CN214776522U

CN214776522U - Propeller speed regulator

Info

Publication number: CN214776522U
Application number: CN202022712372.0U
Authority: CN
Inventors: 徐丁丁; 郝丽; 陈双双; 张鹤方; 王春慧
Original assignee: AVIC Huiyang Aviation Propeller Co Ltd
Current assignee: AVIC Huiyang Aviation Propeller Co Ltd
Priority date: 2020-11-22
Filing date: 2020-11-22
Publication date: 2021-11-19
Anticipated expiration: 2030-11-22

Abstract

The utility model discloses a propeller speed regulator, which comprises an upper shell component, a lower shell component, a bottom plate, an oil filter component, a speed selection mechanism, a power turbine regulating component, a gear pump, a safety and beta valve component and a reset handle component; the engine oil is connected with a low-pressure oil groove on the bottom plate through an oil filter assembly, and the outlet of the gear pump is divided into two paths which are respectively connected with a high-pressure oil inlet of the beta valve assembly and a high-pressure oil cavity of the safety valve assembly; a low-pressure oil cavity of the safety valve assembly is connected with a low-pressure oil groove; a high-pressure oil outlet of the beta valve assembly is connected with a high-pressure oil inlet of the speed selection mechanism, and a high-pressure oil outlet of the speed selection mechanism is connected with a propeller oil cavity; an oil return cavity of the beta valve assembly is connected with an oil groove II of the speed selection mechanism; an oil return port of the speed selection mechanism is connected with an oil return groove of the engine. The utility model discloses have optional speed, steerable feathering, can realize the adjustable controllable of anti-oar and balanced rotational speed, the screw work efficiency who uses this speed regulator is high, saves a large amount of fuel, and the operational safety reliability is high.

Description

Propeller speed regulator

Technical Field

The utility model relates to a screw speed regulator.

Background

The higher the rotating speed of the propeller is, the greater the generated thrust is, and the greater the thrust is required when the airplane takes off, and the less the thrust is required when the airplane flies in a cruise plane. The existing propeller speed regulators only have one balance rotating speed, and the rotating speed is the same as that of the existing propeller speed regulators when the existing propeller speed regulators are in constant balance rotating speed by balancing the centrifugal force of a balancing weight and the spring force, so that the existing propeller speed regulators cannot be selected, and the existing propeller speed regulators can stably and efficiently complete the takeoff task when the balance rotating speed is set to be higher under the condition of completing the takeoff task, so that an engine is not easily damaged; therefore, a proper balance rotating speed is selected according to the actual condition of the airplane, but no matter how, as long as the balance rotating speed meeting the take-off requirement can be met, a large amount of fuel oil is wasted during the cruise flight, so that the requirement that the propeller speed regulator which can select the speed and can realize the adjustable and controllable balance rotating speed is required to ensure that the thrust of the propeller is high when the airplane takes off and the thrust of the propeller is low when the airplane cruises flight. The flight of the airplane is ensured by adjusting the rotating speed and the blade angle of the propeller, the propeller only has one high-efficiency blade angle, the working efficiency of the propeller is lower when the propeller works in other blade angle states, the blade angle needs to be changed to absorb the power of an engine in order to keep the rotating speed of the propeller at a fixed rotating speed under the condition that the flight working condition is changed, the working efficiency of the propeller is lower, and in order to always maintain the working efficiency of the propeller at a higher efficiency, a speed-selectable controllable propeller speed regulator capable of realizing adjustable and controllable balance rotating speed is urgently needed to be researched so that the blade angle is always kept at the position of the high-efficiency blade angle. The existing propeller speed regulator is not provided with a small-distance limiting mechanism, the propeller is protected at a fixed distance by adopting an end surface tooth meshing mechanism, the end surface tooth meshing mechanism is complex in structure, the size and the weight of the propeller are increased, the use requirements of aircrafts such as airplanes and the like cannot be met, and the research on the propeller speed regulator with the small-distance limiting and fixed-distance protection function is urgently needed. The feathering function of the existing propeller is realized by switching an oil way speed regulator and an oil way in the propeller, a plurality of oil ways are arranged in the speed regulator and the propeller, the oil way structure is very complex, the manufacture is not easy, and the sealing of each oil way is not easy to ensure; the existing speed regulator has no beta manipulation and reverse propeller functions, and the airplane can land and slide by reducing the blade angle of the propeller in a certain range to achieve a certain damping effect, but the effect is very little, the airplane has long landing and sliding distance, a long runway needs to be arranged, land resources are wasted, and the utilization rate of the existing land resources is low. Therefore, a speed regulator which has a simple oil path, can control feathering and can realize beta operation and reverse feathering functions is urgently needed to be researched.

SUMMERY OF THE UTILITY MODEL

The utility model aims at solving the above-mentioned problem that exists among the prior art, provide one kind and have optional speed, steerable feathering, can realize the controllable screw speed regulator that anti-oar and balanced rotational speed are adjustable, the screw work efficiency who uses this speed regulator is high, saves a large amount of fuel, and the work fail safe nature is high, has shortened the runway that slides.

In order to achieve the above object, the technical solution of the present invention is: a propeller speed regulator comprises an upper shell assembly, a lower shell assembly, a bottom plate, an oil filter assembly, a speed selection mechanism arranged in inner holes of the upper shell assembly, the lower shell assembly, the bottom plate and the oil filter assembly, a power turbine regulating assembly arranged in the upper shell assembly, a gear pump, a safety valve assembly, a beta valve assembly and a reset handle assembly connected with a power push-pull rod, wherein the gear pump, the safety valve assembly and the beta valve assembly are arranged in the lower shell assembly; the upper shell assembly is fixed on the upper end surface of the lower shell assembly in a sealing manner; the lower shell assembly is fixed on the upper end surface of the bottom plate in a sealing way;

the speed selection mechanism comprises a speed selection handle, a speed selection stop assembly, a reset torsion spring, a maximum speed stop piece, a feathering stop piece, variable diameter screw shafts, an upper spring seat, a lower spring seat, a spring, a bearing, a centrifugal counterweight assembly, a valve sleeve, a valve core bonnet assembly and an inserting piece, wherein the variable diameter screw shafts, the upper spring seat, the lower spring seat, the spring, the bearing, the centrifugal counterweight assembly, the valve sleeve, the valve core bonnet assembly and the inserting piece are positioned in inner cavities of the upper shell assembly, the lower shell assembly and the bottom plate; one end of the speed selection handle is provided with a spline hole, and the other end of the speed selection handle is provided with a connecting structure with the propeller rod; the upper part of the speed selection stop assembly is sleeved between a spline hole of the speed selection handle and the upper part of the reducing screw shaft, an external spline of the speed selection stop assembly is connected with an internal spline of the speed selection handle, an internal spline of the speed selection stop assembly is connected with an external spline of the upper part of the reducing screw shaft, and a limiting flanging is arranged on the internal spline; the maximum speed stop piece and the feathering stop piece are respectively fixed on two small cylinders on the upper end surface of the upper shell assembly; the outer end of the large cylinder at the upper end of the upper shell component is sleeved with a reset torsion spring of which the upper end is fixed on the speed selection stop component and the lower end is fixed on one small cylinder; the speed-selecting stop assembly limits the flanging to rotate between the maximum speed stop piece and the feathering stop piece; the upper part of the reducing screw shaft is sleeved and connected with a threaded hole formed in a large cylinder at the upper end of the upper shell assembly in a threaded sealing manner, and the thinned part at the middle lower part is assembled in an inner hole of the upper spring seat in an interference manner; the valve core and valve bonnet assembly comprises a valve core and a valve bonnet integrated with the upper end of the valve core, an integrated lower spring seat is arranged on the outer circle of the upper end surface of the valve core, a circle of groove is formed on the inner circle of the lower spring seat, and the inserting piece is arranged in the groove and connected with the inner circle key groove of the lower spring seat; the lower end part of the reducing screw shaft is sleeved in the insert in a micro-clearance manner, the lower end with the thickened diameter is positioned below the insert, and the springs fixed on the upper spring seat and the lower spring seat penetrate through the reducing screw shaft; the valve core of the valve core bonnet assembly is arranged in the valve sleeve, and a bearing with a bottom surface boss is assembled in a gap on the valve core on the lower end surface of the valve bonnet; the centrifugal counterweight component comprising a centrifugal block is positioned in an inner cavity at the upper end of the lower shell component, the lower end of the centrifugal counterweight component is clamped on an excircle at the upper end of the valve sleeve through a spline sleeve, and the hook end of the centrifugal block is abutted on a bottom boss of the bearing; the valve sleeve micro-gap is assembled in the mounting hole of the lower shell component, and the lower end of the valve sleeve micro-gap is provided with a connecting mechanism with an engine; a convex shoulder is arranged on the outer circle of the valve core, and an oil groove I and an oil groove II are arranged on the outer circle of the valve core above and below the convex shoulder; the valve sleeve is provided with a high-pressure oil inlet and a high-pressure oil outlet which are communicated with the oil groove I and an oil return port I which is communicated with the oil groove II; when the propeller normally works at the selected balance rotating speed, the convex shoulder blocks the high-pressure oil outlet on the valve sleeve; when the rotating speed of the propeller is smaller than the selected balance rotating speed, the convex shoulder is arranged at the lower end of the high-pressure oil outlet, and the high-pressure oil outlet is communicated with the high-pressure oil inlet; when the rotating speed of the propeller is higher than the selected balance rotating speed, the convex shoulder is arranged at the upper end of the high-pressure oil outlet, and the high-pressure oil outlet is communicated with the oil return opening I;

one end of the gear pump is arranged in the low-pressure oil groove of the bottom plate and comprises a driving gear, a driven gear, a driving shaft and a driven shaft; the driving shaft is borrowed from the excircle of the middle part of the valve sleeve, and the driving gear is integrally formed on the excircle of the middle part of the valve sleeve; a driven shaft is fixedly arranged in the lower shell assembly, and a driven gear is rotatably fixed on the driven shaft through a bearing;

the safety valve assembly comprises a cap I with an n-shaped section, a spring shaft seat, a pressure spring, a safety valve and a lining I; the bushing I is fixed in a threaded mounting hole formed in the lower shell assembly through threads; the cap I is fixed at the upper end of an inner hole of the bush I through threads, the spring shaft seat is arranged in the inner hole of the bush I, the upper end of the spring shaft seat abuts against the inner hole of the cap I, and the safety valve sleeve is clamped in the reducing inner hole of the bush through a boss on the outer circle of the safety valve sleeve; the pressure spring is sleeved on the spring shaft seat and the safety valve and compressed between the spring shaft seat and the boss of the safety valve; an inner hole of the bushing I at the lower end of the safety valve is a high-pressure oil cavity, a low-pressure oil cavity is also arranged between the peripheral wall of the bushing I and the lower shell assembly, and oil holes I and II which are communicated with the low-pressure oil cavity are formed in the peripheral wall of the bushing I; the oil hole II is also communicated with an inner hole of the bush where the pressure spring is located; the distance between the spring shaft seat and the safety valve is larger than the distance between the lower end face of the safety valve and the lower end wall of the oil hole I; when the pressure of high-pressure oil in the high-pressure oil cavity is greater than the pressure of the pressure spring, the high-pressure oil flows into the safety valve assembly from the high-pressure oil cavity, the safety valve moves upwards, the oil hole I is communicated with the high-pressure oil cavity, part of high-pressure oil at the high-pressure oil outlet of the gear pump of the lower shell assembly flows into the low-pressure oil cavity from the oil hole I until the pressure of the high-pressure oil in the high-pressure oil cavity is balanced with the spring force of the pressure spring, the safety valve moves downwards, the oil hole I is not communicated with the high-pressure oil cavity, and the pressure of the high-pressure oil is stable at the pressure capable of keeping the speed regulator to normally work. The oil hole II communicates an inner hole of the bush where the pressure spring is located with the low-pressure oil cavity, low-pressure oil is used for rust prevention of parts such as the spring and the like besides pressure balance inside and outside the inner hole, and the service life of the parts is prolonged;

the beta valve assembly comprises a bushing II, a valve, a return spring, a U-shaped fork with a step and a central hole and a cap II; one end of the valve is provided with a small-distance end plug, and the other end of the valve is fixed with a U-shaped fork; the bushing II is press-mounted in the round mounting hole extending out of the lower shell assembly in an interference manner, an adjusting washer with the same diameter as the round mounting hole extending out of the lower shell assembly is press-mounted at the port through the cap II, and the relative position of the small-distance end plug of the valve and the high-pressure oil outlet of the bushing II is adjusted through the adjusting washer; one end of the valve with a small-distance end plug is assembled in the bushing II in a micro-gap mode, and the position between the valve and the bushing II is sealed by a sealing ring at the end part of the bushing II; the reset spring which is sleeved on the valve and fixed in the U-shaped fork groove is pressed on the adjusting washer; the cap II is provided with a reducing inner hole with the diameter matched with the excircle of the U-shaped fork, the excircle of the step of the U-shaped fork, the adjusting washer and the excircle of the circular mounting opening, the reducing inner hole is sleeved on the excircle of the U-shaped fork, the adjusting washer and the excircle of the circular mounting opening and is fixed on the circular mounting opening, and the length of the inner hole part matched with the excircle of the step of the U-shaped fork is the maximum range of the movement of the valve; an oil groove III is formed in the valve, a high-pressure oil outlet and a high-pressure oil inlet which are communicated with the oil groove III are formed in the bushing II, and an inner cavity of the bushing II at the tail end of the small-distance end plug is an oil return cavity; under the normal working state, the high-pressure oil outlet is communicated with the oil groove III, when the valve is limited at a small distance, the valve moves to the outer end of the circular mounting port in place, and the small-distance end plug just seals the high-pressure oil outlet;

the power turbine adjusting assembly comprises a support rod shifting fork assembly, a baffle plate support assembly, a blocking cover and a nozzle which are arranged in the upper shell assembly; the support rod and shifting fork assembly comprises a balancing weight, springs I and II, a shifting fork, a small wheel and a support rod; one end of the shifting fork is fixed with a balancing weight, the other end of the shifting fork is a U-shaped fork matched with a shell cavity for installing the valve core and valve cap assembly, and two ends of the U-shaped fork are respectively fixed with a pin; when the valve core and bonnet assembly is used, the lower end of the pin is abutted to the upper end wall of the valve core and bonnet assembly valve bonnet; one end of the shifting fork close to the balancing weight penetrates through a through hole of the supporting rod, and the shifting fork is hinged on the supporting rod through a needle bearing which is assembled in the inner hole in an interference manner and a pin of which two ends are assembled on two opposite walls of the through hole of the supporting rod in an interference manner; the lower end of a shifting fork arranged in the through hole of the support rod is U-shaped, a small wheel is arranged in a U-shaped groove of the shifting fork, and a pin which is assembled in an inner hole of the small wheel in a clearance mode is fixed on the U-shaped end wall; a spring II is fixed on the upper end face of the supporting rod, a U-shaped groove connected with the reset handle assembly is formed in the lower end face of the supporting rod, and a spring I is fixed on the upper end face of the shifting fork; the nozzle is fixed in a mounting hole extending out of the side wall of the lower end of the upper shell assembly, and the outer end of the nozzle is provided with a plug cover; the baffle support assembly comprises a baffle and a spring III fixed on the side wall of the baffle, one end of the baffle is rotatably arranged in an installation shell extending out of the side wall of the lower end of the upper shell assembly, the other end of the baffle is connected with the lower end of the balancing weight in a propping manner, in a normal state, one side wall of the baffle seals the nozzle, and the small wheel is connected with the side wall of the other end of the baffle in a propping manner; the U-shaped groove at the lower end of the supporting rod is inserted on the reset handle component; when the valve core valve cap rises or the reset handle assembly acts, the balancing weight presses the baffle of the baffle support assembly, and the nozzle is opened for air injection;

the oil coming from the engine is connected with a low-pressure oil tank arranged on a bottom plate through an oil filter assembly, the outlet of a gear pump with one end arranged in the low-pressure oil tank is divided into two paths through an oil inlet hole in a lower shell assembly, one path is connected with a high-pressure oil inlet of a beta valve assembly, and the other path is connected with a high-pressure oil cavity of a safety valve assembly; the low-pressure oil cavity of the safety valve assembly is connected with the low-pressure oil groove through an oil return oil way of the lower shell assembly; a high-pressure oil outlet of the beta valve assembly is connected with a high-pressure oil inlet of the speed selection mechanism through a high-pressure oil inlet hole in the lower shell assembly, and a high-pressure oil outlet of the speed selection mechanism is connected with a propeller oil cavity; an oil return cavity of the beta valve assembly is connected with an oil groove II of the speed selection mechanism through an oil return oil way of the lower shell assembly; an oil return port of the speed selection mechanism is connected with an oil return groove of the engine.

Further preferably, the peripheral wall of one end of the speed selecting handle of the speed selecting mechanism, which is provided with the internal spline hole, is disconnected, and a through hole and a threaded hole are formed in the two end walls of the disconnected peripheral wall and are fixed together by a spherical cylindrical head screw I with a hole and a light spring washer I. This structure is easy to mount and dismount.

Further preferably, the peripheral wall of the speed selection stop assembly of the speed selection mechanism is disconnected, a through hole and a threaded hole are formed in two end walls of the disconnected peripheral wall, and the through hole and the threaded hole are fixed together through a spherical cylindrical head screw II with a hole and a light spring washer II. This structure is easy to mount and dismount.

Further preferably, the centrifugal counterweight component of the speed selection mechanism comprises a support, two centrifugal blocks and a spiral retainer ring which are correspondingly distributed; the lower end of the support is clamped on the excircle of the upper end part of the valve sleeve through a spline sleeve; two centrifugal blocks are assembled on the support through a shaft and a bearing clearance respectively, a circle of spiral retainer ring is clamped and fixed on the outer wall of the upper end of the support, and two ends of the shaft are abutted on the inner end wall of the spiral retainer ring; the hook end which is abutted on the boss at the bottom surface of the bearing is provided with an arc surface. The existence of spiral retaining ring makes the axle be difficult for deviating from, and structural reliability is high, and the circular arc face has reduced the friction of the bottom surface boss of bearing, has increased life.

Further preferably, the distance between the spring shaft seat of the safety valve assembly and the safety valve is 2.8 mm. So as to ensure that the pressure of the pressure spring meets the use requirement.

Further preferably, the upper end of the seat of the spring shaft seat of the safety valve assembly abuts against the inner hole of the cap I through a gasket I, and the lower end of the seat of the spring shaft seat of the safety valve assembly is pressed on the pressure spring through a gasket II. The distance between the spring shaft seat and the safety valve can be guaranteed by adjusting the thickness of the gasket I, the pressure of the pressure spring can be adjusted by adjusting the thickness of the gasket II, and the structure is easy to install and adjust, so that the pressure spring meets the parameter requirement.

Further preferably, the bushing I of the safety valve assembly is fixed in a threaded mounting hole formed in the lower shell assembly through a washer thread; the cap I is fixed at the upper end of the inner hole of the bushing I through another washer thread between the upper end wall of the bushing I and the lower end wall of the cap I. The connection reliability is high, and the falling is not easy.

Further preferably, a plastic gasket embedded on the inner wall of the port of the cap is arranged between the cap of the beta valve assembly and the U-shaped fork for sealing and dust prevention; and another sealing ring is pressed and mounted among the bushing, the circular mounting opening and the adjusting gasket.

Further preferably, the structure that one end of the baffle plate support assembly of the power turbine adjusting assembly is rotatably installed in the installation shell protruding out of the side wall of the lower end of the upper shell assembly is as follows: the bearing is assembled at the root of the supporting shaft of the supporting seat in a clearance mode, the baffle is assembled on the bearing in a clearance mode, and the supporting shaft is sleeved with a spring IV through a gasket; and integrally pressing the support seat, the bearing and the spring IV into the inner hole of the mounting shell.

The utility model discloses five operating condition as follows have:

a) selection of balance rotating speed and feathering:

through the propeller shaft manipulation on the aircraft the utility model discloses an on speed selection handle, change reducing screw shaft position and then change the pressure volume of spring, can make the screw select to work under the balanced rotational speed of difference, the speed regulator is driven rotatoryly by the drive mechanism of engine, at this moment, the elasticity of spring and the centrifugal force of the rotatory production of centrifugal piece of centrifugal counterweight assembly exert the axial component on case valve cap subassembly and reach the balance, the shoulder of case just plugs up the lubricating oil circuit that leads to in the screw intracavity, makes it work under a balanced rotational speed.

When the gear selection handle moves to the feathering position, the valve core valve cap assembly is lifted, the high-pressure oil outlet is communicated with the oil return port, high-pressure oil in the propeller cavity flows into the low-pressure oil tank, pressure acting on the propeller servo piston is reduced, and at the moment, the propeller servo piston moves to the feathering position under the action of feathering spring force and blade counterweight centrifugal force.

b) Overspeed cycling and protection:

under the condition of overspeed, a centrifugal block of a centrifugal counterweight component of the speed regulator is thrown upwards, the valve core bonnet component is lifted by overcoming the elasticity of a spring, a high-pressure oil outlet is communicated with an oil return opening, high-pressure oil in a propeller cavity is shunted to a low-pressure oil groove, the propeller pitch is increased, the load is increased, the rotating speed of the propeller is reduced until the valve core bonnet component descends, the axial component force of the elasticity of the spring and the centrifugal force is balanced, the rotating speed returns to the selected balanced rotating speed, and a convex shoulder of the valve core blocks a lubricating oil circuit leading to the propeller cavity again.

When the speed regulator exceeds the speed limit to a certain value, the power turbine regulating assembly acts, the valve core and valve bonnet assembly is lifted to a certain degree to push the shifting fork to rotate, the balancing weight presses the baffle of the baffle support assembly to open the nozzle, and a signal is provided for the fuel regulator by reducing the pressure on one side of the signal conversion device, so that the fuel supply quantity of the engine is reduced, the power of the engine is reduced, the rotating speed of the propeller is reduced to a required range, and the flying rotation is prevented.

c) And (3) underspeed circulation:

under the condition of underspeed, the spring elasticity overcomes the axial component force of the centrifugal block of the centrifugal counterweight component, so that the valve core bonnet component descends, the high-pressure oil outlet is communicated with the high-pressure oil inlet, high-pressure oil enters the propeller cavity, the propeller pitch is reduced, the load is reduced, the rotating speed of the propeller is increased until the valve core bonnet component ascends, the spring elasticity and the axial component force of the centrifugal force are balanced, the rotating speed returns to the selected balanced rotating speed, and the convex shoulder of the valve core blocks the oil path leading to the propeller cavity again.

d) β -steering and counter-paddles:

when the reverse propeller is operated, the rear pull power rod enables the rotating speed of the propeller to be lower than the selected rotating speed, the speed regulator can enable the propeller to move towards a small distance direction, and when the propeller enters a beta range, a required blade angle can be selected through the power rod, and the specific process is as follows: rear pull power rod → reverse paddle rod action → reset handle action → strut move down → counterweight press baffle open nozzle → P_{Burning device}Air passage deflation → engine power reduction → under-speed condition occurrence → valve core valve cap reduction → high-pressure oil enters a propeller cavity → the propeller moves towards the reverse propeller direction, the low-distance stop ring drives the beta valve to move forwards as a result of the movement, the small-distance end plug closes an oil passage leading to the propeller cavity, so that the beta valve automatically keeps at a certain propeller blade angle, the power rod is pulled backwards continuously, the beta valve moves backwards again, the small-distance end plug leaves the oil passage leading to the propeller cavity, the oil passage is communicated, the high-pressure oil enters the propeller cavity again to move towards the reverse propeller direction, the oil passage is closed again as a result of the movement, and the process repeatedly occurs until full reverse propeller is realized.

e) Small-distance limiting and distance protecting:

when the engine slows down, high-pressure oil pumped by the speed regulator enters a propeller cavity, the propeller moves from feathering to a small distance direction, when the blade angle of the propeller is reduced to an alpha angle, the propeller continues to be in a small distance, the beta valve moves under the elastic force action of the reverse paddle lever and the return spring, and the small distance end on the beta valve closes the high-pressure oil outlet, so that the blade angle of the propeller is automatically kept at a certain blade angle, the propeller is spaced, and the protection function is achieved.

The utility model has the advantages and beneficial effect: the structure is relatively simple, the assembly and disassembly are convenient, and the adjustable and controllable functions of speed selection, forward propeller control, reverse propeller control and balanced rotating speed control are realized; the propeller using the speed regulator has high working efficiency, saves a large amount of fuel oil, has high working safety and reliability, and shortens a taxiway. And the speed regulator has an overspeed protection function, so that the airplane can fly more safely and reliably.

Drawings

Fig. 1 is a schematic structural view of the present invention;

fig. 2 is a top view of the present invention;

FIG. 3 is a top view of the centrifugal weight assembly of the speed selection mechanism of the present invention;

FIG. 4 is a schematic view of the installation structure of the safety valve assembly of the present invention;

FIG. 5 is a schematic structural view of a safety valve assembly according to the present invention;

fig. 6 is a schematic view of an installation structure of the middle beta valve assembly of the present invention;

FIG. 7 is a schematic structural view of a valve in the middle beta valve assembly of the present invention;

FIG. 8 is a top view of the upper housing assembly, power turbine adjustment assembly and speed selection mechanism of the present invention;

FIG. 9 is a cross-sectional view AA in FIG. 8;

FIG. 10 is a schematic structural view of a strut fork assembly of the medium power turbine adjustment assembly of the present invention;

FIG. 11 is a front view of a baffle bracket assembly of the medium power turbine adjustment assembly of the present invention;

FIG. 12 is a bottom view of a baffle bracket assembly of the medium power turbine adjustment assembly of the present invention;

FIG. 13 is a view in cross section BB of FIG. 8;

FIG. 14 is a diagram showing the relative positions of a spool boss of the speed selection mechanism and an oil passage hole leading to a propeller chamber at overspeed;

FIG. 15 is a diagram showing the relative position of the spool boss of the underspeed gear selection mechanism and the oil passage hole leading to the propeller chamber;

fig. 16 is a relative position relationship diagram of a spool boss of the speed selection mechanism and an oil passage hole leading to the propeller chamber at the time of balancing the rotational speed.

Detailed Description

The invention is further described with reference to the accompanying drawings and specific embodiments.

As shown in fig. 1 to 16, the present embodiment includes an upper casing assembly 1, a lower casing assembly 9, a bottom plate 16, an oil filter assembly, a speed selection mechanism installed in the inner holes of the upper and lower casing assemblies 1, 9, the bottom plate 16 and the oil filter assembly, a power turbine adjustment assembly installed in the upper casing assembly 1, a gear pump 97 installed in the lower casing assembly 9, a safety valve assembly 96, a beta valve assembly 69 and a reset handle assembly 70 connected to a power push-pull rod. The upper shell assembly 1 is fixed on the upper end surface of the lower shell assembly 9 in a sealing mode through a sealing gasket. The lower shell component 9 is sealed and fixed on the upper end surface of the bottom plate 16 by a sealing ring.

The speed selection mechanism comprises a speed selection handle 3, a speed selection stop assembly 5, a reset torsion spring 2, a maximum speed stop piece 14, a feathering stop piece 15, a variable diameter screw shaft 4, upper and

lower spring seats

13 and 17, a spring 6, a bearing 7, a centrifugal counterweight assembly 8, a valve sleeve 10, a valve core bonnet assembly 11 and an inserting piece 12, wherein the variable diameter screw shaft is positioned in inner cavities of an upper shell assembly 1 and a lower shell assembly 9 and a bottom plate 16. One end of the speed-selecting handle 3 is provided with a splined hole, and the other end is provided with a connecting structure with the propeller rod. Preferably, the speed-selecting handle 3 has a broken peripheral wall at one end with an internal spline hole, a through hole and a threaded hole are arranged on two end walls of the broken peripheral wall, and the through hole and the threaded hole are fixed together by a spherical cylindrical head screw I28 with a hole and a light spring washer I27. The upper part of the speed-selecting stop component 5 is sleeved between the splined hole of the speed-selecting handle 3 and the upper part of the reducing screw shaft 4, the external spline of the speed-selecting stop component is connected with the internal spline of the speed-selecting handle 5, the internal spline of the speed-selecting stop component is connected with the external spline of the upper part of the reducing screw shaft 4, and the speed-selecting stop component is provided with a limiting flanging. Preferably, the peripheral wall of the speed-selecting stop assembly 5 is broken, and a through hole and a threaded hole are formed in two end walls of the broken peripheral wall, and the two are fixed together by a spherical cap screw II 29 with a hole and a light spring washer II 30. The maximum speed stop 14 and the feathering stop 15 are fixed to two small cylinders, respectively, on the upper end surface of the upper housing assembly 1. The outer end of the big cylinder at the upper end of the upper shell component 1 is sleeved with a reset torsion spring 2, the upper end of which is fixed on the speed-selecting stop component 5, and the lower end of which is fixed on one of the small cylinders. The speed stop assembly 5 limits the turn-up from rotating between the maximum speed stop 14 and the feathering stop 15. The upper part of the reducing screw shaft 4 is sleeved and hermetically connected in a threaded hole formed in a large cylinder at the upper end of the upper shell assembly 1 by adopting a trapezoidal thread, and the thinning part of the middle lower part is in interference fit in an inner hole of the upper spring seat 13. The valve core and bonnet assembly 11 comprises a valve core 19 and a bonnet 18 integrated with the upper end of the valve core 19, an integrated lower spring seat 17 is arranged on the outer circle of the upper end face of the valve core 19, a circle of groove is formed on the inner circle of the lower spring seat 17, and the inserting piece 12 is arranged in the groove and connected with an inner circular key groove of the lower spring seat 17. The lower end of the valve housing 10 is provided with a spline connected with an output shaft of the engine. The lower end part of the reducing screw shaft 4 is sleeved in the insert 12 in a micro-clearance way, and the lower end with the thickened diameter is positioned below the insert 12. The spring 6 fixed on the upper and

lower spring seats

13, 17 is threaded on the reducing screw shaft 4. The valve core 19 of the valve core bonnet assembly is arranged in the valve sleeve 10, and the bearing 7 with a bottom surface boss is arranged on the valve core 19 on the lower end surface of the valve bonnet 18 in a clearance mode. The centrifugal counterweight component 8 comprising a centrifugal block is positioned in the inner cavity at the upper end of the lower shell component 9, the lower end of the centrifugal counterweight component is clamped on the excircle at the upper end of the valve sleeve 10 through a spline sleeve, and the hook end of the centrifugal block is abutted on the bottom boss of the bearing 7. Preferably, the centrifugal weight assembly comprises a support 32, two centrifugal blocks 33 and a spiral retainer ring 31 which are distributed correspondingly; the lower end of the support 32 is clamped on the excircle of the upper end part of the valve sleeve 10 through a spline sleeve; two centrifugal blocks 33 are respectively assembled on a support 32 through a shaft 35, a bearing 36 and a gasket 34 in a clearance mode, a circle of spiral retainer ring 31 is fixedly clamped on the outer wall of the upper end of the support 32, and two ends of the shaft 35 are abutted to the inner end wall of the spiral retainer ring 31; the end surface of the hook end which is abutted on the boss at the bottom surface of the bearing 7 is provided with an arc surface. The valve sleeve 10 is micro-gap fitted in the mounting hole of the lower housing assembly 9, and its lower end is splined to the engine. A convex shoulder 20 is arranged on the outer circle of the valve core 19, and an oil groove I22 and an oil groove II 24 are arranged on the outer circle of the valve core 19 above and below the convex shoulder 20. The valve housing 10 is provided with a high pressure oil inlet 26 and a high pressure oil outlet 23 which are communicated with the oil groove I22, and an oil return port I25 which is communicated with the oil groove II 24. When the propeller normally works at the selected balance rotating speed, the convex shoulder 20 blocks the high-pressure oil outlet 23 on the valve sleeve 10; when the rotating speed of the propeller is smaller than the selected balance rotating speed, the convex shoulder 20 is arranged at the lower end of the high-pressure oil outlet 23, the high-pressure oil outlet 23 is communicated with the high-pressure oil inlet 26, high-pressure oil is fed into the propeller, the rotating speed is increased, and the convex shoulder 20 blocks the high-pressure oil outlet 23 on the valve sleeve 10 until the propeller normally works at the selected balance rotating speed. When the rotating speed of the propeller is higher than the selected balance rotating speed, the convex shoulder 20 is arranged at the upper end of the high-pressure oil outlet 23, the high-pressure oil outlet 23 is communicated with the oil return port I25, the propeller returns oil, the rotating speed is reduced, and the convex shoulder 20 blocks the high-pressure oil outlet 23 on the valve sleeve 10 until the selected balance rotating speed is reached to normally work. 39 is a boss on the exterior of the upper end wall of the bonnet 18.

One end of the gear pump 97 is disposed in a low-pressure oil groove in the bottom plate 16, and includes a driving gear 38, a driven gear 71, a driving shaft and a driven shaft 72. The driving shaft is driven by the middle excircle of the valve sleeve 10, and the driving gear 38 is integrally formed on the middle excircle of the valve sleeve 10. A driven shaft 72 is fixedly installed in the lower housing assembly 9, and the driven gear 71 is rotatably fixed to the driven shaft 72 through a bearing. 37 is a protective cover installed during transportation.

The safety valve assembly 96 comprises a cap I41 with an n-shaped section, a spring shaft seat 44, a pressure spring 45, a safety valve 46 and a bushing I47. Bushing I47 is threadably secured within a threaded mounting hole formed in lower housing assembly 9 by a washer 48. The cap I41 is screwed on the upper end of the inner hole of the bush I47 through another gasket 40 between the upper end wall of the bush I47 and the lower end wall of the cap I41. The spring shaft seat 44 is arranged in the inner hole of the lining I47, the upper end of the spring shaft seat abuts against the inner hole of the cap I41, and the safety valve 46 is sleeved and clamped in the reducing inner hole of the lining I47 through a boss 52 on the outer circle of the safety valve. Preferably, the upper end of the spring shaft seat 44 is abutted against the inner hole of the cap I41 through a gasket I42, and the lower end is pressed on the pressure spring 43 through a gasket II 45. The compression spring 45 is fitted over the spring axle seat 44 and the safety shutter 46 and compressed between the spring axle seat 44 and the boss 52 of the safety shutter 46. The bushing i 47 has a high-pressure oil chamber 49 in an inner hole at the lower end of the relief valve 46, and a low-pressure oil chamber 51 is provided between the peripheral wall thereof and the lower housing unit 9, and oil holes i 50 and ii 53 both communicating with the low-pressure oil chamber 51 are provided in the peripheral wall thereof. The oil hole II 53 is also communicated with an inner hole of the bushing I47 where the pressure spring 45 is located. The distance between the spring shaft seat 44 and the safety valve 46 is larger than the distance between the lower end surface of the safety valve 46 and the lower end wall of the oil hole I50; preferably, the distance between the spring axle seat 44 and the safety shutter 46 is 2.8 mm. When the pressure of the high-pressure oil in the high-pressure oil chamber 49 is greater than the pressure of the pressure spring 45, the high-pressure oil flows into the safety valve assembly from the high-pressure oil chamber 49, the safety valve 46 moves upwards, the oil hole I50 is communicated with the high-pressure oil chamber 49, part of the high-pressure oil at the high-pressure oil outlet of the gear pump in the lower shell assembly 9 flows into the low-pressure oil chamber 51 from the oil hole I50 until the pressure of the high-pressure oil in the high-pressure oil chamber 49 is balanced with the spring force of the pressure spring 45, the safety valve 46 moves downwards, the oil hole I50 is not communicated with the high-pressure oil chamber 49, and the pressure of the high-pressure oil is stabilized at the pressure capable of keeping the speed regulator to normally work. The oil hole II 53 communicates the inner hole of the bush I47 where the pressure spring 45 is located with the low-pressure oil cavity 51, and low-pressure oil is used for rust prevention of parts such as the pressure spring and the like besides keeping pressure balance inside and outside the inner hole, so that the service life of the parts is prolonged.

The beta valve assembly 69 comprises a bushing II 58, a valve 59, a return spring 61, a U-shaped fork 60 with steps and a central hole and a cap II 64. One end of the valve 59 is provided with a small-distance end plug 66, and the other end is fixed with a U-shaped fork 60. The bushing II 58 is pressed in a round mounting hole 65 extending out of the lower shell assembly 9 in an interference fit mode, and an adjusting washer 63 with the same diameter as the round mounting hole 65 extending out of the lower shell assembly 9 is pressed in the port through a cap II 64; the relative position of the valve small distance end plug 66 and the high pressure oil outlet 55 of the bushing II is adjusted through the adjusting washer 63. The valve 59 is assembled in the bush II 58 with a small clearance at one end with a small distance end plug 66, and the sealing ring is used for sealing between the valve 59 and the bush II 58 at the end position of the bush II 58. And another sealing ring is pressed and installed among the bushing II 58, the circular mounting opening 65 and the adjusting gasket 63. A return spring 61, which is fitted over the shutter 59 and fixed in a groove of the clevis 60, is pressed against the adjusting washer 63. The cap II 64 is provided with a reducing inner hole with the diameter matched with the excircle of the U-shaped fork 60, the excircle 67 of the step of the U-shaped fork, the adjusting washer 63 and the excircle of the circular mounting hole 65, the reducing inner hole is sleeved on the excircle of the U-shaped fork 60, the adjusting washer 63 and the excircle of the circular mounting hole 65 and is fixed on the circular mounting hole 65 in a threaded manner, and the length of the inner hole part matched with the excircle 67 of the step of the U-shaped fork is the maximum range of the movement of the valve 59. Preferably, a plastic gasket 62 embedded on the inner wall of the port of the cap II 64 is arranged between the cap II 64 and the U-shaped fork 60 for sealing and preventing dust. The valve 59 is provided with an oil groove III 56, the bushing II 58 is provided with a high-pressure oil outlet 55 and a high-pressure oil inlet 57 which are communicated with the oil groove III 56, and the inner cavity of the bushing II 58 at the tail end of the small-distance end plug 66 is an oil return cavity 54. Under the normal operating condition, high-pressure oil outlet 55 is communicated with oil groove III 56, and when the small distance is limited, valve 59 moves to the outer end of circular mounting opening 65 to the right position, and small distance end plug 66 just seals high-pressure oil outlet 55. When the speed regulator is used, the oil return cavity 54 is directly communicated with an oil return hole 68 in the lower shell assembly 9, the high-pressure oil outlet 55 and the high-pressure oil inlet 57 are respectively connected with the high-pressure oil inlet 26 of the speed regulator speed selection mechanism and the high-pressure oil outlet of the gear pump through a high-pressure oil hole in the lower shell assembly 9, the outer end of the U-shaped fork 60 is connected with a reverse paddle lever, and the reverse paddle lever is connected with the power rod and the propeller.

The power turbine adjustment assembly includes a strut fork assembly, a flapper seat assembly, a blanking cap 75 and a nozzle 78 mounted within the upper housing assembly 1. The support rod shifting fork assembly comprises a balancing weight 89, springs I92 and II 91, a shifting fork 93, a small wheel 86 and a support rod 84. One end of a shifting fork 93 is fixed with a balancing weight 89 through an elastic cylindrical pin 88, the other end of the shifting fork is a U-shaped fork matched with a cavity of an upper shell component 1 for installing a valve core and valve cap component, and two ends of the U-shaped fork are respectively fixed with a pin 94; in use, the lower end of the pin 94 abuts against the boss 39 on the outside of the upper end wall of the bonnet of the cartridge bonnet assembly. One end of the fork 93 close to the weight 89 is inserted into a through hole of the rod 84, and it is hinged to the rod 84 by a needle bearing 87 which is interference fitted into the through hole and a pin 90 whose two ends are interference fitted on two opposite walls of the through hole of the rod 84. The lower end of a shifting fork 93 arranged in the through hole of the support rod 84 is U-shaped, a small wheel 86 is arranged in the U-shaped groove of the shifting fork 93, and a pin 85 which is assembled in the inner hole of the small wheel at intervals is fixed on the U-shaped end wall. A spring II 91 is fixed on the upper end face of the supporting rod 84, a U-shaped groove 95 connected with a reset handle assembly is formed in the lower end face of the supporting rod, and a spring I92 is fixed on the upper end face of the shifting fork 93. The nozzle 78 is fixed in a mounting hole projecting from the lower end side wall of the upper housing assembly 1, and a cap 75 is provided at the outer end of the nozzle 78. The baffle support assembly comprises a baffle 79 and a spring III 77 fixed on the side wall of the baffle, one end of the baffle 79 is rotatably arranged in an installation shell extending out of the side wall of the lower end of the upper shell assembly 1, the other end of the baffle is connected to the lower end of a balancing weight 89 in a propping mode, a side wall of the baffle 79 is closed to form a nozzle 78 in a normal state, and a small wheel 86 is connected to the side wall of the other end of the baffle 79 in a propping mode. The U-shaped slot at the lower end of the strut 84 is inserted into the reset handle assembly. When the valve core valve cap rises, the balancing weight 89 presses the baffle 79 of the baffle support assembly downwards, and the nozzle 78 is opened to spray air. Preferably, the structure that one end of the baffle 79 of the baffle seat assembly is rotatably installed in the installation shell protruding from the side wall of the lower end of the upper shell assembly 1 is as follows: the bearing 81 is assembled at the root of the supporting shaft of the supporting seat 80 in a clearance mode, the baffle 79 is assembled on the bearing 81 in a clearance mode, and the supporting shaft is sleeved with a spring IV 83 through a gasket 82. And integrally pressing the support seat, the bearing 81 and the spring IV 83 in the inner hole of the mounting shell. Both 74 and 76 are sealing rings.

The oil coming from the engine is connected with a low-pressure oil tank arranged on the bottom plate 16 through an oil filter assembly, the outlet of a gear pump with one end arranged in the low-pressure oil tank is divided into two paths through an oil inlet hole in the lower shell assembly 9, one path is connected with a high-pressure oil inlet 57 of the beta valve assembly 69, and the other path is connected with a high-pressure oil cavity 49 of the safety valve assembly 96. The low-pressure oil chamber 51 of the safety valve assembly 96 is connected to the low-pressure oil tank through an oil return passage of the lower housing assembly 9. The high-pressure oil outlet 55 of the beta valve assembly 69 is connected with the high-pressure oil inlet 26 of the speed selection mechanism through the high-pressure oil inlet hole 21 in the lower shell assembly 9, and the high-pressure oil outlet 23 of the speed selection mechanism is connected with the propeller oil cavity. The oil return cavity 54 of the beta valve assembly 69 is connected with the oil groove II 24 of the speed selection mechanism through an oil return passage 68 of the lower shell assembly 9. The oil return port 25 of the speed selection mechanism is connected with an oil return groove of the engine.

Naturally, the invention also relates to other embodiments, and those skilled in the art can make corresponding changes and modifications according to the invention without departing from the spirit and substance of the invention, and these corresponding changes and modifications should be considered as improvements in the equivalent technology, and fall within the scope of protection of the claims of the invention.

Claims

1. A propeller governor characterized by: the device comprises an upper shell assembly, a lower shell assembly, a bottom plate, an oil filter assembly, a speed selection mechanism, a power turbine adjusting assembly, a gear pump, a safety valve assembly, a beta valve assembly and a reset handle assembly, wherein the speed selection mechanism is arranged in inner holes of the upper shell assembly, the lower shell assembly, the bottom plate and the oil filter assembly; the upper shell assembly is fixed on the upper end surface of the lower shell assembly in a sealing manner; the lower shell assembly is fixed on the upper end surface of the bottom plate in a sealing way;

the safety valve assembly comprises a cap I with an n-shaped section, a spring shaft seat, a pressure spring, a safety valve and a lining I; the bushing I is fixed in a threaded mounting hole formed in the lower shell assembly through threads; the cap I is fixed at the upper end of an inner hole of the bush I through threads, the spring shaft seat is arranged in the inner hole of the bush I, the upper end of the spring shaft seat abuts against the inner hole of the cap I, and the safety valve sleeve is clamped in the reducing inner hole of the bush through a boss on the outer circle of the safety valve sleeve; the pressure spring is sleeved on the spring shaft seat and the safety valve and compressed between the spring shaft seat and the boss of the safety valve; an inner hole of the bushing I at the lower end of the safety valve is a high-pressure oil cavity, a low-pressure oil cavity is also arranged between the peripheral wall of the bushing I and the lower shell assembly, and oil holes I and II which are communicated with the low-pressure oil cavity are formed in the peripheral wall of the bushing I; the oil hole II is also communicated with an inner hole of the bush where the pressure spring is located; the distance between the spring shaft seat and the safety valve is larger than the distance between the lower end face of the safety valve and the lower end wall of the oil hole I; when the pressure of high-pressure oil in the high-pressure oil cavity is greater than the pressure of the pressure spring, the high-pressure oil flows into the safety valve assembly from the high-pressure oil cavity, the safety valve moves upwards, the oil hole I is communicated with the high-pressure oil cavity, and the oil hole I is not communicated with the high-pressure oil cavity when the pressure of the high-pressure oil in the high-pressure oil cavity is balanced with the spring force of the pressure spring;

2. The propeller governor of claim 1, wherein: the speed selection handle of the speed selection mechanism is characterized in that the peripheral wall of one end, provided with an internal spline hole, of the speed selection handle is disconnected, a through hole and a threaded hole are formed in two end walls of the disconnected peripheral wall, and the through hole and the threaded hole are fixed together through a spherical cylindrical head screw I with a hole and a light spring washer I.

3. The propeller governor of claim 2, wherein: the peripheral wall of the speed selection stop assembly of the speed selection mechanism is disconnected, a through hole and a threaded hole are formed in two end walls of the disconnected peripheral wall, and the through hole and the threaded hole are fixed together through a spherical cylindrical head screw II with a hole and a light spring washer II.

4. The propeller governor of claim 3, wherein: the centrifugal counterweight component of the speed selection mechanism comprises a support, two centrifugal blocks and a spiral retainer ring which are correspondingly distributed; the lower end of the support is clamped on the excircle of the upper end part of the valve sleeve through a spline sleeve; two centrifugal blocks are assembled on the support through a shaft and a bearing clearance respectively, a circle of spiral retainer ring is clamped and fixed on the outer wall of the upper end of the support, and two ends of the shaft are abutted on the inner end wall of the spiral retainer ring; the hook end which is abutted on the boss at the bottom surface of the bearing is provided with an arc surface.

5. The propeller governor of claim 4, wherein: the distance between the spring shaft seat of the safety valve assembly and the safety valve is 2.8 mm.

6. The propeller governor of claim 5, wherein: the upper end of the seat of the spring shaft seat of the safety valve assembly abuts against the inner hole of the cap I through the gasket I, and the lower end of the seat of the spring shaft seat of the safety valve assembly is pressed on the pressure spring through the gasket II.

7. The propeller governor of claim 6, wherein: the bushing I of the safety valve assembly is fixed in a threaded mounting hole formed in the lower shell assembly through a washer thread; the cap I is fixed at the upper end of the inner hole of the bushing I through another washer thread between the upper end wall of the bushing I and the lower end wall of the cap I.

8. The propeller governor of claim 6, wherein: a plastic gasket embedded on the inner wall of the port of the cap is arranged between the cap of the beta valve assembly and the U-shaped fork; and another sealing ring is pressed and mounted among the bushing, the circular mounting opening and the adjusting gasket.

9. The propeller governor of claim 8, wherein: the structure that baffle one end of the baffle support subassembly of power turbine adjusting part rotatably installs in the installation shell that stretches out on the lower extreme lateral wall of last casing subassembly is: the bearing is assembled at the root of the supporting shaft of the supporting seat in a clearance mode, the baffle is assembled on the bearing in a clearance mode, and the supporting shaft is sleeved with a spring IV through a gasket; and integrally pressing the support seat, the bearing and the spring IV into the inner hole of the mounting shell.

10. A propeller governor according to claim 1 or 2, characterized in that: the centrifugal counterweight component of the speed selection mechanism comprises a support, two centrifugal blocks and a spiral retainer ring which are correspondingly distributed; the lower end of the support is clamped on the excircle of the upper end part of the valve sleeve through a spline sleeve; two centrifugal blocks are assembled on the support through a shaft and a bearing clearance respectively, a circle of spiral retainer ring is clamped and fixed on the outer wall of the upper end of the support, and two ends of the shaft are abutted on the inner end wall of the spiral retainer ring; the hook end which is abutted on the boss at the bottom surface of the bearing is provided with an arc surface.