阅读说明：本技术 一种外涵气控制的滑油活门 (Oil lubricating valve controlled by external air ) 是由 郁丽 左斌辉 李国权 于 2021-06-25 设计创作，主要内容包括：本申请提供了一种外涵气控制的滑油活门,包括：具有容纳腔的活门壳体,其侧边具有滑油进口,其下端具有滑油出口,滑油出口与滑油进口连通,其中部具有台阶部,在台阶部上设有连通容纳腔的外涵进气口；设置在容纳腔内的T形阀芯,T形阀芯能够调节滑油进口与滑油出口之间的滑油流通量,其的外侧设有密封槽,密封槽内设有涨圈,T形阀芯上设有弹簧外引导套,其中,T形阀芯端部与活门壳体之间设有密封圈；与活门壳体固定连接的堵盖,堵盖上设有与大气环境连通的通孔,堵盖上设有弹簧内引导；设置在T形阀芯与堵盖之间的弹簧。通过构建滑油活门在低状态下的稳态控制模型及在高状态下的稳态控制模型实现外涵气控制下的滑油活门的开启与关闭。(The application provides a smooth oil valve of outer air control of containing includes: the valve shell is provided with an accommodating cavity, the side edge of the valve shell is provided with a lubricating oil inlet, the lower end of the valve shell is provided with a lubricating oil outlet, the lubricating oil outlet is communicated with the lubricating oil inlet, the middle part of the valve shell is provided with a step part, and a bypass air inlet communicated with the accommodating cavity is arranged on the step part; the T-shaped valve core is arranged in the accommodating cavity, the T-shaped valve core can adjust the flow of lubricating oil between a lubricating oil inlet and a lubricating oil outlet, a sealing groove is formed in the outer side of the T-shaped valve core, an expansion ring is arranged in the sealing groove, a spring outer guide sleeve is arranged on the T-shaped valve core, and a sealing ring is arranged between the end part of the T-shaped valve core and the valve shell; the plug cover is fixedly connected with the valve shell, a through hole communicated with the atmospheric environment is formed in the plug cover, and a spring inner guide is arranged on the plug cover; and the spring is arranged between the T-shaped valve core and the blocking cover. The opening and closing of the lubricating oil valve under external air control are realized by constructing a stable state control model of the lubricating oil valve under a low state and a stable state control model of the lubricating oil valve under a high state.)

1. An oil control by external air, said oil control valve comprising:

the valve comprises a valve shell (1) with an accommodating cavity, wherein a lubricating oil inlet (2) perpendicular to the axis of the valve shell is formed in the side edge of the valve shell (1), a lubricating oil outlet (3) arranged along the axis of the valve shell is formed in the lower end of the valve shell (1), the lubricating oil outlet (3) is communicated with the lubricating oil inlet (2), a step part is formed in the middle of the valve shell (1), and an external culvert air inlet (4) communicated with the accommodating cavity is formed in the step part;

the valve comprises a T-shaped valve core (6) arranged in a containing cavity, wherein the end part of the T-shaped valve core (6) extends into a lubricating oil inlet (2) and can adjust the flow of lubricating oil between the lubricating oil inlet (2) and a lubricating oil outlet (3), a sealing groove (7) is arranged on the outer side of the T-shaped valve core (6), a piston ring (10) in contact with a valve shell (1) is arranged in the sealing groove (7), the T-shaped valve core (6) is provided with an axially extending spring outer guide sleeve (8), and a sealing ring (9) is arranged between the end part of the T-shaped valve core extending into the lubricating oil inlet (2) and the valve shell (1);

the blocking cover (12) is fixedly connected with the valve shell (1), a through hole (13) communicated with the atmospheric environment is formed in the blocking cover (12), and the blocking cover (12) is provided with an axially extending spring inner guide (14);

the spring (11) is arranged between the T-shaped valve core (6) and the blocking cover (12) and is limited by the spring outer guide sleeve (8) and the spring inner guide (14);

the sealing ring (9) divides the valve shell (1) and the T-shaped valve core (6) into an oil slide cavity (15) and an outer bypass air cavity (16), the pressure of the oil slide cavity (15) is the pressure of an oil supply pressurization oil way, the outer bypass air cavity (16) is the pressure of the outer bypass air of the engine, and an environment air cavity (17) equivalent to the pressure of the external atmospheric environment is formed among the valve shell (1), the T-shaped valve core (6) and the blocking cover (12);

the opening and closing of the lubricating oil valve under external air control are realized by constructing a stable state control model of the lubricating oil valve under a low state and a stable state control model of the lubricating oil valve under a high state.

2. The bypass control oil damper according to claim 1, characterized in that a boss (18) is provided inside the step portion in a low engine state.

3. An externally controlled oil gallery valve as claimed in claim 1 or 2, wherein the steady state control model at low engine conditions is:

P_0j·A₂+F_tj≥P_1j·A₁+P_2j·A₂+F_m1·n+F_m2

in the formula:

P_0jwhen the lubricating oil flow path is in a throttling state, the pressure of the lubricating oil flow path corresponds to the pressure of an environment air cavity (17);

A₂the area corresponding to the maximum diameter of the T-shaped valve core (6);

F_tjwhen the lubricating oil flow path is in a throttling state, the stress of the spring (11) is corresponded;

P_1jwhen the lubricating oil flow path is in a throttling state, the pressure of the corresponding lubricating oil cavity (15) is adjusted;

A₁the area of the T-shaped valve core (6) is corresponding to the diameter of a matching shaft of the sealing ring (9);

P_2jwhen the lubricating oil flow path is in a throttling state, the pressure of the corresponding external culvert air cavity (16) is obtained;

F_m1starting frictional resistance for the sealing ring (9);

n is the number of the sealing rings (9);

F_m2starting frictional resistance for the piston ring (10);

△P_jis the local resistance loss of the lubricating oil through a fluid area formed by the corresponding lubricating oil outlet (3) and the T-shaped valve core (6);

xi is a local resistance loss coefficient of the fluid area formed by the corresponding lubricating oil outlet (3) and the T-shaped valve core (6) through the lubricating oil;

g is the mass flow of the lubricating oil;

ρ_oilis the lube density;

A₃the area of the lubricating oil outlet (3) corresponding to the fluid area formed by the T-shaped valve core (6), namely the throttling clearance.

4. A bypass air controlled oil dam as defined in claim 3 wherein the local drag coefficient ξ is

In the formula, A₀Is the area corresponding to the diameter of the lubricating oil outlet (3).

5. An externally controlled oil control flap according to claim 3, characterized in that the steady state control model at high engine conditions is:

P_0j2·A₂+F_tj2≥P_1j2·A₁+P_2j2·A₂+F_m1·n+F_m2

in the formula:

P_0j2when the lubricating oil flow path is in a non-throttling state, the pressure of the corresponding environment air cavity (17) is controlled;

F_tj2when the lubricating oil flow path is in a non-throttling state, the corresponding spring (11) is stressed;

P_1j2when the lubricating oil flow path is in a non-throttling state, the pressure of the corresponding lubricating oil cavity (15) is controlled;

P_2j2when the lubricating oil flow path is in a non-throttling state, the pressure of the corresponding external culvert air cavity (16) is obtained.

Technical Field

The application belongs to the technical field of aeroengines, and particularly relates to an oil lubricating valve controlled by external air.

Background

The main bearing cavity of the advanced aeroengine is tightly sealed by a full-envelope outer-culvert gas sealing method, a lubricating oil supply system adopts a scheme that the state above slow turning is a constant-pressure-difference oil supply scheme, the aeroengine is in a slow turning or throttling state near the left boundary of a flight envelope, the main bearing cavity is tightly sealed and has small pressure difference, so that the lubricating oil leakage risk at the tight sealing position exists in the bearing cavity, the consumption of the lubricating oil system is increased, the endurance capacity is influenced, and the lubricating oil is leaked to a main runner of the engine to cause the lubricating oil coking, even firing and other faults.

At present, the advanced aeroengine mostly adopts a one-way valve structure with throttling to realize the scheme of reducing oil supply in the low state of the engine, the opening pressure of a spring corresponds to the rotating speed characteristic of the engine, when the rotating speed of the engine is low, the oil supply is reduced by the throttling hole of the one-way valve, when the rotating speed of the engine reaches a certain value, the oil supply pressure and the oil supply flow reach a certain value, the one-way valve is opened, the area of a flow passage is increased, and therefore the normal oil supply is realized. In addition, the control can also be realized by adopting electromagnetic signals.

However, both of the above solutions have some disadvantages:

1) the one-way valve with throttling cannot be matched with the pneumatic state of the high-altitude engine for control, and is only used for reducing oil supply in the starting state of the engine to ensure the reliability of a mechanical system, so that the design requirements of most working conditions such as slow vehicle starting from the engine to the ground, slow vehicle high-altitude air, throttling in high-altitude air and the like cannot be met;

2) the electromagnetic signal is adopted to carry out the control scheme, an engine is required to provide a power supply, control judgment logic, a pressure measuring point and a signal acquired by the pressure measuring point, and meanwhile, the electromagnetic valve of the scheme needs an electromagnet, so that the overall weight and the volume are larger than those of a mechanical valve.

Disclosure of Invention

It is an object of the present application to provide a bleed valve with bypass control to solve or mitigate at least one of the problems of the background art.

The technical scheme of the application is as follows: an oil galley that is externally vented and controlled, the oil galley comprising:

the valve comprises a valve shell (1) with an accommodating cavity, wherein a lubricating oil inlet (2) perpendicular to the axis of the valve shell is formed in the side edge of the valve shell (1), a lubricating oil outlet (3) arranged along the axis of the valve shell is formed in the lower end of the valve shell (1), the lubricating oil outlet (3) is communicated with the lubricating oil inlet (2), a step part is formed in the middle of the valve shell (1), and an external culvert air inlet (4) communicated with the accommodating cavity is formed in the step part;

the valve comprises a T-shaped valve core (6) arranged in a containing cavity, wherein the end part of the T-shaped valve core (6) extends into a lubricating oil inlet (2) and can adjust the flow of lubricating oil between the lubricating oil inlet (2) and a lubricating oil outlet (3), a sealing groove (7) is arranged on the outer side of the T-shaped valve core (6), a piston ring (10) in contact with a valve shell (1) is arranged in the sealing groove (7), the T-shaped valve core (6) is provided with an axially extending spring outer guide sleeve (8), and a sealing ring (9) is arranged between the end part of the T-shaped valve core extending into the lubricating oil inlet (2) and the valve shell (1);

the blocking cover (12) is fixedly connected with the valve shell (1), a through hole (13) communicated with the atmospheric environment is formed in the blocking cover (12), and the blocking cover (12) is provided with an axially extending spring inner guide (14);

the spring (11) is arranged between the T-shaped valve core (6) and the blocking cover (12) and is limited by the spring outer guide sleeve (8) and the spring inner guide (14);

the sealing ring (9) divides the valve shell (1) and the T-shaped valve core (6) into an oil slide cavity (15) and an outer bypass air cavity (16), the pressure of the oil slide cavity (15) is the pressure of an oil supply pressurization oil way, the outer bypass air cavity (16) is the pressure of the outer bypass air of the engine, and an environment air cavity (17) equivalent to the pressure of the external atmospheric environment is formed among the valve shell (1), the T-shaped valve core (6) and the blocking cover (12);

the opening and closing of the lubricating oil valve under external air control are realized by constructing a stable state control model of the lubricating oil valve under a low state and a stable state control model of the lubricating oil valve under a high state.

Further, a boss is provided inside the stepped portion.

Further, the steady state control model under the low state of the lubricating oil valve is as follows:

P_0j·A₂+F_tj≥P_1j·A₁+P_2j·A₂+F_m1·n+F_m2

in the formula:

P_0jwhen the lubricating oil flow path is in a throttling state, the pressure of the lubricating oil flow path corresponds to the pressure of an environment air cavity (17);

A₂the area corresponding to the maximum diameter of the T-shaped valve core (6);

F_tjwhen the lubricating oil flow path is in a throttling state, the stress of the spring (11) is corresponded;

P_1jwhen the lubricating oil flow path is in a throttling state, the pressure of the corresponding lubricating oil cavity (15) is adjusted;

A₁the area of the T-shaped valve core (6) is corresponding to the diameter of a matching shaft of the sealing ring (9);

P_2jwhen the lubricating oil flow path is in a throttling state, the pressure of the corresponding external culvert air cavity (16) is obtained;

F_m1starting frictional resistance for the sealing ring (9);

n is the number of the sealing rings (9);

F_m2starting frictional resistance for the piston ring (10);

△P_jis the local resistance loss of the lubricating oil through a fluid area formed by the corresponding lubricating oil outlet (3) and the T-shaped valve core (6);

xi is a local resistance loss coefficient of the fluid area formed by the corresponding lubricating oil outlet (3) and the T-shaped valve core (6) through the lubricating oil;

g is the mass flow of the lubricating oil;

ρ_oilis the lube density;

A₃the area of the lubricating oil outlet (3) corresponding to the fluid area formed by the T-shaped valve core (6), namely the throttling clearance.

Further, the local resistance coefficient ξ is

In the formula, A₀Is the area corresponding to the diameter of the lubricating oil outlet (3).

Further, the steady state control model under the high state of the oil sliding valve is as follows:

P_0j2·A₂+F_tj2≥P_1j2·A₁+P_2j2·A₂+F_m1·n+F_m2

in the formula:

P_0j2when the lubricating oil flow path is in a non-throttling state, the pressure of the corresponding environment air cavity (17) is controlled;

F_tj2when the lubricating oil flow path is in a non-throttling state, the corresponding spring (11) is stressed;

P_1j2when the lubricating oil flow path is in a non-throttling state, the pressure of the corresponding lubricating oil cavity (15) is controlled;

P_2j2when the lubricating oil flow path is in a non-throttling state, the pressure of the corresponding external culvert air cavity (16) is obtained.

The utility model provides a contain the smooth oil valve of gas control outward can adjust along with engine pneumatic state, has realized the full envelope control of aircraft, has expanded the controllable scope of smooth oil system, reduces the control logic of having abandoned electrical component simultaneously to can reduce electrical equipment and reduce structure weight, and the reliability is high.

Drawings

In order to more clearly illustrate the technical solutions provided by the present application, the following briefly introduces the accompanying drawings. It is to be expressly understood that the drawings described below are only illustrative of some embodiments of the invention.

Fig. 1 is a schematic view of an oil trap controlled by external air under throttling conditions in the present application.

Fig. 2 is a schematic view of the externally contained air controlled oil trap in an un-throttled state in the present application.

Reference numerals:

1-valve housing

2-lubricating oil inlet

3-lubricating oil outlet

4-culvert air inlet

5-mounting edge

6-T type valve core

7-seal groove

8-guide sleeve

9-sealing ring

10-piston ring

11-spring

12-plug cover

13-linked via

14-guide part

15-lubricating oil cavity

16-outer culvert air cavity

17-ambient air Chamber

18-convex platform

Detailed Description

In order to make the implementation objects, technical solutions and advantages of the present application clearer, the technical solutions in the embodiments of the present application will be described in more detail below with reference to the drawings in the embodiments of the present application.

As the throttle state of the oil valve of the outer air control shown in fig. 1 and the non-throttle state of the oil valve of the outer air control shown in fig. 2, the oil valve of the outer air control provided by the application mainly comprises: the valve comprises a valve shell 1, a T-shaped valve core 6, a blocking cover 12, a spring 11 and the like.

The valve shell 1 is provided with a containing cavity, a lubricating oil inlet 2 perpendicular to the axis of the valve shell is formed in the side edge of the valve shell 1, a lubricating oil outlet 3 arranged along the axis of the valve shell is formed in the lower end of the valve shell 1, the lubricating oil outlet 3 is communicated with the lubricating oil inlet 2, a step portion is formed in the middle of the valve shell 1, and an outer bypass air inlet 4 communicated with the containing cavity is formed in the step portion. Further, a boss 18 is provided inside the stepped portion to prevent the T-shaped valve body 6 from completely adhering to the stepped portion.

The T-shaped valve core 6 is arranged in the containing cavity, the end part of the T-shaped valve core 6 extends into the lubricating oil inlet 2 and can adjust the flow rate of lubricating oil between the lubricating oil inlet 2 and the lubricating oil outlet 3, a sealing groove 7 is arranged on the outer side of the T-shaped valve core 6, an expansion ring 10 which is in contact with the valve shell 1 is arranged in the sealing groove 7, the T-shaped valve core 6 is provided with an axially extending spring outer guide sleeve 8, and a sealing ring 9 is arranged between the end part of the T-shaped valve core which extends into the lubricating oil inlet 2 and the valve shell 1.

The closure cap 12 is fixedly connected to the valve housing 1, and the closure cap 12 is provided with a through hole 13 communicating with the atmosphere, the closure cap 12 having an axially extending spring inner guide 14.

The spring 11 is arranged between the T-shaped valve core 6 and the blocking cover 12 and limited by the spring outer guide sleeve 8 and the spring inner guide 14.

The valve shell 1 and the T-shaped valve core 6 are divided into an oil cavity 15 and an outer bypass air cavity 16 by the sealing ring 9, the pressure of the oil cavity 15 is the pressure of an oil supply pressurization oil way, the outer bypass air cavity 16 is the pressure of the outer bypass air of the engine, and an environment air cavity 17 with the pressure equivalent to the pressure of the external atmospheric environment is formed among the valve shell 1, the T-shaped valve core 6 and the blocking cover 12.

The opening and closing of the lubricating oil valve under external air control are realized by constructing a stable state control model of the lubricating oil valve under a low state and a stable state control model of the lubricating oil valve under a high state.

In a low state of the engine (i.e., a state where the engine speed is low, such as cruising), the oil flow path of the oil slide valve is in a throttle state, the T-shaped valve element 6 of the valve is in a state shown in fig. 1, and the throttle equivalent area of the oil flow path is a clearance area formed between the oil outlet 3 and the minimum outer diameter of the T-shaped valve element 4. At this time, the spring force F of the spring 11_tjAt ambient atmospheric pressure P_0jActing on the maximum diameter area A of the T-shaped valve core 6₂Is greater than or equal to the pressure P of the oil gallery 15_1jActing on the area A corresponding to the sealing diameter of the T-shaped valve core 6₁Acting force of, pressure P of outer culvert air cavity 16_2jActing on the maximum diameter area A of the T-shaped valve core 6₂The sum of the acting force of the piston ring 9 and the starting friction force of the piston ring 10.

The mathematical model for controlling the valve in the steady state under the low state is as follows:

P_0j·A₂+F_tj≥P_1j·A₁+P_2j·A₂+F_m1·n+F_m2

in the high state of the engine (i.e., the state where the engine speed is high, such as climbing), the oil flow path of the oil slide valve is in the non-throttle state, the T-shaped valve element 6 of the valve is in the state shown in fig. 2, and the flow area of the oil flow path is the area of the oil outlet 3. At this time, the pressure P of the oil chamber 15₁The sealing diameter acting on the T-shaped valve core 6 corresponds toArea A₁Acting force of, pressure P of outer culvert air cavity 16₂Acting on the maximum diameter area A of the T-shaped valve core 6₂The sum of the acting force of (3) and the starting friction force of the seal ring 9 and the piston ring 10 is equal to or greater than the spring force F of the spring 11_tAt ambient atmospheric pressure P₀Acting on the maximum diameter area A of the T-shaped valve core 6₂The sum of the forces of (a).

The mathematical model for controlling the valve in the steady state under the high state is as follows:

P_0j2·A₂+F_tj2≥P_1j2·A₁+P_2j2·A₂+F_m1·n+F_m2。

alphabetical meanings in the above model:

F_tjwhen the lubricating oil flow path is in a throttling state, the corresponding spring is stressed;

F_tj2when the lubricating oil flow path is in an unthrottled state, the corresponding spring is stressed;

F_m1-seal ring start-up friction resistance;

F_m2-piston ring starting friction resistance;

n is the number of seal rings;

P_1jwhen the lubricating oil flow path is in a throttling state, the pressure of the corresponding lubricating oil cavity 15 is high;

P_1j2when the lubricating oil flow path is in an unthrottled state, the pressure of the corresponding lubricating oil cavity 15 is high;

P_2jwhen the lubricating oil flow path is in a throttling state, the pressure of the corresponding external culvert air cavity 16 is controlled;

P_2j2when the lubricating oil flow path is in an unthrottled state, the pressure of the corresponding external culvert air cavity 16 is controlled;

P_0jwhen the lubricating oil flow path is in a throttling state, the pressure of the lubricating oil flow path corresponds to the pressure of the environment air cavity 17;

P_0j2when the lubricating oil flow path is in an unthrottled state, the pressure of the corresponding environment air cavity 17 is high;

△P_jlocal drag loss of the oil through the fluid area formed by the corresponding oil outlet 3 and the T-shaped spool 6;

A₀-area corresponding to the diameter of the oil outlet 3;

A₁the area of the T-shaped spool 6 corresponding to the diameter of the shaft on which the sealing ring 9 is fitted;

A₂the area corresponding to the maximum diameter of the T-shaped valve core 6;

A₃the area of the oil outlet 3 corresponding to the fluid area formed by the T-shaped spool 6 (throttle gap);

ρ_oil-oil density;

xi-local resistance loss coefficient of the oil passing through the fluid region formed by the corresponding oil outlet 3 and the T-shaped valve core 6 can be approximately obtained

G is the mass flow of the lubricating oil.

The utility model provides a contain the smooth oil valve of gas control outward can adjust along with engine pneumatic state, has realized the full envelope control of aircraft, has expanded the controllable scope of smooth oil system, reduces the control logic of having abandoned electrical component simultaneously to can reduce electrical equipment and reduce structure weight, and the reliability is high.

The above description is only for the specific embodiments of the present application, but the scope of the present application is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present application should be covered within the scope of the present application. Therefore, the protection scope of the present application shall be subject to the protection scope of the claims.