Rotary flow distribution adjusting device and method for aviation

Abstract

The invention belongs to the technical field of fluid control, and relates to a rotary flow distribution adjusting device and method for aviation. Comprising an inlet shell, an annular impeller, a torsion spring, a valve element, a magnetic damper and an outlet shell. The flow distribution adjusting device is arranged at the pipeline branch position of a liquid pipe network branch system, fluid flows through the annular impeller, the annular impeller generates torsional force to drive the valve element to rotate to change the overflowing sections of the two outlets, continuous adjustment of the flow distribution proportion of different branches is achieved, and the larger the fluid flow speed is, the larger the stress of the annular impeller is. And the valve core is driven to select a larger angle to correspond to different outlet flow distribution conditions. According to the flow distribution adjusting device, the complexity of an adjusting system can be reduced, the flow resistance caused by flow distribution adjustment is reduced, and then the energy consumption of a power source in a liquid system is reduced.

Description

Technical Field

[0001] The invention belongs to the technical field of fluid control and relates to a rotary flow distribution and adjustment device for aviation and an adjustment method. Background Art

[0002] In the field of aircraft fluid control, to achieve optimal performance in systems using liquid as the working fluid, the flow distribution ratio of different branches needs to be adjusted according to the system flow rate at the pipeline branch. For the requirement of regulating the flow of fluid branches in closed pipeline systems, the current mainstream method is to install electric flow control valves on the branches or at the branch locations, and arrange flow detection and control devices in the system. The control device issues a corresponding opening instruction to the electric flow control valve based on the liquid flow signal fed back by the flow detection device. The electric flow control valve changes its opening to achieve flow distribution adjustment for different branches.

[0003] This method has the following disadvantages: when using flow control valves for regulation, a separate control valve is required for each branch, which is not conducive to improving system integration; the control valve uses throttling to regulate flow, resulting in large flow resistance losses, which is not conducive to aircraft weight reduction and increases the power consumption of the liquid power source; automatic regulation requires each flow control valve to be equipped with an electric or hydraulic drive mechanism and a set of parameter detection and control systems, which increases the weight and complexity of the system and causes control lag. Specifically in the aviation field, for working conditions requiring flow as the control input, due to the strict weight restrictions and strong electromagnetic interference of the airborne environment, it is impossible to install a flow sensor on board. Under certain conditions, pressure parameters can be used to approximately replace flow parameters, but this method is difficult to adapt to real-world working conditions. To further reduce the number of components, reduce weight, and improve system reliability, technological innovation is needed. Summary of the Invention

[0004] Purpose of the Invention

[0005] A rotary flow distribution and regulation device and method for aviation use are invented. In an aircraft fluid system with branches, purely mechanical structural components are used to replace the electric flow control valve, equivalent flow detection device and control device used to adjust flow distribution, thereby reducing the number of components, improving system reliability, improving control lag, and reducing system weight.

[0006] Technical Solution

[0007] A rotary flow distribution and regulation device for aviation, comprising an inlet casing, an annular impeller, a torsion spring, a valve core, a magnetic damper, and an outlet casing; the outer cylindrical surface of the annular impeller is in a rotationally mating relationship with the inner cylindrical surface of the inlet casing, and is circumferentially limited by a boss on the inlet casing; a tooth-like protrusion extends from the trailing edge of the annular impeller, which engages with the toothed sleeve at the front end of the downstream valve core; the valve core is a cylindrical structure with a single-sided bottom surface, the outer cylindrical surface is in a rotationally mating relationship with the inner cylindrical surface of the outlet casing, two openings are provided on the bottom surface of the valve core, and the bottom surface is in contact with two outlets on the inner bottom surface of the outlet casing.

[0008] Furthermore, the blades in the annular impeller are arranged radially and centrally symmetrically, the shapes and angles of the blades are arranged in a windmill state, and the number of blades is an odd number not less than 3.

[0009] Furthermore, balls and an annular groove for limiting the balls are provided between the annular impeller and the inlet housing.

[0010] Furthermore, one end of the torsion spring is fixed to the bottom of the valve core, and the other end is circumferentially limited by a boss on the inner side of the outlet housing.

[0011] Furthermore, it also includes a magnetic damper, the fixed part of the magnetic damper is a magnet, which is evenly distributed on the inner wall of the outlet shell along the circumferential direction, and the moving part of the magnetic damper is a copper rod, which is arranged along the circumference of the valve core and evenly distributed on the outer wall of the valve core in the circumferential direction, and the positions of the copper rod and the magnet correspond to each other.

[0012] Furthermore, the opening and the outlet correspond to each other, the opening is a special-shaped hole of a specific shape, and the overlapping portion of the opening and the outlet forms an effective flow channel.

[0013] Furthermore, the profile of the special-shaped hole is determined according to the relationship between the outlet flow ratio and the inlet total flow.

[0014] Furthermore, a limiting boss is provided on the inner wall of the outlet housing, and a limiting boss is provided on the outer wall of the valve core. The limiting bosses are in a circumferential limiting relationship, so that the torsion spring is always in a tightened working range.

[0015] When the incoming liquid flows through the annular impeller, the annular impeller is subjected to a torsional force, which drives the valve core through the end teeth to overcome the elastic force of the torsion spring and rotate around the valve core axis to another angle. At this time, the effective flow cross-section formed by the two openings at the bottom of the valve core and the two outlets changes simultaneously. When the flow area of ​​one outlet increases, the flow area of ​​the other outlet decreases accordingly, realizing flow regulation of the two outlets;

[0016] The distribution and adjustment of the flow rates of the two outlets is determined by the area ratio of the two outlets when the annular impeller and the valve core are in a specific equilibrium position. The flow cross-sectional area is larger than the flow cross-sectional area required for adjustment by throttling the minimum flow outlet, thereby achieving lower adjustment resistance.

[0017] In the initial state, the torsion spring is in a free state. When the fluid flows through the annular impeller, the annular impeller drives the valve core to rotate against the elastic force of the torsion spring. The size of the rotation angle is corresponding to the fluid flow rate. When the fluid stops flowing, the torsion spring drives the valve core and the annular impeller to return to the initial position, and the limiting bosses on the inner wall of the outlet housing and the limiting bosses provided on the outer wall of the valve core are circumferentially limited. The blades in the annular impeller are arranged radially and symmetrically. The number of blades is an odd number not less than 3, which can reduce the influence of resonance.

[0018] When the valve core twists at a certain speed, the copper rod cuts the magnetic flux lines of the magnet, and the induced current generates a magnetic field opposite to that of the magnet, generating a damping force to prevent the valve core from rotating and shaking.

[0019] A rotary flow distribution and regulation method for aviation, comprising the following steps:

[0020] Step 1: The flow rates of the two outlets 601 a and b are Qa and Qb respectively, and the total inlet flow rate is Q; the spring torsional stiffness is k;

[0021] Step 2: The required flow distribution relationship between outlets a and b is described by the following formula:

[0022]

[0023] Step 3: The annular impeller is subjected to torque N1 at the inlet flow rate Q1. At this time, the outlet flow rate of a is Qa1, and the outlet flow rate of b is Qb1. When the inlet flow rate increases by a small increment δQ, the torque increase is:

[0024]

[0025] The torsion angle generated by the valve core 4 is denoted as δθ, and δθ is expressed as follows:

[0026]

[0027] At this time, the length and width of the corresponding exit b that is not blocked by the opening is recorded as y, and the effective area changes of the two exits a and b are:

[0028] δA a =L a ·x (3)

[0029] δA b =-(L a -y)·x (4)

[0030] For the flow change, we can perform integral calculation with x as the independent variable, and we have

[0031]

[0032] Combined with the known effective area A of outlets a and b when there is no flow in the example a0 and A b0 , combining the above equations (1) to (5) to obtain y = f(x), and the contour shape of the outlet can be determined.

[0033] The beneficial effects of this application are:

[0034] The flow distribution and regulation device of the present invention is arranged at a branch point in a branching system of a liquid pipe network. Fluid flows through an annular impeller, which generates a torsional force that drives the valve core to rotate, changing the flow cross-section of the two outlets, thereby achieving continuous adjustment of the flow distribution ratio of different branches. The greater the fluid flow rate, the greater the force on the annular impeller, which drives the valve core to select a larger angle to correspond to different outlet flow distribution conditions. This flow distribution and regulation device can reduce the complexity of the regulation system, reduce the flow resistance caused by flow distribution regulation, and thus reduce the energy consumption of the power source in the liquid system. At the same time, the device can reduce the number of regulating components, reduce the cost of the fluid regulation device, improve system reliability, improve control hysteresis and control fluctuation, and reduce system weight. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] Figure 1 This is a schematic structural diagram of the flow distribution and regulation device of the present invention;

[0036] Figure 2 It is a front view of the inner cavity of the outlet housing of the present invention;

[0037] Figure 3 This is a schematic diagram of the upper opening of the valve core of the present invention;

[0038] Figure 4 This is a schematic diagram of the valve core opening and outlet coordination of the present invention;

[0039] Figure 5 This is a schematic diagram of the design dimensions of the letter-sending opening of the present invention;

[0040] Among them: 1-inlet housing, 2-annular impeller, 3-torsion spring, 4-valve core, 5-magnetic damper, 6-outlet housing, 101-shoulder, 102-ball, 103-annular groove, 401-opening, 501-copper rod, 502-magnet, 601-outlet. DETAILED DESCRIPTION

[0041] In order to make the purpose, technical solutions and advantages of the implementation of the present invention clearer, the technical solutions in the embodiments of the present invention will be described in more detail below in conjunction with the embodiments of the present invention. In the examples, the same or similar reference numerals throughout represent the same or similar originals or elements with the same or similar functions. The described embodiments are part of the embodiments of the present invention, not all of the embodiments. The embodiments described below by reference are illustrative and intended to be used to explain the present invention, and should not be understood as limiting the present invention. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of the present invention. The following is a detailed description in conjunction with the embodiments of the present invention.

[0042] A rotary flow distribution and regulation device for aviation includes an inlet housing 1, an annular impeller 2, a torsion spring 3, a valve core 4, a magnetic damper 5, and an outlet housing 6. Its core components are an annular impeller 2 and a valve core 4. The outer cylindrical surface of the impeller is in a rotational fit relationship with the inner cylindrical surface of the inlet shell 1, and is circumferentially limited by the boss 101 on the inlet shell; balls 102 and annular grooves 103 for limiting the balls are arranged between the annular impeller 2 and the inlet shell 1 to reduce friction resistance; the blades in the impeller are arranged radially and centrally symmetrically, and the number of blades is an odd number not less than 3 to reduce the influence of resonance; a tooth-like protrusion extends from the trailing edge of the impeller and engages with the front end tooth of the downstream valve core 4; the valve core 4 is a cylindrical structure with a single-sided bottom surface, and the outer cylindrical surface is in a rotational fit relationship with the inner cylindrical surface of the outlet shell 6. Two openings 401 are provided on the bottom surface of the valve core 4, and the bottom surface is in contact with two outlets 601 on the inner bottom surface of the outlet shell 6; a plurality of teeth are provided on the side of the valve core side cylinder without a bottom surface, which is in contact with the teeth on the trailing edge of the impeller and is used to receive the impeller torque. One end of the torsion spring 3 is fixed to the bottom of the valve core 4 , and the other end is circumferentially limited by a boss 602 on the inner side of the outlet housing 6 .

[0043] When liquid flows through the annular impeller 2, the annular impeller 2 generates a circumferential force, which drives the valve core 4 to twist, overcomes the torque of the torsion spring 3, and rotates around the axis of the valve core 4 by an angle. The elastic force of the torsion spring 3 at the corresponding angular displacement is balanced with the torsional force of the impeller. By changing the overlapping part of the two openings 401 on the valve core 4 and the two outlets 601 of the housing, the flow distribution ratio of different branches can be adjusted;

[0044] The opening 401 at the bottom of the valve core 4 is a special-shaped hole. When the valve core 4 rotates with the annular impeller 2, the opening 401 at the bottom of the valve core 4 rotates around the axis of the valve core 4 by an angle, changing the effective cross-section of the outlet facing the valve core 4. The special-shaped profile of each opening 401 is designed according to the relationship between the ratio of each outlet flow rate and the total inlet flow rate.

[0045] The torsion spring 3 is used to provide a restoring force after the valve core 4 rotates. The torsion spring 3 is arranged between the bottom of the valve core 4 and the bottom of the outlet housing 6. It is limited and transmits torque by the spring positioning platform on the bottom surface of the outlet housing 6 and the limiting hole on the valve core 4. The working circle of the torsion spring 3 is installed outside the positioning platform of the outlet housing. The fixed end spring arm is limited by the limiting boss 602 in the spring ring groove, and the movable end is bent and extended into the limiting hole on the bottom surface of the valve core 4. A limiting boss 602 is provided on the inner wall of the outlet housing 6, and a limiting boss 402 is provided on the outer wall of the valve core 4. The limiting boss 602 and the limiting boss 402 are in a circumferential limiting relationship, and the positions of the limiting hole and the limiting boss 602 are coordinated to ensure that the torsion spring 3 is always in the tightening working range.

[0046] The distribution and regulation of the flow rates of the two outlets 601 is determined by the area ratio of the two outlets 401 when the annular impeller 2 and the valve core 4 are in a specific equilibrium position, and the flow cross-sectional area is larger than the flow cross-sectional area required for regulation by throttling the minimum flow outlet, thereby achieving a lower regulation resistance;

[0047] The magnetic damper 5 is arranged between the valve core 4 and the outlet housing 6, and consists of a magnet 502 and a copper rod 501; the magnet 502 is arranged on the inner surface of the outlet housing 6, and its outer contour does not exceed the cylindrical surface of the outlet housing 6 and the valve core 4 in rotation. The copper rod 501 is arranged on the cylindrical surface outside the valve core 4, and is arranged axially parallel to the valve core 4 at a position facing the magnet 502; when the valve core 4 twists at a certain speed, the copper rod 501 cuts the magnetic flux lines of the magnet 502, and the induced current generates a magnetic field opposite to that of the magnet, generating a damping force to prevent the valve core 4 from generating rotational jitter.

[0048] The rotary flow distribution and adjustment method for aviation includes the following steps:

[0049] 1. Let the flow rates of the two outlets 601 a and b be Qa and Qb respectively, and the total inlet flow rate be Q; the spring torsional stiffness is k;

[0050] 2. The required flow distribution relationship between outlets a and b is described by the following formula:

[0051]

[0052] 3. The annular impeller 2 is subjected to torque N1 at the inlet flow rate Q1. At this time, the outlet flow rate of a is Qa1, and the outlet flow rate of b is Qb1. When the inlet flow rate increases by a small increment δQ, the torque increase is:

[0053]

[0054] The torsion angle generated by the valve core 4 is denoted as δθ, and δθ is expressed as follows:

[0055]

[0056] At this time, the length and width of the corresponding outlet b that is not blocked by the opening 502 is recorded as y, and the effective area changes of the two outlets a and b are:

[0057] δA a =L a ·x (3)

[0058] δA b =-(L a -y)·x (4)

[0059] For the flow change, we can perform integral calculation with x as the independent variable, and we have

[0060]

[0061] Combined with the known effective area A of outlets a and b when there is no flow in the example a0 and A b0 By combining the above equations (1) to (5), we can obtain y=f(x), and the contour shape of the outlet 502 can be determined.

[0062] Since the driving force change of the regulating device is directly derived from the liquid flow rate, there is no need for parameter acquisition and control logic feedback control, and therefore the control lag disadvantage unique to PID control does not exist.

[0063] It will be understood by those skilled in the art that, unless otherwise defined, all terms (including technical and scientific terms) used herein have the same meaning as those generally understood by those skilled in the art in the art to which the present invention belongs. It should also be understood that terms such as those defined in general dictionaries should be understood to have meanings consistent with those in the context of the prior art, and unless defined as such, they will not be interpreted in an idealized or overly formal sense. The specific embodiments described above further describe the objectives, technical solutions and beneficial effects of the present invention in detail. It should be understood that the above description is only a specific embodiment of the present invention and is not intended to limit the present invention. Within the spirit and principles of the present invention, any person skilled in the art may use the technical content disclosed above to change or modify it into an equivalent embodiment of an equivalent change and apply it to other fields. However, any simple modification, equivalent change and modification made to the above embodiments according to the technical essence of the present invention without departing from the content of the technical solution of the present invention, any modification, equivalent replacement, improvement, etc. made should be included in the scope of protection of the present invention.

Claims

1. A rotary flow distribution and adjustment device for aviation, characterized in that: It includes an inlet casing, an annular impeller, a torsion spring, a valve core, a magnetic damper, and an outlet casing; the outer cylindrical surface of the annular impeller is in a rotational fit relationship with the inner cylindrical surface of the inlet casing, and is circumferentially limited by a boss on the inlet casing; a sleeve tooth-like protrusion extends from the rear edge of the annular impeller and meshes with the sleeve teeth at the front end of the downstream valve core; the valve core is a cylindrical structure with a single-sided bottom surface, the outer cylindrical surface is in a rotational fit relationship with the inner cylindrical surface of the outlet casing, two openings are arranged on the bottom surface of the valve core, and the bottom surface is in contact with two outlets on the inner bottom surface of the outlet casing.

2. The device according to claim 1, characterized in that The blades in the annular impeller are arranged radially and centrally symmetrically, the shapes and angles of the blades are arranged in a windmill state, and the number of blades is an odd number not less than 3.

3. The device according to claim 2, characterized in that Balls and an annular groove for limiting the position of the balls are arranged between the annular impeller and the inlet housing.

4. The device according to claim 3, characterized in that One end of the torsion spring is fixed to the bottom of the valve core, and the other end is circumferentially limited by a boss on the inner side of the outlet housing.

5. The device according to claim 4, characterized in that It also includes a magnetic damper, the fixed part of which is a magnet, which is evenly distributed on the inner wall of the outlet shell along the circumferential direction, and the moving part of the magnetic damper is a copper rod, which is arranged along the circumference of the valve core and evenly distributed on the outer wall of the valve core in the circumferential direction, and the positions of the copper rod and the magnet correspond.

6. The device according to claim 5, characterized in that The opening and the outlet correspond to each other, the opening is a special-shaped hole of a specific shape, and the overlapping part of the opening and the outlet forms an effective flow channel.

7. The device according to claim 6, characterized in that The profile of the special-shaped hole is determined according to the relationship between the outlet flow rate ratio and the inlet total flow rate.

8. The device according to claim 7, characterized in that A limit boss is provided on the inner wall of the outlet shell, and a limit boss is provided on the outer wall of the valve core. The limit bosses and the limit bosses are in a circumferential limit relationship, so that the torsion spring is always in a tightened working range; when the incoming liquid flows through the annular impeller, the annular impeller is subjected to a torsional force, and the valve core is driven by the end teeth to overcome the elastic force of the torsion spring and rotate around the valve core axis to another angle. At this time, the effective flow cross-section formed by the two openings at the bottom of the valve core and the two outlets changes at the same time. When the flow area of ​​one outlet increases, the flow area of ​​the other outlet decreases accordingly, thereby realizing flow regulation of the two outlets.

9. The device according to claim 8, characterized in that The distribution and regulation of the two outlet flows is determined by the area ratio of the two outlets when the annular impeller and the valve core are in a specific equilibrium position, and the flow cross-sectional area is larger than the flow cross-sectional area required for regulation by throttling the minimum flow outlet, thereby achieving lower regulation resistance; In the initial state, the torsion spring is in a free state. When the fluid flows through the annular impeller, the annular impeller drives the valve core to rotate to overcome the elastic force of the torsion spring. The rotation angle corresponds to the fluid flow rate. When the fluid stops flowing, the torsion spring drives the valve core and the annular impeller to return to the initial position, and the limiting boss on the inner wall of the outlet shell and the limiting boss on the outer wall of the valve core are circumferentially limited. The blades in the annular impeller are radially and centrally arranged, and the number of blades is an odd number not less than 3, which can reduce the resonance effect. When the valve core twists at a certain speed, the copper rod cuts the magnetic flux lines of the magnet, and the induced current generates a magnetic field opposite to that of the magnet, generating a damping force to prevent the valve core from rotating and shaking.

10. The rotary flow distribution and adjustment method of the device according to claim 9, characterized in that: The steps include: Step 1: The flow rates of the two outlets 601 a and b are Qa and Qb respectively, and the total inlet flow rate is Q; the spring torsional stiffness is k; Step 2: The required flow distribution relationship between the two outlets a and b is described as follows: Step 3: The annular impeller is subjected to torque N1 at the inlet flow rate Q1. At this time, the outlet flow rate of a is Qa1, and the outlet flow rate of b is Qb1. When the inlet flow rate increases by a small increment δQ, the torque increase is: The torsion angle generated by the valve core 4 is denoted as δθ, and δθ is expressed as follows: At this time, the length and width of the corresponding exit b that is not blocked by the opening is recorded as y, and the effective area changes of the two exits a and b are: δA a =L a ·x (3) δA b =-(L a -y)·x (4) For the flow change, taking x as the independent variable for integral calculation, we have Combined with the known effective area A of outlets a and b when there is no flow in the example a0 and A b0 By combining the above equations (1) to (5), we can obtain y=f(x), and the contour shape of the outlet can be determined.

Images