CN115823224A - Transmission mechanism of torque measuring pump of aircraft engine - Google Patents

Abstract

The invention discloses an aero-engine torque measurement pump transmission mechanism, which comprises an aero-engine speed reducer part, wherein the speed reducer part comprises a gear connecting hub and a speed reducer casing, a torque measurement pump is arranged below the speed reducer casing, a flange mounting edge is arranged on a radial plate of the gear connecting hub, the aero-engine torque measurement pump transmission mechanism further comprises a driving gear, a driven gear and a coupling which is respectively connected with the torque measurement pump and the driven gear, the driving gear comprises an inner mounting edge and an outer tooth part, the driving gear is connected to the flange mounting edge through the inner mounting edge, the driven gear comprises a driving shaft and a driven tooth part, the driving shaft is connected with the driven tooth part through a conical radial plate, and the driven tooth part is meshed with an outer tooth part of the driving gear; the bearing unit is sleeved on the outer surface of the driving shaft and is installed in a bearing support seat on the casing of the speed reducer. The transmission mechanism has few transmission parts, the power transmission reliability is ensured by the connection between the transmission parts, and each part is arranged in the narrow inner cavity of the casing of the speed reducer, so that the compact structure effect is realized.

Description

Transmission mechanism of torque measuring pump of aircraft engine

Technical Field

The invention relates to the technical field of mechanical transmission, in particular to a transmission mechanism of a torque measuring pump of an aero-engine.

Background

Aircraft engine accessories typically draw power from the engine to enable their function. With the development of aero-engines with high thrust-weight ratio, the engines must meet the requirements of compact structure, light weight and high reliability, so that for the accessory transmission mechanism built in the engines, how to reduce the number of transmission mechanism components and the size and weight of the engine accessory pump and the transmission mechanism is the research direction of advanced accessory transmission schemes, and the structural design of integrating the accessories and the engines is an effective measure for minimizing transmission parts.

The speed reducer of a turboprop type aero-engine outputs the shaft power of the engine to an important part of a propeller, a hydraulic torque measuring system is arranged in the speed reducer and used for measuring the output torque and power of the engine, high-pressure oil in the torque measuring system needs to work and be pressurized through a torque measuring pump, therefore, the engine needs to be provided with the torque measuring pump and is arranged on a mounting seat on the lower right of a speed reducer part speed reducer casing, in order to avoid arranging an additional accessory for driving the torque measuring pump to work on the engine, a mechanical transmission mechanism which can lead part of power out from a gear transmission mechanism in the speed reducer part and transmit the power to the torque measuring pump needs to be designed, so that the torque measuring pump and the engine speed reducer part are connected into a whole, the torque measuring pump is driven to work efficiently, and the high working reliability of the torque measuring system of the engine is kept.

The patent with publication number CN108104949B discloses a multifunctional speed reduction transmission casing structure of a micro gas turbine, wherein the whole lubricating oil system is arranged in the speed reduction transmission casing, the whole accessory transmission system and the speed reduction system are integrated into a whole by skillfully designing the internal and external structures of an input casing and an output casing, and the whole accessory system is arranged on the outer side of the speed reduction transmission casing, so that the volume of the gas turbine is reduced to a great extent, the whole spatial layout of the gas turbine is optimized, and the whole gas turbine is compact in structure. Although the patent also aims to be compact, the accessory transmission system is still arranged outside the speed reduction transmission casing, the detailed transmission mechanism structure arrangement is not involved, the compact structure effect cannot be confirmed, and how the speed reduction system and the accessory transmission system perform mechanical transmission is not known.

Disclosure of Invention

The technical problem to be solved by the invention is to overcome the defects of the prior art and provide the aero-engine torque measurement pump transmission mechanism which is simple and compact in structure and can reliably and efficiently transmit partial power of the speed reducer part to the torque measurement pump.

The purpose of the invention is realized by the following technical scheme:

the utility model provides an aeroengine surveys and turns round pump drive mechanism, including aeroengine reduction gear part, reduction gear part includes gear connection hub and reduction gear machine casket, survey and turn round the pump to install below reduction gear machine casket, set up the flange mounting edge on the radials of gear connection hub, still include driving gear and driven gear, the driving gear includes interior mounting edge and outer tooth portion, the driving gear is connected on the flange mounting edge through interior mounting edge, the driven gear includes integrated design's drive shaft and driven tooth portion, meet through the conical surface radials between drive shaft and the driven tooth portion, driven tooth portion meshes with the outer tooth portion of driving gear; the outer surface of the driving shaft is sleeved with a bearing unit, the bearing unit is arranged in a bearing support seat, and a mounting hole is formed in the speed reducer casing and used for mounting the bearing support seat; the torque measuring pump also comprises a coupling which is respectively connected with the torque measuring pump and the driven gear through splines.

Furthermore, the end part of the coupling close to the driving shaft is connected with the driving shaft by arranging an external spline, and the other end of the coupling is provided with an internal spline which is meshed with a tooth part of a transmission driving gear of the torque measuring pump; one end of the inner spline of the coupling, which is close to the torque measuring pump, is provided with a circle of retainer ring groove, and the other end of the inner spline, which is far away from the torque measuring pump, is provided with a tool withdrawal groove.

Furthermore, the external splines and the internal splines on the coupling are involute splines.

Further, the flange mounting edge is arranged in the middle of the spoke plate of the gear connecting hub.

Furthermore, the inner installation edge of the driving gear is connected with the outer tooth part through a cylindrical surface wheel rim.

Furthermore, the conical surface radials of the driven gears are linear conical surface radials, and a plurality of through hole grooves are formed in the conical surface radials.

Further, the bearing unit comprises bearings arranged at two ends of the driving shaft and spacing bushes arranged between the bearings at the two ends, and a grooved round nut and a stop washer are sleeved on the periphery of the end part, close to the shaft coupling, of the driving shaft so as to fix the bearing unit.

Further, the outer diameter of the shaft section of the drive shaft on which the spacer bush is mounted is smaller than the outer diameter of the shaft section on which the bearing is mounted.

Further, the bearing is a deep groove ball bearing.

Furthermore, the bearing support seat is in clearance connection with a mounting hole in the casing of the speed reducer.

Compared with the prior art, the invention has the following beneficial effects:

the power at the gear connecting hub in the speed reducer part is led out of the transmission driving gear of the transmission torque measuring pump only through the pair of gear pairs and the coupling, the number of transmission parts is small, the connection mode of the driving gear and the gear connecting hub, the structural design of the driven gear and the coupling guarantee the reliability of power transmission, two ends of the coupling are in floating connection with the driven gear and the transmission driving gear of the torque measuring pump respectively through a spline structure, the connected axis is compensated for certain radial displacement and deflection through backlash matching centering, and the load-sharing characteristic of the spline tooth surface is realized;

by carrying out size reduction structural design on each component of the transmission mechanism, each component can be installed in a narrow inner cavity of a casing of the speed reducer, and the compact structure effect of the engine is really realized;

the tool withdrawal groove arranged in the inner spline of the coupling has a shearing diameter function, and when the load transmitted by the engine through the transmission mechanism is abnormal or the torque measuring pump is clamped, the coupling can be twisted off at the shearing diameter to protect the engine or the torque measuring pump.

Drawings

FIG. 1 is a schematic structural view of a transmission mechanism according to embodiment 1 of the present invention;

FIG. 2 is a sectional view of a shaft coupling in embodiment 1 of the invention

Fig. 3 is a side view of a driven gear in embodiment 1 of the invention;

fig. 4 is a sectional view of a driven gear in embodiment 2 of the invention.

Detailed Description

In order to clearly illustrate the technical features of the present solution, the following detailed description of the present solution is provided with reference to the accompanying drawings.

In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present application, however, the present application may be practiced in other ways than those described herein, and therefore the scope of the present application is not limited by the specific embodiments disclosed below.

In addition, in the description of the present application, it is to be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", and the like, indicate orientations and positional relationships based on those shown in the drawings, are only for convenience of description and simplicity of description, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the present application. Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present application, "a plurality" means two or more unless specifically limited otherwise.

In this application, unless expressly stated or limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can include, for example, fixed connections, removable connections, or integral parts; the connection can be mechanical connection, electrical connection or communication; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art as appropriate.

In this application, unless expressly stated or limited otherwise, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through intervening media. In the description herein, reference to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the application. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

Example 1

As shown in fig. 1, the aero-engine torque measurement pump transmission mechanism comprises an aero-engine speed reducer part, the speed reducer part comprises a gear connection hub 1 and a speed reducer casing 2, a torque measurement pump 3 is mounted on a torque measurement pump mounting seat on the right lower portion of the outer surface of the speed reducer casing 2, the transmission mechanism is used for dividing partial power of the speed reducer part to drive the torque measurement pump 3 to work, the gear connection hub 1 is a power input mechanism of the transmission mechanism, a circular boss flange mounting edge 11 with a plurality of threaded holes is formed in a radial plate of the gear connection hub 1, the transmission mechanism comprises a driving gear 4 and a driven gear 5, the driving gear 4 comprises an inner mounting edge 41 and an outer tooth 42, the inner mounting edge 41 and the outer tooth 42 of the driving gear are connected through a cylindrical flange 43, connecting holes with the number equal to that of the threaded holes in the circular boss flange mounting edge 11 are formed in the inner mounting edge 41, the driving gear 4 is connected to the circular boss flange mounting edge 11 through the inner mounting edge 41, namely, the inner mounting edge 41 and the circular boss flange mounting edge 11 are internally provided with stop washers, the driving gear 4 can be fastened on the gear connection hub 1 through the single-lug stop washers to transmit power, the driving gear adopts single-lug stop washers, and the single-head stop washers are vertical stop washers, and the hexagonal bolts are convenient for interchange. The mode of adopting screw connection, friction torque transmission and positioning by the cylindrical surface of the circular boss and the rim 43 of the cylindrical surface has simple structure, is convenient to process and is beneficial to supporting and positioning the driving gear 4.

Wherein, circular boss flange installation limit 11 sets up in gear connection hub 1 radials middle part position, makes driving gear 4 have major diameter, so on the one hand can increase the figure of the screw of usefulness of connecting, on the other hand can reduce the influence of both contact surface machining inaccuracy to gear engagement.

Because the peripheral speed and the transmission load of the driving gear 4 are lower, the driving gear 4 is selected as an involute cylindrical gear which is a high-performance gear with multiple teeth, thin rim and narrow tooth width, and has the main characteristics of light weight, fine structure, high bearing capacity and high working reliability in structure. Meanwhile, in order to improve the wear resistance and fatigue strength of the driving gear 4, the driving gear 4 needs to be carburized.

In fig. 1, the driven gear 5 includes a driving shaft 51 and a driven tooth portion 52 which are integrally designed, the driving shaft 51 is connected with the driven tooth portion 52 through a conical web 53, the driven tooth portion 52 is meshed with the external tooth portion 42 of the driving gear 4, and the driving gear 4 drives the driven gear 5 to rotate through the external tooth portion 42; the outer surface of the driving shaft 51 is sleeved with a bearing unit 54, the bearing unit 54 is installed in a bearing support 55, the speed reducer casing 2 is provided with an installation hole for installing the bearing support 55, and the transmission mechanism further comprises a coupling 6 which is in splined connection with the torque measuring pump 3 and the driven gear 5 respectively.

The speed reducer casing 2 is an integral casing shell, and is preferably made of magnesium alloy materials for reducing weight, and the mounting hole is formed in a middle web plate of the speed reducer casing; in addition, the corresponding position of the middle web plate on the excircle of the speed reducer casing 2 is the mounting surface of the torque measuring pump mounting seat.

The driven gear 5 integrates the driven tooth part 52, the conical web 53 and the driving shaft 51, so that the structure is simplified, and the precision and the working reliability can be improved. The driven gear 5 also adopts an involute cylindrical gear, the number of teeth is designed according to the rotation speed conversion, and the tooth width is narrow. The conical surface spoke plate 53 is designed into an equal-thickness linear conical surface spoke plate, so that the axial rigidity of the conical surface spoke plate can be improved, and the overall length of the driven gear is reduced; as shown in fig. 3, the conical web 53 is provided with a plurality of through-hole grooves 531, the through-hole grooves 531 can reduce the weight of the driven gear 5, and the transmission mechanism is located inside the speed reducer component, the working environment is oil mist lubrication, and the through-hole grooves 531 are provided to facilitate the lubricating oil mist inside the speed reducer to pass through the grooves to lubricate the bearing unit 54.

A flange is arranged at the switching part of the driving shaft 51 of the driven gear 5 and the conical radial plate 53 and is used for axial limiting of the bearing unit 54; specifically, the bearing unit 54 includes bearings 541 respectively disposed at two ends of the driving shaft 51 and a spacer bushing 542 located between the bearings at the two ends, two sections of journals for assembling the bearings are disposed at two ends of the driving shaft 51, the spacer bushing 542 plays a role in spacing the bearings and limiting a distance between bearing fulcrums, the bearings at the two ends are ball bearings, a groove is disposed at an end of the bearing support 55 close to the driven gear conical web 53 for installing the elastic retainer ring 56, the bearing unit 54 is axially limited, a slotted round nut 57 and a stop washer 58 are sleeved on an outer periphery of an end of the driving shaft 51 close to the coupling 6 for locking the bearing unit 54, so that the bearing unit 54 forms a unit structure which can be conveniently disassembled on the shaft of the driven gear 5. Applying a suitable tightening torque to the slotted round nut 57 to lock the inner race of the bearing to the driven gear drive shaft 51 and preload the bearing to eliminate bearing end runout; the pre-bent inner ring locking claw of the stop washer 58 is assembled in the locking claw groove of the driven gear 5, and after the grooved round nut 57 is screwed down, the outer ring locking claw of the stop washer 58 is bent into the locking claw groove of the grooved round nut 57, so that the loosening phenomenon of the grooved round nut 57 in the working process is prevented.

The driven gear 5 is supported by a simple mounting using two ball bearings, which minimizes the influence of bearing play and angular deformation of the shaft of the driven gear 5 on the deflection of the driven gear 5, and optimizes the load distribution generated in the bearings and the bearing support 55. In order to prevent the ball bearing from being too large in looseness or excessively worn due to work or thermal expansion, the bearing support 55 is made of steel materials, a flange is arranged at the end part, close to the coupling 6, of the bearing support, a groove for installing the elastic check ring 56 is formed in the other end of the bearing support, the elastic check ring 56 is an elastic check ring for holes and is tensioned in the groove by elasticity, a small hole convenient to install and disassemble is formed in the opening, the bearing support 55 carries out axial limiting on the outer ring of the ball bearing and the driven gear 5 and has a certain axial clearance, so that clamping stagnation of the bearing due to thermal expansion in the working process is avoided, and meanwhile, a certain axial movement of the bearing is ensured; a plurality of flange connecting edges 551 with holes are formed on the outer surface of the bearing support seat 55, studs, nuts and stop washers are arranged at the positions of the flange connecting edges 551, and the bearing support seat 55 is mounted on the end surface of the mounting hole of the speed reducer case 2; the nut adopts a hexagon nut, and the stop washer adopts an angular vertical single-lug stop washer.

The driven tooth part 52 transmits power to a driving gear of the torque measuring pump 3 through a coupling 6 to drive the torque measuring pump 3 to work, the end part of the coupling 6 close to the driving shaft 51 is connected with the driving shaft 51 through an external spline 61, the other end of the coupling 6 is provided with an internal spline 62 to be meshed with the transmission driving gear tooth part of the torque measuring pump 3, and the external spline 61 and the internal spline 62 on the coupling are involute splines; as shown in fig. 2, a circle of retainer ring groove 63 is formed at one end of the inner spline 62 of the coupling 6 close to the torque measuring pump 3, a tool withdrawal groove 64 is formed at one end of the inner spline far from the torque measuring pump 3, a steel wire retainer ring is installed in the retainer ring groove 63 to limit axial movement of the coupling 6, the tool withdrawal groove 64 has a shearing diameter function, and when load abnormality transmitted by an engine through the transmission mechanism or jamming of the torque measuring pump 3 occurs, the coupling 6 is directly twisted off at the shearing diameter to protect the engine or the torque measuring pump 3. The two ends of the coupling 6 adopt spline floating connection structures, and the spline floating connection structures can compensate certain radial displacement and deflection of the connected axis through side clearance fit centering, so that the load-balancing characteristic of the spline tooth surface is realized, and the mounting and the dismounting are convenient. In order to improve the wear resistance and fatigue strength of the coupling 6, the coupling 6 is entirely subjected to cyanidation.

In order to facilitate the installation and replacement of the bearing support 55, the outer circle of the bearing support 55 is in small clearance fit with the installation inner hole of the speed reducer casing 2.

According to the torque measuring pump, the gear connecting hub 1 is connected through the screw to divide power to the driving gear 4, and then the driving gear of the torque measuring pump 3 is driven by the driven gear 5 and the coupling 6, so that the torque measuring pump 3 works normally, the number of transmission components is small, the size is small, and the reliability and the stability of power transmission can be realized on the basis of a simpler integral structure of a transmission mechanism; two bearings are fixed on a transmission driven gear of the torque measuring pump 3 through a locking structure of a grooved round nut 57 to form a unit body structure, so that the assembly and disassembly are convenient; the driven gear unit and the bearing support 55 are installed in a narrow inner cavity of the speed reducer casing 2, so that a compact structural design is realized.

Example 2

The present example differs from example 1 in that: as shown in fig. 4, the outer diameter of the shaft segment of drive shaft 51 on which spacer bushing 542 is mounted is smaller than the outer diameter of the shaft segment at which bearing 541 is mounted to facilitate assembly of the bearing and spacer bushing.

Example 3

The present embodiment differs from embodiment 2 in that: the bearing further selects a deep groove ball bearing, so that trace axial displacement can be effectively ensured.

It should be understood that the above examples are only for clearly illustrating the technical solutions of the present invention, and are not intended to limit the embodiments of the present invention. Other variations and modifications will be apparent to persons skilled in the art in light of the above description. This need not be, nor should it be exhaustive of all embodiments. Any modification, equivalent replacement, and improvement made within the spirit and principle of the present invention should be included in the protection scope of the claims of the present invention.

Claims (10)

1. The utility model provides an aeroengine surveys and turns round pump drive mechanism, includes aeroengine reduction gear part, and the reduction gear part includes gear connection hub and reduction gear machine casket, installs and surveys the pump of turning round below reduction gear machine casket, its characterized in that, sets up flange installation limit on the radials of gear connection hub, still includes driving gear and driven gear, the driving gear includes interior installation limit and outer tooth portion, and the driving gear passes through interior installation limit to be connected on the flange installation, and driven gear includes the drive shaft and the driven tooth portion of integrated design, meets through the conical surface radials between drive shaft and the driven tooth portion, and the external tooth portion meshing of driven tooth portion and driving gear; the outer surface of the driving shaft is sleeved with a bearing unit, the bearing unit is arranged in a bearing support seat, and a mounting hole is formed in the speed reducer casing and used for mounting the bearing support seat; the transmission mechanism also comprises a coupling which is respectively connected with the torque measuring pump and the driven gear by splines.

2. The aero-engine torque measurement pump transmission mechanism according to claim 1, wherein an end portion of the coupling close to the drive shaft is connected with the drive shaft through an external spline, and an internal spline is arranged at the other end of the coupling and meshed with a gear portion of a torque measurement pump transmission driving gear; one end of the inner spline of the coupling, which is close to the torque measuring pump, is provided with a circle of retainer ring groove, and the other end of the inner spline, which is far away from the torque measuring pump, is provided with a tool withdrawal groove.

3. The aircraft engine torque measurement pump transmission mechanism of claim 2, wherein the external splines and the internal splines on the coupling are involute splines.

4. The aircraft engine torque measuring pump drive mechanism of claim 1, wherein the flange mounting edge is disposed at a central location of a gear attachment hub web.

5. The aero-engine torque measuring pump transmission mechanism of claim 1, wherein the inner mounting edge and the outer tooth of the drive gear are connected by a cylindrical rim.

6. The aircraft engine torque measuring pump transmission mechanism as defined in claim 1, wherein the conical web of the driven gear is a linear conical web, and the conical web is provided with a plurality of through-hole slots.

7. The aero-engine torque measuring pump transmission mechanism as claimed in claim 1, wherein the bearing unit includes bearings respectively provided at both ends of the drive shaft and a spacer bushing provided between the bearings at both ends, and a grooved nut and a stopper washer are fitted around an outer circumference of an end portion of the drive shaft near the coupling to fix the bearing unit.

8. The aircraft engine torque measuring pump transmission of claim 7, wherein the outer diameter of the shaft segment on the drive shaft on which the spacer bushing is mounted is smaller than the outer diameter of the shaft segment on which the bearing is mounted.

9. The aircraft engine torque measurement pump transmission mechanism of claim 7, wherein the bearing is a deep groove ball bearing.

10. The aero-engine torque measurement pump transmission mechanism according to claim 1, wherein the bearing support is in clearance connection with a mounting hole in a casing of the speed reducer.

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