} - the relative number of revolutions of the shaft of the _{high pressure hitch} , taken as a unit;

i _CCL - gear ratio of the main bevel gear pair of CCL;

i _{GKP KDA} - the same, the main bevel gear pair GKP KDA;

i _shpvvv - the same, of the first cylindrical gear pair formed by the leading main distributing spur gear and the first spur gear of the intermediate shaft of the five-stage section of the fuel pump gearbox;

i _sp2 - the same, of the second cylindrical gear pair formed by the second cylindrical gear wheel of the intermediate shaft and the driven gear of the drive shaft of the pump regulator;

i _sp4 - the same, of a third cylindrical gear pair formed by a leading cylindrical gear located on the drive shaft of the regulator pump and a driven gear located on the drive shaft of the plunger pump;

i _sp5 - the same, of the fourth cylindrical gear pair formed by the cylindrical gear of the drive shaft of the said plunger pump and the first gear of the intermediate shaft located between the drive shafts of the plunger pump and the fuel priming pump;

i _sp6 - the same, of a fifth cylindrical gear pair formed by a cylindrical gear of said intermediate shaft and a cylindrical gear of a drive shaft of a fuel priming pump;

and defined in the range of values relative to the shaft of the WFD as

i _dtsn = (0.47 ÷ 0.66).

In this case, a centrifugal motor fuel priming pump can be installed on the bottom of the KDA housing, in communication with the automatic control and regulation system (SAUiR), with the fuel and oil systems and in working torque through the multi-stage drive gearbox is communicated with the HPH shaft.

The task in terms of performing a motor centrifugal fuel-pumping pump of the box of motor units (KDA) of a twin-shaft turbofan engine (TRD), is solved by the fact that, according to the invention, it has a housing with a working gear of the gear type or in the form of an impeller and is made with the ability to implement the working function of providing increased fuel pressure in the fuel system of the engine using the energy of the working torque obtained by agr by an engine from the HPH shaft during the operation of the engine, performed in the indicated way.

The set task in terms of the method of operation of the oil aggregate of the box of motor units (KDA) in the operation mode of a twin-shaft double-circuit turbojet engine (TRD) having a high-pressure rotor shaft (RVD), a central conical drive (CCP), a box of engine units and a remote box of aircraft units (RCA) ), it is decided that, according to the invention, the oil unit contains a housing comprising at least two sections, with installed in the first pumping equipment for pumping and filtering the used oil, and a pump equipment in the second section for returning oil to the engine oil system, and performs the working function of pumping out, filtering the used oil and returning the purified oil to the engine oil system using the working torque obtained during the engine’s operation from the rotary shaft of the high pressure hitch; at the same time, during the operation of the engine, the working torque is taken from the high pressure hoses shaft and sequentially through a spline sleeve coaxial with the shaft, endowed with two rows of external front-end slots with an angular frequency of the splines

γ _b.w. = (12.4 ÷ 20.1) [unit / rad]

and further, through the main bevel gear pair of the central bevel gear (CCP) and the spring informing the CCP in torque with the bevel gear pair of the main bevel gear (GPC) of the KDA, and the driven bevel gear mounted on the input shaft of the GPC KDA, feed the indicated KDA to the input shaft of the KDA to made in one piece with it, having a ring gear with an angular frequency of teeth

γ _c.c.in. = (2.87 ÷ 4.30) [unit / rad]

the main cylindrical gear wheel, from which the working torque is supplied to the oil unit through a multi-stage drive gearbox, which includes a multi-stage plunger pump drive gearbox and its own oil unit drive gearbox containing no more than two gear pairs, the first of which transmits torque with an increased gear ratio

i _sp5 = (1.23 ÷ 1.75)

through the engagement of the first gear of the intermediate shaft with the gear gear of the drive shaft of the mentioned multi-stage gearbox of the plunger pump, and through the second cylindrical gear pair, also made with an increasing gear ratio i _shp6 , defined in the range of values

i _sp6 = (1.03 ÷ 1.46),

with a gear located on the combined drive shaft, in common with the drive shaft of the engine centrifugal fuel pump, and the specified working torque is transmitted to the oil unit through a multi-stage drive of the oil unit with a total gear ratio of i _ma , counting from the HPH shaft, formed by a combination of gear ratios of a two-stage gearbox drive of the oil unit from a cylindrical gear on the drive shaft of the plunger pump and multi-stage gearbox of the plunger pump drive, endowed additional transfer function of the working torque oil system blocks identified in the range

i _ma = (0.47 ÷ 0.66).

In this case, the total gear ratio i _{ma of the} aggregate working multi-stage gearbox transmitting the shared working torque from the HPH shaft to the oil unit is determined in the range of values relative to the HPH shaft

i _ma = (0.47 ÷ 0.66) [units / rad]

and is formed by the product of the ratios of the gear ratios of the fourth and fifth stages of cylindrical gear pairs of a two-stage section of the oil unit gearbox and the torque transmitting to it a multi-stage gearbox of the plunger pump, counting from the RVD shaft to the oil unit shaft having gear ratios

n _r.vrvd : i _gkp : i _{gkp kda} : i _dl1vv : i _dlp2 : i _dlp4 : i _dlp5 : i _dlp6 = (1) :( 1.01 ÷ 1.43) :( 0.71 ÷ 0.99) : (0.62 ÷ 0.88) :( 0.48 ÷ 0.68) :( 0.58 ÷ 0.83) :( 1.23 ÷ 1.75) :( 1.03 ÷ 1.46) where

n _{century rvd} - the relative number of revolutions of the shaft of the _{high pressure hitch} , taken as a unit;

i _CCL - gear ratio of the main bevel gear pair of CCL;

i _{GKP KDA} - the same, the main bevel gear pair GKP KDA;

i _Шп1вв - the same, of the first cylindrical gear pair formed by the leading main spur gear of the input shaft of the KDA and the first cylindrical gear of the intermediate shaft of the two-stage section of the gearbox of the pump-regulator drive;

i _sp2 - the same, of the second cylindrical gear pair formed by the second cylindrical gear wheel of the intermediate shaft and the driven gear of the drive shaft of the pump regulator;

i _sp4 - the same, of a third cylindrical gear pair formed by a leading cylindrical gear located on the drive shaft of the regulator pump and a driven gear located on the drive shaft of the plunger pump.

i _sp5 - the same, of the fourth cylindrical gear pair formed by the cylindrical gear of the drive shaft of the said plunger pump and the first gear of the intermediate shaft located between the drive shafts of the plunger pump and the motor centrifugal fuel priming pump, respectively.

i _Шп6 - the same, of the fifth cylindrical gear pair formed by the cylindrical gear wheel of the said intermediate shaft and the cylindrical gear wheel of the drive shaft is a motor centrifugal fuel priming pump.

At the same time, the oil unit is installed on the cover of the KDA housing, it is communicated with the automatic control and regulation system (SAUiR), with the oil system, and also with the working torque through the multi-stage gearbox of the drive, it is communicated with the HPH shaft. The task in terms of the implementation of the oil unit box motor units (KDA) of a twin-shaft turbofan engine (TRD), is solved by the fact that, according to the invention, is configured to implement the working function of pumping, filtering the used oil and returning the cleaned oil to the engine oil system in this way using for this, during the operation of the engine, the energy of the working torque from the shaft of the WFD.

The technical result achieved by the group of inventions related by a single creative idea is to develop a KDA turbofan engine and its components, which ensures, during the operation of the engine, a combined increase in efficiency by 2% and more than double the life of the gearboxes of drives, drive motor units, and the engine in general, due to the geometrical parameters of KDA found in the technical solutions of the group of inventions, the kinematic parameters of the drives due to the developed gear system developed in the inventions in and ensuring balanced ratios of ranges of gear ratios that reduce the unevenness of loads in gear pairs, providing an increase in the service life of parts of multi-stage drives of KDA units due to the uniform loading of gear rims and wheel disks in gear pairs, due to the improved kinematics of gearboxes of drives transferring torque to gears found in the inventions torque with less energy loss and reduced wear of gear rims due to optimization of the angular frequency of the teeth in the wheels axle gear pairs with a decrease in material consumption, the number of assembly units and increased alignment of gear sections blocked in an optimized KDA housing, thereby achieving more than a twofold increase in engine life during its operation.

The invention is illustrated by drawings, where:

in FIG. 1 shows a kinematic diagram of the transmission of torque to KDA units;

in FIG. 2 shows a box of propulsion units, side view.

The turbojet engine is double-shaft, double-circuit. The turbojet engine contains a two-stage low and high pressure compressor divided by a power intermediate casing and gas-dynamically interconnected coaxial shaft of the high pressure rotor - HPH and low pressure rotor shaft - HPH (not shown in the drawings).

Box 1 of motor units (KDA) is made by the national team. A motor centrifugal fuel priming pump 2, a plunger pump 3, a breather 4 centrifugal are mounted on the bottom of the box body 1. From the bottom of the body to the box 1 there is an end bellows-hinge assembly 5 of the flexible shaft 6. An oil unit 7, a fuel pump-regulator 8 and an afterburner pump 9 are mounted on the cover of the KDA 1. In the internal volume of KDA 1, an extensive gear system of gears of multistage gearboxes of units was installed. KDA 1 is made with the possibility of operation of the motor units in the operating engine mode as described below.

The working torque during the operation of the turbojet engine is taken from the HPH shaft and sequentially directed through the main bevel gear pair 10 of the central conical drive (CCP) 11, the spring 12 informing the CCP 11 of the torque with the bevel gear pair 13 of the main conical drive (GPC) KDA 1 , and through the driven bevel gear 15 mounted on the input shaft 14 of the GPC KDA 1 onto a gear made integrally with the input shaft 14 of the KDA 1 and having a ring gear with an angular frequency of teeth

γ _c.c.in. = (2.87 ÷ 4.30) [unit / rad]

the main cylindrical gear distributing gear 16. The main cylindrical gear distributing gear 16 is informed by the torque of not less than two cylindrical gears in contact with it to form two head gear pairs of 18.25 multi-stage gearboxes. One of them, the head gear pair 18 is made with a reduction gear ratio defined in the range

i _shp1vv = (0.62 ÷ 0.88),

and the other gear pair 25 is made with a gear ratio determined in the range

i _sp2vv = (1.03 ÷ 1.25).

These gear pairs are made dividing the shared flows of working torque into two groups according to the number of units - the final recipients of shared flows of working torque. One of these groups of shared flows of torque is transmitted by a multi-stage gearbox of at least one of the KDA 1 engine units, consisting of no more than two stages of spur gears. They are located in KDA 1 with a two-stage section of another gearbox, which transmits torque through the flexible shaft 6 to the aircraft units of the remote box (RCA) (not shown in the drawings). The other of these groups transports the shared flows of torque by means of the multi-stage gearboxes of the KDA 1 motor units integrated in it, at least 2.5 times greater than the corresponding number of shared flows of the first of the indicated groups within KDA 1.

From the input shaft 14 KDA 1, the shared working torques are distributed between the engine units in accordance with the power consumed by them and the speeds of rotation of the shafts of the units, expressed relative to the speed of rotation of the WFD shaft by two groups of gear ratios, the first of which is determined by the ranges of values

n _int.rvd : i _nr : i _ts : i _np : i _dtsn : i _ma = (1) :( 0.39 ÷ 0.55): 0.79 ÷ 0.99) :( 0.28 ÷ 0, 39) :( 0.47 ÷ 0.66) :( 0.47 ÷ 0.66), where

n _{BB RVD} - the relative number of revolutions of the input shaft of the RVD, taken as a unit;

i _nr is the gear ratio of the gearbox of the pump regulator relative to the input shaft of the high pressure hitch;

i _cs - the same as a centrifugal prompter gearbox;

i _np - the same as a plunger gear pump;

i _dtsn - the same as a fuel pump gearbox;

i _ma - the same, gear unit;

the second group combines ratios of gear ratios, which are defined by ranges of values

n _{BB RVD} : i _NF : i _m.v. = (1) :( 1.75 ÷ 2.46) :( 0.61 ÷ 0.85), where

n _{BB RVD} - the relative number of revolutions of the input shaft of the RVD, taken as a unit;

i _nf is the gear ratio of the afterburner gearbox relative to the input shaft of the KDA;

i _gu - the same, the internal section of the gearbox in the KDA, which supplies the shared working torque to the flexible shaft for the VKA units.

KDA 1 is made in the form of a prefabricated spatial shell, on the bottoms of the housing and cover of which are mounted motor units with multi-stage gearboxes of drives installed in a box with the ability to change the number and type of gear stages involved in the gearboxes to receive the units of torque from the starter when starting the engine or from the RVD shaft of the running engine.

The fuel pump regulator 8 KDA 1 consists of a pumping unit with a metering device arranged in a single unit; control unit for metering valve; speed regulator; speed sensor; pick-up machine and pressure limiter; launch machine; regulators of the input guide vane of the low-pressure compressor (VNA KND) and the guide vane of the high-pressure compressor (ON KVD). The fuel pump regulator 8 is configured to implement the working function of regulating the fuel system in the process of engine operation using the energy of the torque obtained from the WFD shaft as follows. The pump regulator 8 in the process of engine operation performs the working function of regulating the fuel system, using for this purpose the energy of the torque obtained from the rotation of the shaft of the WFD. Part of the working torque is taken from the RVD shaft and sequentially transmitted through a spline sleeve coaxial with the shaft (not shown conventionally in the drawings), endowed with two rows of external front-end splines with an angular frequency of the splines in the connection of the sleeve with the shaft of the bevel gear 17 of the central gearbox 11, exceeding the angular frequency of the slots in the connection of the sleeve with the shaft of the WFD is not less than 1.12 times. Further, through the main bevel gear pair 10 of the central control gear 11 and the spring 12, which informs the central control gear 11 of torque with the bevel gear pair 13 of the main rotary gearbox KDA 1, and mounted on the input shaft 14 of the central rotary gearbox KDA 1, the driven bevel gear 15 is fed through the specified input shaft 14 of the KDA 1 made integrally with it, having a ring gear with an angular frequency of teeth

γ _c.c.in. = (2.87 ÷ 44.30) [unit / rad]

the main cylindrical transfer gear 16 of the input shaft 14 GKP KDA 1. From it, the shared working torque is supplied to the pump controller 8 through a two-stage section of the drive gearbox made of two successive cylindrical gear pairs 18, 19 with gear ratios i _{gear 1} and _{gear 2} respectively . The total gear ratio i _{nr of a} multi-stage gearbox transmitting the shared working torque to the regulator pump 8 is obtained as the product of the gear ratios of the gear ratios of the gearbox taken from the ratio of the gearbox, counting from the HPH shaft,

n _r.vrvd : i _fcc : i _{fcc kda} : i _dp1 : i _dp2 = (1) :( 1.01 ÷ 1.43) :( 0.71 ÷ 0.99) :( 0.62 ÷ 0.88 ) :( 0.48 ÷ 0.68),

Where

n _{century rvd} - the relative number of revolutions of the shaft of the _{high pressure hitch} , taken as a unit;

i _tskp - gear ratio of the main bevel gear pair 10 TsKP 11;

i _{GKP KDA} - the same, the main bevel gear pair 13 GKP KDA 1;

i _Шп1 - the same, of the first cylindrical gear pair 18 formed by the leading main gear of the spur gear 16 of the input shaft 14 of the KDA 1 and the first spur gear 20 of the intermediate shaft 21 of the two-stage section of the gearbox of the pump drive regulator 8;

i _Шп2 - the same, of the second cylindrical gear pair 19 formed by the second cylindrical gear wheel 22 of the intermediate shaft 21 and the driven gear 23 of the drive shaft 24 of the pump regulator 8.

This total gear ratio is defined in the range of values.

i _nr = (0.37 ÷ 0.53).

The pump-regulator 8 is installed on the cover of the housing KDA 1, is in communication with the automatic control and regulation system (SAUiR), as well as with the fuel and oil systems and, according to the working torque, is kinematically communicated with the RVD shaft via a multi-stage drive gearbox.

The afterburner pump 9 performs the operational function of supplying fuel to the afterburner circuit of the engine, using the energy of the working torque received by the unit during operation of the engine from the rotating shaft of the high pressure hitch. The working torque during the operation of the engine is taken from the shaft of the high pressure hoses and sequentially through a spline sleeve coaxial with the shaft, endowed with two rows of external front-end slots with an angular frequency of the splines

γ _b.w. = (12.4 ÷ 20.1) [units / rad].

Then, through the main bevel gear pair ЦКП 11 and spring 12, which informs ЦКП 11 in torque with a bevel gear pair 13 ГКП КДА 1 and installed on the input shaft 14 ГКП КДА 1, the driven bevel gear 15 is fed through the specified input shaft 14 КДА 1 for integrally with it, the main cylindrical gear wheel 16. The main cylindrical gear 16 has a ring gear with an angular frequency of teeth

γ _c.c.in. = (2.87 ÷ 4.30) [unit / rad].

From it, working torque is supplied to the afterburner pump 9 through a two-stage gear section made of successive cylindrical gear pairs 25, 26 having gear ratios i _bf1 and i _bf2, respectively. The total gear ratio i _{nf of the} working multi-stage gearbox, transmitting the shared working torque to the afterburner pump 9 from the high pressure hitch shaft, which is obtained as the product of the ratio of the gear ratios of the stages of the multi-stage gear, counting from the high pressure hitch shaft

n _r.vrvd : i _gkp : i _{gkp kda} : i _bf1 : i _bf2 = (1) :( 1.01 ÷ 1.43) :( 0.71 ÷ 0.99) :( 1.03 ÷ 1.25 ) :( 1.49 ÷ 2.14), where

n _{century rvd} - the relative number of revolutions of the shaft of the _{high pressure hitch} , taken as a unit;

i _tskp - gear ratio of the main bevel gear pair 10 TsKP 11;

i _{GKP KDA} - the same, the main bevel gear pair 13 GKP KDA 1;

i _шф1 - the same, of the first cylindrical gear pair 25 formed by the leading main distributing spur gear 16 and the first spur gear 27 of the intermediate shaft 28 of the two-stage section of the gearbox pump 9 afterburner;

i _bf2 - the same, of the second cylindrical gear pair 26 formed by the second cylindrical gear wheel 29 of the intermediate shaft 28 and the driven gear 30 of the drive shaft 31 of the afterburner pump 9.

The total gear ratio is determined in the range of values relative to the high pressure shaft

i _n.ph. = (1.73 ÷ 2.44).

The afterburner pump 9 is installed on the lid of the KDA 1 housing, in communication with the automatic control and regulation system (SAUiR), as well as with the fuel and oil system and in working torque via the multi-stage gearbox of the drive is in communication with the HPH shaft.

The prompter 4 centrifugal KDA 1 is configured to implement the working function of separating oil from air from an air-oil emulsion discharged from the oil cavities of the rotor bearings using the energy of the working torque received by the unit during operation of the engine using the energy of the torque received from the WFD shaft as follows way. The working torque in the process of engine operation is taken from the shaft of the high pressure hoses and sequentially through a spline sleeve coaxial with the shaft, endowed with two rows of external frontal slots with the angular frequency of the slots of the first of these rows, namely, the sleeve that is included in the spline connection of the sleeve with the high pressure hoses, defined in the

γ _b.w. = (12.4 ÷ 20.1) [units / rad].

Further, through the main bevel gear pair 10 of the central control gear 11 and the spring 12, which informs the central control gear 11 of torque with the bevel gear pair 13 of the main rotary gearbox KDA 1, and mounted on the input shaft 14 of the central rotary gearbox KDA 1, the driven bevel gear 15 is fed through the specified input shaft 14 of the KDA 1 to the main distributing cylindrical gear 16 made together with it. The main distributing cylindrical gear 16 has a ring gear with an angular frequency of teeth

γ _c.c.in. = (1.87 ÷ 4.30) [unit / rad].

From it, working torque is supplied to a breather 4 centrifugal mounted on the bottom of the KDA 1 housing through a three-stage section of the drive gearbox made of three consecutive cylindrical gear pairs 18, 19, 32, with gear ratios i _{gear 1} , _{gear 2} and _{gear 3,} respectively. The total gear ratio i _{cs of} all stages of the working multi-stage gearbox of the breather 4 centrifugal relative to the shaft

i _cs = (0.77 ÷ 0.99).

It is obtained on the basis of a combination of gear ratios of gear stages adopted from the relations of ranges of values

n _r.vrvd : i _hkp : i _{hkp qda} : i _dl1 : i _dlp2 : i _dl3 = (1) :( 1.01 ÷ 1.43) :( 0.71 ÷ 0.99) :( 0.62 ÷ 0.88) :( 0.48 ÷ 0.68) :( 1.75 ÷ 2.12),

Where

n _{century rvd} - the relative number of revolutions of the shaft of the _{high pressure hitch} , taken as a unit;

i _tskp - gear ratio of the main bevel gear pair 10 TsKP 11;

i _{GKP KDA} - the same, the main bevel gear pair 13 GKP KDA 1;

i _sp1 - the same, of the first cylindrical gear pair 18 formed by the leading main gear spur gear 16 of the input shaft 14 of the KDA 1 and the first spur gear 20 of the intermediate shaft 21 of the three-stage section of the gearbox of the actuator 4 of the centrifugal prompter;

i _Шп2 - the same, of the second cylindrical gear pair 19 formed by the second cylindrical gear wheel 22 of the first intermediate shaft 21 and the driven gear 23 of the drive shaft 24 of the pump regulator 8

i _sp3 - the same, of the third cylindrical gear pair 32 formed by the gear 23 of the drive shaft 24 of the pump-regulator 8 and the driven spur gear 33 of the drive shaft 34 of a three-stage section of the gearbox of the drive of the actuator of the centrifugal prompter 4.

A prompter 4 centrifugal mounted on the cover of the housing KDA, communicated with the automatic control and regulation system (SAUiR), as well as with the oil system and the working torque kinematically communicated with the shaft of the high pressure hitch via a multi-stage drive gearbox.

The plunger pump 3 contains a housing with a cover, a spring connected to a shaft endowed with a spring, plungers and an inclined washer that allows axial movements of the rod part of the plungers in the cylinder block, concentrically spaced in the pump casing around the pump shaft with an angular frequency

γ _square = (1.20 ÷ 1.72) [units / rad],

with alternating phases of suction and discharge of the working fluid - fuel in each revolution of the shaft. The plunger pump 3 is made of an axial type with an adjustable supply and end distribution of the working fluid with the possibility of realizing the working function of supplying high pressure fluid to the engine control system using the energy of the working torque received by the unit from the HPH shaft during the operation of the engine, performed as follows.

The working torque is taken from the RVD shaft and sequentially through a spline sleeve coaxial with the shaft, endowed with two rows of external front-end splines with an angular frequency of splines

γ _b.w. = (12.4 ÷ 20.1) [units / rad].

Further, through the main bevel gear pair 10 of the central control gear 11 and the spring 12, which informs the central control gear 11 of torque with the bevel gear pair 13 of the main rotary gearbox KDA 1, and mounted on the input shaft 14 of the central rotary gearbox KDA 1, the driven bevel gear 15 is fed through the specified input shaft 14 of the KDA 1 to made in one piece with him, the main spur gear 16. It has a ring gear with an angular frequency of teeth

γ _c.c.in. = (2.87 ÷ 4.30) [unit / rad].

From the main distributing cylindrical gear wheel 16, working torque is supplied to the plunger pump 3 through a three-stage gear section made of sequentially arranged cylindrical gear pairs 18, 19, 35 with lower gear ratios i _{gears 1} , _{gear 2} and _{gear 4} as part of a common multi-stage pump gearbox 3 plunger, transmitting the shared working torque to the specified unit from the shaft of the HPH, with the formation of the total gear ratio i. _Np , obtained as the product of the ranges of gear ratios of steps of the specified gearbox, counting from the high pressure hitch shaft

n _r.vrvd : i _hkp : i _{gkp kda} : i _dl1vv : i _dlp2 : i _dlp4 = (1) :( 1.01 ÷ 1.43) :( 0.71 ÷ 0.99) :( 0.62 ÷ 0.88) :( 0.48 ÷ 0.68) :( 0.58 ÷ 0.83), where

n _{century rvd} - the relative number of revolutions of the shaft of the _{high pressure hitch} , taken as a unit;

i _tskp - gear ratio of the main bevel gear pair 10 TsKP 11;

i _{GKP KDA} - the same, the main bevel gear pair 13 GKP KDA 1;

i _shpvvv - the same, of the first cylindrical gear pair 18 formed by the leading main distributing spur gear 16 and the first spur gear 20 of the intermediate shaft 21 of the three-stage section of the gearbox of the pump 3 of the plunger;

i _Шп2 - the same, of the second cylindrical gear pair 19 formed by the second cylindrical gear wheel 22 of the intermediate shaft 21 and the driven gear 23 of the drive shaft 24 of the pump regulator 8;

i _sp4 - the same, of a third cylindrical gear pair 35 formed by a spur gear 36 located on the drive shaft 24 of the regulator pump 8 and the driven gear 37 located on the drive shaft 38 of the plunger pump 3.

The total gear ratio is determined in the range of values relative to the high pressure shaft

i _np = (0.28 ÷ 0.39).

The plunger pump 3 is installed on the cover of the KDA 1 housing, in communication with the automatic control and regulation system (SAUiR), as well as with the fuel and oil system and in working torque via the multistage drive gearbox is in communication with the HPH shaft.

A motor centrifugal fuel priming pump (DCS) 2 KDA 1 of a twin-shaft double-circuit turbojet engine (TRD) has a housing with a working gear type or in the form of an impeller installed in it. It is made with the possibility of implementing the working function of providing increased fuel pressure in the fuel system of the engine using the energy of the working torque received by the unit from the WFD shaft during engine operation, performed in the following way.

The working torque is taken from the RVD shaft and sequentially, through the main bevel gear pair 10 of the central control gear 11, the torque is transmitted to the bevel gear pair 13 of the GPC KDA 1 through the main conical gear pair 10 of the central control gearbox.

The specified spline sleeve is endowed with two rows of external frontal splines with the angular frequency of the splines

γ _b.w. = (12.4 ÷ 20.1) [units / rad].

Next, the torque is transmitted to the driven bevel gear 15 mounted on the input shaft 14 of the GPC KDA 1. Then, the indicated gear shaft 16 is fed through the specified input shaft 14 to the main gear sprocket gear 16. The main gear sprocket 16 has a gear ring with tooth angular frequency

γ _c.c.in. = (2.87 ÷ 4.30) [unit / rad].

From it, working torque is supplied to the engine centrifugal fuel-priming pump 2 through no more than a five-stage gear section made of successive cylindrical gear pairs 18, 19, 35, 39, 40 having gear ratios i _{gear 1} , gear ₂ , _{gear 4} and _{gear 6} , included in the overall gear ratio i _DCN working multistage reducer, transmitting shared operating torque from the shaft 2. Said RVD DAYS overall gear ratio i _DCN obtained as the product received from gear ratio ranges Num l all stages of a multistage gearbox, apart from the shaft of the WFD,

n _r.vrvd : i _gkp : i _{gkp kda} : i _dl1vv : i _dlp2 : i _dlp4 : i _dlp5 : i _dlp6 = (1) :( 1.01 ÷ 1.43) :( 0.71 ÷ 0.99) : (0.62 ÷ 0.88) :( 0.48 ÷ 0.68) :( 0.58 ÷ 0.83) :( 1.23 ÷ 1.75) :( 1.03 ÷ 1.46) where

n _{century rvd} - the relative number of revolutions of the shaft of the _{high pressure hitch} , taken as a unit;

i _CCL - gear ratio of the main bevel gear pair of CCL;

i _{GKP KDA} - the same, the main bevel gear pair GKP KDA;

i _shpvvv - the same, of the first cylindrical gear pair formed by the leading main distributing spur gear and the first spur gear of the intermediate shaft of the five-stage section of the fuel pump gearbox;

i _sp2 - the same, of the second cylindrical gear pair formed by the second cylindrical gear wheel of the intermediate shaft and the driven gear of the drive shaft of the pump regulator;

i _sp4 - the same, of a third cylindrical gear pair 35 formed by a spur gear 36 located on the drive shaft 24 of the regulator pump 8 and the driven gear 37 located on the drive shaft 38 of the plunger pump 3.

i _sp5 - the same, of the fourth cylindrical gear pair 39 formed by the cylindrical gear 37 of the drive shaft 38 of the said plunger pump 3 and the first gear 41 of the intermediate shaft 42 located between the drive shafts 38, 43 of the pump 3 of the plunger and ДЦН 2, respectively.

i _sp6 - the same, of the fifth cylindrical gear pair 40 formed by the spur gear 44 of the said intermediate shaft 42 and the spur gear 45 of the drive shaft 43 of the center plate 2.

The total gear ratio is determined in the range of values relative to the shaft of the WFD as

i _dtsn = (0.47 ÷ 0.66).

An engine centrifugal fuel priming pump 2 is installed on the bottom of the KDA 1 housing, in communication with an automatic control and regulation system (SAUiR), with fuel and oil systems, and with a working torque via a multi-stage gearbox of the drive is communicated with the RVD shaft.

Oil unit 7 KDA 1 of a twin-shaft turbofan engine (turbofan engine) contains a housing comprising at least two sections, with installed in the first pumping equipment for pumping and filtering the used oil, and pumping equipment in the second section for returning oil to the engine oil system. It performs the working function of pumping out, filtering the used oil and returning the refined oil to the engine oil system using the working torque obtained during the engine’s operation by the unit from the rotating WFD shaft for this energy. In the process of engine operation, the working torque is taken from the RVD shaft and sequentially through a spline sleeve coaxial with the shaft, the main bevel gear pair 10 of the central control gear 11 and the spring 12, which informs the central control gear 11 of the torque with the bevel gear pair 13 of the central control gear KDA 1, and installed on the input the shaft 14 GKP KDA 1 driven bevel gear 15 and serves on the specified input shaft 14 KDA 1 made in one piece with him, the main distributing spur gear 16.

The splined sleeve is endowed with two rows of external frontal splines with an angular frequency of splines

γ _b.w. = (12.4 ÷ 20.1) [units / rad].

The main spur gear 16 has a gear ring with an angular frequency of teeth

γ _c.c.in. = (2.87 ÷ 4.30) [unit / rad].

From the main distributing spur gear 16, operating torque is supplied to the oil unit 7 through a multi-stage drive gearbox, which includes a multi-stage gear drive for the pump 3 of the plunger pump and its own gearbox for the drive of the oil unit 7 containing no more than two stages from gear pairs 39, 40. Gear pair 39 transmits torque with an increased gear ratio

i _sp5 = (1.23 ÷ 1.75)

through the engagement of the first gear 41 of the intermediate shaft 42 with the gear wheel 37 of the drive shaft 38 of the plunger pump multi-stage gearbox, and through the second cylindrical gear pair 40, also made with a gear ratio 1 _ШП6 , defined in the range of values

i _sp6 = (1.03 ÷ 1.46),

with a gear wheel 45 located on the combined drive shaft 43, in common with the drive shaft of the DTs 2. The working torque is transmitted to the oil unit 7 through a multi-stage drive of the oil unit 7 with a total gear ratio of i _ma , counting from the HPH shaft. The total gear ratio is formed by the combination of the gear ratios of the two-stage gearbox drive for the oil unit 7 from the cylindrical gear 37 on the drive shaft 38 of the pump 3 of the plunger and multi-stage gearbox of the drive of the pump 3 of the plunger, endowed with an additional function of transmitting working torque to the oil unit 7, defined in the range of values

i _ma = (0.47 ÷ 0.66).

The total gear ratio i _{ma of the} aggregate working multi-stage gearbox transmitting the shared working torque from the HPH shaft to the oil unit 7 is determined in the range of values relative to the HPH shaft

i _ma = (0.47 ÷ 0.66) [units / rad].

It is formed by the product of the ratios of the gear ratios of the fourth and fifth gears of the cylindrical gear pairs of the two-stage section of the gearbox of the oil unit 7 and the torque transmitting to it the multi-stage gearbox of the pump 3 of the plunger, counting from the shaft of the high pressure gearbox to the shaft 43 of the oil unit 7 and DTsN 2, having gear ratios

n _r.vrvd : i _gkp : i _{gkp kda} : i _dl1vv : i _dlp2 : i _dlp4 : i _dlp5 : i _dlp6 = (1) :( 1.01 ÷ 1.43) :( 0.71 ÷ 0.99) : (0.62 ÷ 0.88) :( 0.48 ÷ 0.68) :( 0.58 ÷ 0.83) :( 1.23 ÷ 1.75) :( 1.03 ÷ 1.46) where

n _{century rvd} - the relative number of revolutions of the shaft of the _{high pressure hitch} , taken as a unit;

i _tskp - gear ratio of the main bevel gear pair 10 TsKP 11;

i _{GKP KDA} - the same, the main bevel gear pair 13 GKP KDA 1;

i _shpvvv - the same, of the first cylindrical gear pair 18 formed by the leading main gear spur gear 16 of the input shaft 14 KDA 1 and the first spur gear 20 of the intermediate shaft 21 of the two-stage section of the gearbox of the pump-regulator 8;

i _Шп2 - the same, of the second cylindrical gear pair 19 formed by the second cylindrical gear wheel 22 of the intermediate shaft 21 and the driven gear 23 of the drive shaft 24 of the pump regulator 8.

i _sp4 - the same, of a third cylindrical gear pair 35 formed by a spur gear 36 located on the drive shaft 24 of the regulator pump 8 and the driven gear 37 located on the drive shaft 38 of the plunger pump 3.

i _sp5 - the same, of the fourth cylindrical gear pair 39 formed by the cylindrical gear 37 of the drive shaft 38 of the said plunger pump 3 and the first gear 41 of the intermediate shaft 42 located between the drive shafts 38, 43 of the pump 3 of the plunger and ДЦН 2, respectively.

i _sp6 - the same, of the fifth cylindrical gear pair 40 formed by the spur gear 44 of the said intermediate shaft 42 and the spur gear 45 of the drive shaft 43 of the center plate 2.

The oil unit 7 is installed on the lid of the housing KDA 1, communicate with the automatic control and regulation system (SAUiR), with the oil system and also with the working torque through a multi-stage gearbox drive communicate with the shaft of the high pressure hoses.

Implementation example.

The mechanism for transmitting torque to the units of a twin-shaft turbofan engine is as follows. They make parts, assemblies and assembly units, including bevel and cylindrical gears and shafts of TsKP 11, as well as gear drives for drives of engine and aircraft units KDA 1. They perform casting of the housing and cover TsKP 11 and KDA 1, in which machining, including grinding, prepare the contact surfaces of the flanges and seats by chrome plating and coating on the surface under the bearings in the housing of the CCP 11.

The main bevel gear pair 10 is assembled in the housing ЦКП 11. The bevel gear pair 13 ГКП КДА 1 is assembled in the housing КДА 1. The leading bevel gear ГКП with roller and thrust ball bearings are installed in the cage. The cage is performed covering the office and the outer end of the outer ring of the roller bearing. In the cage, an opening is sufficient to expose the teeth of the driven bevel wheel 15 of the hydraulic circuit board. The cylindrical section of the cage is provided with a flange for fastening by means of detachable elements with a flange of the housing KDA 1 from the outside and from the inside with a flange of the ring holder of the ball bearing housing. The reciprocal driven bevel gear 15 of the gear pair 13 is mounted on the input shaft 14 of the GCP KDA 1 on two bearings — a thrust ball bearing and a thrust roller bearing. The driven bevel gear 15 is fixed to the flange of the shaft 14 by means of six fasteners.

Manufactured bevel gear GKP perform with a bevel gear in the total number of teeth in the ring N _Z1 = 26 teeth. The driven wheel 17 is performed with a bevel gear in the total number of teeth in the ring N _Z2 = 33 teeth. Thus, the main gear pair 13 GKP KDA perform with a gear ratio of i _{1, rn} = 0.79.

From assembly units - cylindrical gears and shafts, KDA drive gearboxes are assembled and mounted in the cover and housing of KDA 1 gear transmission of torque to the units. The contact ends of the housing and cover KDA 1 center and connect the fasteners. The assembled housing KDA 1 is fixed on the upper part of the intermediate engine housing by means of external fastening elements. The input of torque into the housing of the KDA is carried out by means of a spring 12, which connects the driven bevel wheel of the central gearbox 11 of the main bevel gear pair 10 with the drive wheel of the bevel gear pair 113 of the cylinder head assembly KDA 1.

The motor units are mounted on the KDA 1 housing - a breather 4 centrifugal centrifugal pump, a pump 3 plunger NP, a motor centrifugal fuel priming pump 2 and an end bellows-hinge assembly 5 of a flexible shaft 6 for transmitting torque to the units of the remote box of aircraft units (RCA). On the cover of KDA 1, an oil unit 7 is mounted, a fuel regulator pump 8 and an afterburner pump 9.

KDA 1 engine units report the torque through the central control unit 1 with the HPH shaft by means of multistage gear drives of the unit drives with the ability to switch the units to work from the starter as from a source of starting torque in the engine starting mode.

KDA 1 engine assemblies report the torque through the central control gear 11 with the high pressure hoses shaft by means of multistage gearboxes of the unit drives with the formation of two groups of multistage gearboxes connected to the main spur gear 16 on the input shaft 14 of the GPC KDA 1. drive units includes a two-stage gear pump regulator 8, a three-stage gearbox souffler 4 centrifugal

and plunger pump 3, five-speed gearboxes of the motor centrifugal fuel-priming pump 2 and oil unit 7. The second group of gearboxes of the drive units includes two-stage gearboxes of the pump 9 of the afterburner and flexible shaft 6 for transmitting torque of the rotary gearbox.

The mechanism for transmitting torque to the KDA units works as follows.

In the normal engine operation mode, the torque transmitted to the KDA engine units is taken from the high-pressure turbine and transmitted to the central control gear 11 and then through the spring 12 to the drive wheel with a bevel gear pair 13 (GKP KDA). Through the driven wheel 15 of the bevel gear pair 13 GKP, torque is supplied directly to the main spur gear 16 of the input shaft 14 of the KDA. From the main distributing cylindrical gear wheel 16 by means of a branched set of gear pairs of gearboxes of the units, the torques are divided and distributed to these units and the rotation speed of the input shaft of each unit is proportional to the total gear ratios of the gearboxes. In this case, the gearboxes of the aircraft unit drives mounted in the RCA are communicated by torque from the central control unit 1 in series through a multi-stage gearbox KDA and a connecting flexible shaft 6.

The technical result of the group of inventions is also achieved due to the geometric parameters found in the invention of the KDA housing and the structure of multi-stage gearboxes of drive units installed in the KDA housing with balanced ratios of gear ratios of gear ratios of gear pairs of torque transmission gearboxes to KDA aggregates within the ranges of gear ratios specified in the invention numbers. Going up or down for both gear ratios, both increasing and decreasing gear ratios, is fraught with difficult compensation for unbalancing the gear and overloading the gearbox or the impossibility of eliminating the gearbox imbalance resulting from this, worsening the dimensions and weight of the KDA housing, unjustified increase in the material consumption of gear wheels of gear pairs and the volume they occupy in the KDA enclosure, the complexity of assembling / disassembling assemblies and assemblies, reducing the resource, reliability, efficiency and increasing power goemkosti work torque transmitting mechanism KDA or dangerous occurrence probability in the occurrence of resonance. The selected ranges of permissible values of the total gear ratios of the KDA units are also limited by the real variability of the design and the installation capacity of the latter. The effectiveness of the group of inventions is achieved by providing increased maintainability of the torque transmission mechanism nodes developed in the inventions, which reduces labor costs and the time it takes to perform maintenance and all types of engine repairs during its operation.

Claims (83)

1. The method of operation of the complex of motor units of the box of motor units (KDA) in the mode of operation of a twin-shaft double-circuit turbojet engine (TRD) having coaxial shafts of high pressure rotors (RVD), low pressure (RND), a central conical drive (CCP), a box of motor units (KDA) and the remote box of aircraft units (RCA), characterized in that the working torque in the process of engine operation is taken from the high pressure hoses and sequentially sent through the main bevel gear pair of the central conical drive (CCP), a spring informing the CCP for torque with a bevel gear pair of the main conical drive (GPC) of the KDA, and through the driven conical gear mounted on the input shaft of the GPC KDA, are fed to the gearbox made in one piece with the input shaft of the KDA and having a gear crown with tooth angular frequency γ _c.c.in. = (2.87 ÷ 4.30) [unit / rad] the main spur gear, communicated by torque not less than two cylindrical gears in contact with it with the formation of two head gear pairs of multi-stage gearboxes, one of which is made with a reduction gear ratio defined in the range i _shp1vv = (0.62 ÷ 0.88), and the other is made with a gear ratio defined in the range i _sp2vv = (1.03 ÷ 1.25); moreover, these gear pairs are made dividing the share flows of working torque into two groups according to the number of units - the final recipients of the share flows of working torque, while the first of these groups transports the share flows of working torque through the combined multi-stage gearboxes of at least five motor units KDA, and the other transmits shared torque flows to multi-stage gearboxes consisting of no more than two stages of cylindrical gears Transmission ies at least one of the propulsion units KDA and arranged in a two-stage portion of KDA another gear enables transmission via a flexible shaft running torque airborne remote units carton (BKA); moreover, from the KDA input shaft, the shared working torques are distributed between the motor units in accordance with the power consumed by them and the rotation speeds of the aggregate shafts relative to the rotation speed of the KDA input shaft. 2. The method of operation of the complex of motor units of the box of motor units (KDA) according to claim 1, characterized in that from the input shaft of the KDA, the shared working torques are distributed between the engine units in accordance with the power consumed by them and the speeds of rotation of the shafts of the units, expressed relative to the speed of rotation the WFD shaft by two groups of gear ratios, the first of which is determined by the ranges of values n _int.rvd : i _nr : i _ts : i _np : i _dtsn : i _ma = (1) :( 0.39 ÷ 0.55) :( 0.79 ÷ 0.99) :( 0.28 ÷ 0 , 39) :( 0.47 ÷ 0.66) :( 0.47 ÷ 0.66), where n _{BB RVD} - the relative number of revolutions of the RVD shaft, taken as a unit; i _np is the gear ratio of the gearbox of the pump regulator relative to the shaft of the _{high pressure hitch} ; i _cs - the same as a centrifugal prompter gearbox; i _np - the same as a plunger gear pump; i _dtsn - the same gear motor centrifugal pump; i _ma - the same, gear unit; the second group combines ratios of gear ratios, which are defined by ranges of values n _{centuries rvd} : i _n.f : i _m.v. = (1) :( 1.75 ÷ 2.46) :( 0.61 ÷ 0.85), Where n _{BB RVD} - the relative number of revolutions of the RVD shaft, taken as a unit; i _n.ph. - the gear ratio of the afterburner gearbox relative to the HPH shaft; i _onwards - the same, the internal section of the gearbox in the KDA, which supplies the shared working torque to the flexible shaft for the VKA units. 3. The method of operation of the complex of motor units of the box of motor units (KDA) according to claim 1, characterized in that the box of motor units is made in the form of a prefabricated spatial shell; on the bottom of the box body, the KDA engines included in the complex of engine assemblies are mounted: a motor centrifugal fuel priming pump, pump a plunger, a centrifugal prompter, as well as an end bellows-hinged assembly of a flexible shaft on the bottom of the case to the box; and an oil aggregate, a fuel pump-regulator and an afterburner are mounted on the box lid, and the working torque is transmitted to the motor units through the branched gear system of multi-stage gearboxes installed in the internal volume of the KDA. 4. The method of operation of the pump of the plunger box of motor units (KDA) in the operation mode of a twin-shaft double-circuit turbojet engine (TRD) having a high-pressure rotor shaft (HPH), a central conical drive (CCP), a box of motor units, including a pump regulator, a plunger pump , and a remote box of aircraft units (VKA), characterized in that the plunger pump performs the working function of supplying high-pressure fluid to the engine control system using the energy of the working torque radiated by the unit during operation of the engine from the rotating shaft of the WFD; at the same time, during the operation of the engine, the working torque is taken from the high pressure hoses shaft and sequentially through a spline sleeve coaxial with the shaft, endowed with two rows of external front-end slots with an angular frequency of the splines γ _nw = (12.4 ÷ 20.1) [unit / rad] and further, through the main bevel gear pair of the central bevel gear (CCP) and the spring informing the CCP in torque with the bevel gear pair of the main bevel gear (GPC) of the KDA, and the driven bevel gear mounted on the input shaft of the GPC KDA, feed the indicated KDA to the input shaft of the KDA to made in one piece with it, having a ring gear with an angular frequency of teeth γ _c.c.in. = (2.87 ÷ 4.30) [unit / rad] the main cylindrical gear wheel, from which the working torque is supplied to the plunger pump through a three-stage gear section made of sequentially arranged cylindrical gear pairs with lower gear ratios i _{gear 1vv} , i _{gear 2} and i _{gear 4} as part of a common multi-stage gear pump plunger transmitting a shared working torque to said shaft assembly by RVD, to form the overall gear ratio i _np obtained as the product received from ratio Range mesons gear ratios of said gear stages, counting from the RVD shaft n _r.vrvd : i _hkp : i _{hpc kda} : i _dl1vv : i _dlp2 : i _dlp4 = (1) :( 1.01 ÷ 1.43) :( 0.71 ÷ 0.99) :( 0.62 ÷ 0.88) :( 0.48 ÷ 0.68) :( 0.58 ÷ 0.83), where n _{century rvd} - the relative number of revolutions of the shaft of the _{high pressure hitch} , taken as a unit; i _CCL - gear ratio of the main bevel gear pair of CCL; i _{GKP KDA} - the same, the main bevel gear pair GKP KDA; i _Шп1вв - the same, of the first cylindrical gear pair formed by the leading main distributing spur gear and the first spur gear of the intermediate shaft of the three-stage section of the plunger pump gearbox; i _sp2 - the same, of the second cylindrical gear pair formed by the second cylindrical gear wheel of the intermediate shaft and the driven gear of the drive shaft of the plunger pump; i _sp4 ^_ the same, of a third cylindrical gear pair formed by a leading spur gear located on the drive shaft of the regulator pump and a driven gear located on the drive shaft of the plunger pump; and defined in the range of values relative to the shaft i _np = (0.28 ÷ 0.39). 5. The method of operation of the pump of the plunger box of motor units (KDA) according to claim 4, characterized in that the plunger pump is installed on the cover of the KDA housing, in communication with the automatic control and regulation system (SAUiR), as well as with the fuel and oil system and working torque through a multi-stage gear drive communicated with the shaft of the WFD. 6. The pump plunger box motor units (KDA) of a twin-shaft turbofan engine (TRD), characterized in that it contains a housing with a cover, a spring connected to a shaft endowed with a spring, plungers and an inclined washer that allows axial movements of the rod part of the plungers in cylinder block concentrically spaced in the pump casing around the unit shaft with an angular frequency γ _pl = (1.20 ÷ 1.72) [unit / rad], with alternating phases of suction and discharge of the working fluid - fuel in each revolution of the shaft; moreover, the pump is made of the axial type with adjustable flow and end distribution of the working fluid with the possibility of implementing the working function of supplying high pressure fluid to the engine control system using the energy of the working torque received by the unit from the WFD shaft during the operation of the engine, performed by the method according to any one of claims . 4 and 5. 7. The method of operation of a motor centrifugal fuel priming pump of a box of motor units (KDA) in the operation mode of a twin-shaft double-circuit turbojet engine (TRD) having a rotor shaft of high pressure (RVD), a central conical drive (CCP), a box of motor units, a pump regulator, a pump a plunger and remote box of aircraft units (VKA), characterized in that the centrifugal propulsion fuel pump has a housing with a working body for fuel injection and performs a working function May increase the pressure in the fuel system of the engine using for this energy the working torque received by the unit during operation of the engine from the rotating shaft of the WFD; in this case, the working torque is taken from the RVD shaft and sequentially through a spline sleeve coaxial with the shaft, endowed with two rows of external front-end splines with the angular frequency of the splines γ _nw = (12.4 ÷ 20.1) [unit / rad] and then, through the main bevel gear pair of the central bevel drive (CCL), the torque is transmitted to the conical gear pair of the main bevel drive (GPC) of the KDA and, accordingly, the driven bevel gear installed on the input shaft of the GPC KDA, then fed to the KDA for the input shaft one with it, having a ring gear with an angular frequency of teeth γ _c.c.in. = (2.87 ÷ 4.30) [unit / rad] the main cylindrical transfer gear, from which the working torque is supplied to the engine centrifugal fuel priming pump, through no more than a five-stage gear section made of sequential cylindrical gear pairs having gear ratios i _{gear 1} , gear 2, gear ₄ , _{gear 5} , _{gear 6} included in the total gear ratio i of the _{engine center of a} multi-stage working gearbox transmitting the shared working torque from the HPH shaft to the fuel pump, while the indicated total gear ratio i _{dtsn is} received as a product of the ranges of gear ratios of all stages of a multi-stage gearbox taken from the ratio, counting from the _{high pressure hitch} shaft, n _r.vrvd : i _gkp : i _{gkp kda} : i _dl1vv : i _dlp2 : i _dlp4 : i _dlp5 : i _dlp6 = (1) :( 1.01 ÷ 1.43) :( 0.71 ÷ 0.99) : (0.62 ÷ 0.88) :( 0.48 ÷ 0.68) :( 0.58 ÷ 0.83) :( 1.23 ÷ 1.75) :( 1.03 ÷ 1.46) where n _{century rvd} - the relative number of revolutions of the shaft of the _{high pressure hitch} , taken as a unit; i _CCL - gear ratio of the main bevel gear pair of CCL; i _{GKP KDA} - the same, the main bevel gear pair GKP KDA; i _shpvvv - the same, of the first cylindrical gear pair formed by the leading main distributing spur gear and the first spur gear of the intermediate shaft of the five-stage section of the fuel pump gearbox; i _sp2 ^_ the same, the second cylindrical gear pair formed by the second cylindrical gear wheel of the intermediate shaft and the driven gear of the drive shaft of the pump regulator; i _sp4 - the same, of a third cylindrical gear pair formed by a leading cylindrical gear located on the drive shaft of the regulator pump and a driven gear located on the drive shaft of the plunger pump; i _sp5 ^_ the same, of a fourth cylindrical gear pair formed by a cylindrical gear of a drive shaft of said plunger pump and a first gear of an intermediate shaft located between drive shafts of a plunger pump and a fuel feed pump; i _sp6 - the same, of a fifth cylindrical gear pair formed by a cylindrical gear of said intermediate shaft and a cylindrical gear of a drive shaft of a fuel priming pump; and defined in the range of values relative to the shaft of the WFD as i _dtsn = (0.47 ÷ 0.66). 8. The method of operation of the engine centrifugal fuel pump according to claim 7, characterized in that the engine centrifugal fuel pump is installed on the bottom of the housing KDA, communicates with the automatic control and regulation system (SAUiR), with the fuel and oil systems and operating torque through a multi-stage drive gear communicated with the shaft of the high pressure hitch. 9. An engine centrifugal fuel priming pump of a box of engine units (KDA) of a twin-shaft twin-circuit turbojet engine (TRD), characterized in that it has a housing with a working gear type or in the form of an impeller installed in it and is configured to implement the working function of increasing the fuel pressure in the fuel system of the engine using the energy of the working torque received by the unit from the WFD shaft during engine operation, is performed th method according to any one of paragraphs. 7 and 8. 10. The method of operation of the oil unit of the box of motor units (KDA) in the operation mode of a twin-shaft double-circuit turbojet engine (TRD) having a high-pressure rotor shaft (HPH), a central conical drive (CCP), a box of motor units and a remote box of aircraft units (RCA), characterized in that the oil unit contains a housing comprising at least two sections, with installed in the first pumping equipment for pumping and filtering the used oil, and pumping equipment in the second section for returning the oil to the engine oil system, and performs the working function of pumping out, filtering the used oil and returning the refined oil to the engine oil system using the working torque for this energy obtained during the engine operation from the rotary shaft of the high pressure hitch; at the same time, during the operation of the engine, the working torque is taken from the high pressure hoses shaft and sequentially through a spline sleeve coaxial with the shaft, endowed with two rows of external front-end slots with an angular frequency of the splines γ _b.w. = (12.4 ÷ 20.1) [unit / rad] and further, through the main bevel gear pair of the central bevel gear (CCP) and the spring informing the CCP in torque with the bevel gear pair of the main bevel gear (GPC) of the KDA, and the driven bevel gear mounted on the input shaft of the GPC KDA, feed the indicated KDA to the input shaft of the KDA to made in one piece with it, having a ring gear with an angular frequency of teeth γ _d.c.in. = (2.87 ÷ 4.30) [unit / rad] the main cylindrical gear wheel, from which the working torque is supplied to the oil unit through a multi-stage drive gearbox, which includes a multi-stage plunger pump drive gearbox and its own oil unit drive gearbox as a section of the common oil unit gearbox no more than two stages from gear pairs, the first of which transmits torque with an increasing gear ratio i _sp5 = (1.23 ÷ 1.75) through the engagement of the first gear of the intermediate shaft with the gear gear of the drive shaft of the mentioned multi-stage gearbox of the plunger pump, and through the second cylindrical gear pair, also made with an increasing gear ratio i _shp6 , defined in the range of values i _sp6 = (1.03 ÷ 1.46), with a gear located on the combined drive shaft, in common with the drive shaft of the engine centrifugal fuel pump, and the specified working torque is transmitted to the oil unit through a multi-stage drive of the oil unit with a total gear ratio of i _ma , counting from the HPH shaft, formed by a combination of gear ratios of a two-stage gearbox drive of the oil unit from a cylindrical gear on the drive shaft of the plunger pump and multi-stage gearbox of the plunger pump drive, endowed additional transfer function of the working torque oil system blocks identified in the range i _ma = (0.47 ÷ 0.66). 11. The method of operation of the oil aggregate according to claim 10, characterized in that the total gear ratio i _{ma of the} aggregate working multi-stage gearbox transmitting the shared working torque from the HPH shaft to the oil aggregate is determined in the range of values relative to the HPH shaft i _ma = (0.47 ÷ 0.66) [units / rad] and is formed by the product of the ratios of the gear ratios of the fourth and fifth stages of cylindrical gear pairs of a two-stage section of the oil unit gearbox and the torque transmitting to it a multi-stage gearbox of the plunger pump, counting from the RVD shaft to the oil unit shaft having gear ratios n _r.vrvd : i _gkp : i _{gkp kda} : i _dl1vv : i _dlp2 : i _dlp4 : i _dlp5 : i _dlp6 = (1) :( 1.01 ÷ 1.43) :( 0.71 ÷ 0.99) : (0.62 ÷ 0.88) :( 0.48 ÷ 0.68) :( 0.58 ÷ 0.83) :( 1.23 ÷ 1.75) :( 1.03 ÷ 1.46) where n _{century rvd} - the relative number of revolutions of the shaft of the _{high pressure hitch} , taken as a unit; i _CCL ^_ gear ratio of the main bevel gear pair of CCL; i _{GKP KDA} - the same, the main bevel gear pair GKP KDA; i _Шп1вв - the same, of the first cylindrical gear pair formed by the leading main spur gear of the input shaft of the KDA and the first cylindrical gear of the intermediate shaft of the two-stage section of the gearbox of the pump-regulator drive; i _sp2 ^_ the same, the second cylindrical gear pair formed by the second cylindrical gear wheel of the intermediate shaft and the driven gear of the drive shaft of the pump regulator; i _sp4 ^_ the same, of the third cylindrical gear pair formed by the driving spur gear located on the drive shaft of the regulator pump and the driven gear located on the drive shaft of the plunger pump. i _sp5 - the same, of the fourth cylindrical gear pair formed by the cylindrical gear of the drive shaft of the said plunger pump and the first gear of the intermediate shaft located between the drive shafts of the plunger pump and the motor centrifugal fuel priming pump, respectively. i _Шп6 - the same, of the fifth cylindrical gear pair formed by the cylindrical gear wheel of the said intermediate shaft and the cylindrical gear wheel of the drive shaft is a motor centrifugal fuel priming pump. 12. The method of operation of the oil aggregate according to claim 10, characterized in that the oil aggregate is installed on the cover of the KDA housing; it is communicated with an automatic control and regulation system (SAUiR), with an oil system, and also with a working torque through a multi-stage gearbox of the drive, it is communicated with the RVD shaft . 13. The oil unit of the box of motor units (KDA) of a twin-shaft double-circuit turbojet engine (TRD), characterized in that it is configured to implement the working function of pumping out, filtering the used oil and returning the cleaned oil to the engine oil system by the method according to any one of paragraphs. 10-12 using for this purpose in the process of engine operation the energy of working torque from the shaft of the high pressure hitch.

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