Control valve sleeve structure capable of preventing clamping stagnation and optimization design method

Abstract

The invention discloses an anti-clamping control valve sleeve structure and an optimization design method, and belongs to the technical field of industrial process automatic control valves. The structure comprises a valve core, a sleeve, a circulation hole and an actuating mechanism connecting part, the outer circumference of the valve core comprises a high-pressure side elliptic cylindrical surface section and a low-pressure side cylindrical surface section, and the inner wall of the sleeve is matched with the valve core in shape. The circulation holes are distributed in the wall face of the sleeve, the low-pressure side holes are evenly distributed, and the high-pressure side holes are distributed according to a set circumferential angle so that unbalanced stress of the valve element can be reduced. Through setting parameters of long and short axes of an ellipse, the aperture, a basic circumferential angle and a pressure difference, and combining with an optimization algorithm, hole column distribution is subjected to iterative solution, so that the balance of acting force of fluid in a full-opening range is realized. The structure and the method effectively reduce the clamping stagnation risk of the control valve, improve the operation precision and prolong the service life of the control valve. The method can be widely applied to industrial process control fields of electric power, petrifaction, metallurgy and the like.

Description

Technical Field

[0001] This invention belongs to the field of industrial process automation control valve technology, specifically relating to an anti-jamming control valve sleeve structure and its optimization design method. Background Technology

[0002] Sleeve control valves are widely used in industrial process control in thermal power, petrochemical, and metallurgical industries due to their advantages such as stable throttling, erosion resistance, and convenient maintenance. However, during valve throttling, the uneven distribution of the sleeve window or orifice group and the asymmetry of the jet flow state lead to uneven circumferential pressure distribution in the valve core, generating a large radial fluid force (lateral force). This lateral force increases friction between the valve core and the guide sleeve, causing valve stem bending, packing leakage, and premature wear of the guide sleeve, thus reducing the valve's operating accuracy and lifespan.

[0003] In existing technologies, some solutions reduce lateral forces by increasing the length of the guide sleeve or using a single opposing hole. However, under different opening degrees, different pressure differentials, and multi-stage throttling conditions, it is still difficult to achieve radial force balance throughout the entire stroke range. Simply reducing the number of openings on the high-pressure side of the sleeve not only significantly affects the overall flow capacity of the sleeve valve but also proves ineffective when the unbalanced force is large.

[0004] Therefore, there is an urgent need to provide a new anti-jamming control valve sleeve structure and an optimized design method. Summary of the Invention

[0005] The purpose of this invention is to overcome the deficiencies in the prior art and provide an anti-jamming control valve sleeve structure and an optimized design method. This invention achieves radial fluid force balance throughout the entire stroke of the valve core by changing the shape of the sleeve and valve core corresponding to the high-pressure zone and the arrangement of the throttling orifices.

[0006] The specific technical solution adopted in this invention is as follows: In a first aspect, the present invention provides an anti-jamming control valve sleeve structure, including a valve core, a sleeve, a flow hole, and an actuator connection part; The valve core is slidably and sealed inside the sleeve. The circumferential side of the valve core consists of an elliptical cylindrical section and a cylindrical section, with the minor axis of the elliptical cylindrical section equal to the radius of the cylindrical section, resulting in a smooth circumferential side structure. The elliptical cylindrical section of the valve core is the high-pressure side, and the cylindrical section is the low-pressure side. The sleeve has several rows of holes along its circumference, each row including several vertically spaced flow holes. The rows of holes on the low-pressure side are evenly distributed circumferentially, while the rows of holes on the high-pressure side are spaced at equal circumferential angles and are generally biased towards the minor axis of the elliptical cylindrical section, forming a basic circumferential angle. β This ensures that the radial force exerted on the valve core by the fluid is approximately balanced throughout the entire stroke range, thereby reducing the risk of jamming.

[0007] Preferably, the valve core is provided with an actuator connection part at the top for connecting an external drive device. The drive device enables the valve core to slide up and down along the inner wall of the sleeve to change the opening state of the flow hole and achieve flow regulation.

[0008] Preferably, the wall of the flow hole is perpendicular to the wall of the sleeve.

[0009] Preferably, when the valve core is in the lower limit position, it can block all flow holes; when the valve core is in the upper limit position, it can fully open all flow holes.

[0010] Secondly, the present invention provides an optimized design method for an anti-jamming control valve sleeve structure as described in any of the first aspects, as follows: S1: Set the length of the major axis including the elliptical cylindrical segment. a Length of the minor axis of the elliptical cylindrical segment b Flow hole radius r Total number of holes N Basic inscribed angle β High-pressure side pressure p h and low-pressure side pressure p l Initial pore distribution parameters, including those included; S2: Distributed on the low-pressure side cylindrical section and the high-pressure side elliptical cylindrical section respectively. N L Group of holes and N H A set of holes, and satisfying... N L + N H = N ;make N H The value is even, and the circumferential angle interval between adjacent hole rows on the low-pressure side cylindrical section and the high-pressure side elliptical cylindrical section is calculated respectively. Δθ j and Δθi ; where subscript i , j Represent the first segment of the elliptical cylindrical surface, respectively. i The first row of holes and cylindrical sections j perforated; S3: Based on the results obtained in S2, calculate the radial force components exerted on the valve core by each set of holes on the cylindrical section on the low-pressure side. F j and the radial force components exerted on the valve core by each set of holes on the elliptical cylindrical section on the high-pressure side. F i ; S4: Radial force component obtained from S3 Fj and F i Determine the total unbalanced radial force F tot And set the objective function. F tot ≈0 is used as the optimization objective; S5: Utilize optimization algorithms to... a and β Iterative adjustments were made until... F tot After meeting the set precision or threshold, Δ is then calculated to meet the requirements. θ i ; S6: If the Δ obtained in S5 θ i If it is less than the set value, then increase. a The values ​​are iterated again through steps S1 to S6 until the optimal hole distribution parameters that satisfy the constraints are obtained.

[0011] Preferably, the calculation formula for S2 is as follows: , , , .

[0012] Preferably, in S3, the radial force component of the current iteration step , ;in, , d The area of ​​the circular surface of the flow hole is indicated by the superscript. k This indicates the current iteration number.

[0013] Preferably, in S4, the total unbalanced radial force .

[0014] Preferably, in step S1, the flow field inside the control valve is simulated using CFD technology to estimate the pressure difference between the high-pressure side and the low-pressure side, which serves as a reference for the distribution orifice array in step S2.

[0015] Preferably, in S1, the initially set length of the major axis of the elliptical cylindrical segment is... a Not exceeding 1.5 times the minor axis length of the elliptical cylindrical segment b .

[0016] Compared with the prior art, the present invention has the following advantages: This invention distributes flow holes on the sleeve wall, with low-pressure side holes evenly distributed and high-pressure side holes distributed at a set circumferential angle to reduce the force imbalance of the valve core. By setting the major and minor axes of the ellipse, hole diameter, basic circumferential angle, and pressure difference parameters, and combining an optimization algorithm to iteratively solve the hole distribution, the balance of forces acting on the fluid within the full opening range is achieved. This structure and method effectively reduce the risk of control valve jamming and improve its operating accuracy and lifespan. It can be widely used in industrial process control fields such as power, petrochemical, and metallurgy. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of a control valve sleeve structure designed to prevent jamming. Figure 2 This is a top-down view of the force distribution on the valve core. Figure 3 This is a schematic diagram of the circumferential angle of the sleeve's circumferential flow hole (top view); Figure 4 This is the algorithm flowchart for Example 1; The attached diagram is labeled as follows: valve core 1, sleeve 2, flow hole 3, actuator connection part 4. Detailed Implementation

[0018] The present invention will be further described and illustrated below with reference to the accompanying drawings and specific embodiments. The technical features of each embodiment of the present invention can be combined accordingly, provided that there is no mutual conflict.

[0019] like Figure 1 As shown, this invention provides an anti-jamming control valve sleeve structure, which mainly includes a valve core 1, a sleeve 2, a flow hole 3, and an actuator connection part 4. The structure and connection method of each component will be described in detail below.

[0020] In the control valve sleeve structure of the present invention, the valve core 1 has a columnar structure and is slidably connected to the inside of the sleeve 2. The circumferential side surface of the valve core 1 is composed of an elliptical cylindrical segment and a cylindrical segment, and the minor axis of the elliptical cylindrical segment is equal to the radius of the cylindrical segment, making the circumferential side surface of the valve core 1 a smooth structure, such as... Figure 2 As shown. Similarly, the inner wall of sleeve 2 should match the shape of valve core 1 to form a sealing sliding structure. The elliptical cylindrical section of valve core 1 and its corresponding part of sleeve 2 are the high-pressure side, and the cylindrical section and its corresponding part of sleeve 2 are the low-pressure side.

[0021] In a preferred embodiment of the present invention, the top of the valve core 1 is provided with an actuator connection part 4, which is used to connect an external drive device. In actual use, the actuator connection part 4 is driven by the drive device, which enables the valve core 1 to slide up and down along the inner wall of the sleeve 2, thereby changing the opening state of the flow hole 3 and realizing the adjustment of the flow rate.

[0022] In the control valve sleeve structure of the present invention, the sleeve 2 is provided with multiple sets of holes along the circumferential direction, and each set of holes includes multiple flow holes 3 spaced apart in the vertical direction (e.g., Figure 1 As shown, each group of orifices includes 5 flow holes. Multiple groups of orifices on the low-pressure side are evenly distributed circumferentially; multiple groups of orifices on the high-pressure side are spaced at equal circumferential angles and are generally biased towards the minor axis of the elliptical cylindrical section, forming a basic circumferential angle. β ,like Figure 3 As shown, this configuration enables the radial force exerted by the fluid on the valve core 1 to be approximately balanced throughout the entire stroke range, thereby reducing the risk of jamming.

[0023] In a preferred embodiment of the present invention, the walls of each flow hole 3 are perpendicular to the wall surface of the sleeve 2.

[0024] In a preferred embodiment of the present invention, the dimensions of the valve core and sleeve, as well as the opening method of the flow holes, should satisfy the following: when the valve core 1 is in the lower limit position, it can block all flow holes 3; when the valve core 1 is in the upper limit position, it can fully open all flow holes 3.

[0025] like Figure 2 As shown, the pressure generated by the fluid mainly acts on the valve core through the flow orifice, and the direction of the pressure coincides with the direction of the normal vector within the curved surface of the valve core at the location of the orifice. Therefore, under the same fluid pressure, the pressure vector (i.e., the direction perpendicular to the axis of symmetry) can be changed by altering the curvature of the valve core surface. F x And parallel to the axis of symmetry F y (The direction of) Figure 2 The vector symbols and curved arrows in the diagram indicate the direction of fluid flow. The overall outflow direction coincides with the axis of symmetry, and the main radial unbalanced force on the valve core is also in this direction. Due to geometric symmetry, the flow on both sides of the axis of symmetry can also be considered almost symmetrical, and the fluid unbalanced forces perpendicular to the axis of symmetry cancel each other out. Therefore, the purpose of this invention is to change the radial unbalanced force on the valve core in the high-pressure region, which is parallel to the axis of symmetry.

[0026] The structure provided by this invention reduces the pressure component along the unbalanced direction on the valve core by both the sleeve shape and the distribution of the flow holes, thereby reducing the overall radial unbalanced force.

[0027] Based on the aforementioned anti-jamming control valve sleeve structure, this invention also provides an optimized design method, the specific steps of which are as follows: S1, Initial Settings: Set the initial hole array distribution parameters, specifically: preset the major axis length of the elliptical cylindrical segment. a Length of the minor axis of the elliptical cylindrical segment b (radius of cylindrical surface segment) RLength of the minor axis of the elliptical cylindrical segment b (Equal); determine the radius of flow orifice 3 according to flowability requirements. r Total number of holes N Preset basic circumferential angle β Preset high-pressure side pressure p h and low-pressure side pressure p l .

[0028] In a preferred embodiment of the present invention, the initially set length of the major axis of the elliptical cylindrical segment is... a Not exceeding 1.5 times the minor axis length of the elliptical cylindrical segment b .

[0029] S2, Hole Number Allocation: Under the condition of satisfying... N L + N H = N Under these conditions, distribution is carried out on the cylindrical section of the low-pressure side. N L The perforation array is distributed on the elliptical cylindrical section of the high-pressure side. N H Group of holes. Let... N H If the number is even, calculate the circumferential angle interval between adjacent rows of holes on the cylindrical section on the low-pressure side. Δθ j and the circumferential angle interval between adjacent rows of holes on the elliptical cylindrical section on the high-pressure side. Δθi Among them, subscript i , j Represent the first segment of the elliptical cylindrical surface, respectively. i The first row of holes and cylindrical sections j Columns of holes.

[0030] It should be noted that, as Figure 3 As shown ( Figure 3 The circle in the diagram is used to indicate the location of the opening and does not represent the actual shape of the opening on the top-view cross-section.

[0031] As a preferred embodiment of the present invention, the number of high-pressure side holes... N H For even numbers, the specific hole arrangement in S2 follows these rules: , , , .

[0032] S3, Force Calculation: Based on the results obtained in S2 (including the position and radius of curvature of the holes), calculate the radial force components exerted on valve core 1 by each set of holes on the cylindrical section on the low-pressure side. F j and the radial force component exerted on valve core 1 by each set of holes on the elliptical cylindrical section on the high-pressure side. F i .

[0033] In a preferred embodiment of the present invention, in step S3, the radial force component of the current iteration step... , ;in, , d The area of ​​the circular surface of the flow hole 3 is indicated by the superscript. k This indicates the current iteration number.

[0034] S4: Radial force component obtained from S3 F j and F i Determine the total unbalanced radial force F tot And set the objective function. F tot ≈0 is used as the optimization objective.

[0035] In a preferred embodiment of the present invention, in step S4, the total unbalanced radial force .

[0036] S5: Utilize optimization algorithms (such as gradient descent, Newton's iteration method, particle swarm optimization, genetic optimization, etc.) to... a and β Iterative adjustments were made until... F tot After meeting the set precision or threshold, Δ is then calculated to meet the requirements. θ i .

[0037] S6: If the Δ obtained in S5 θ i If it is less than the set value, then increase. a The value is then iterated through steps S1 to S6 again until the constraint conditions are met (i.e., F tot The optimal hole distribution parameters are approximately 0.

[0038] In a preferred embodiment of the present invention, the clearance between the valve core and the sleeve is less than 0.1 mm to reduce eccentric movement caused by fluid disturbance.

[0039] As a preferred embodiment of the present invention, the above-described method of the present invention can be implemented by a computer program to perform the above-described optimization steps and automatically generate a hole arrangement diagram.

[0040] As a preferred embodiment of the present invention, the flow field inside the control valve can be simulated using CFD technology to estimate the approximate pressure difference between the high-pressure and low-pressure zones, thereby improving design efficiency and saving test costs.

[0041] The optimized design method of the present invention will be specifically illustrated below through examples.

[0042] Example 1 This embodiment takes a DN100 flow-opening DC sleeve control valve as an example, and its basic parameters are as follows: R =50mm, b =50mm, initially selected as long shaft a =55mm. According to relevant literature, the axial fluid force on the valve core of this type of sleeve control valve is along the outlet direction, meaning the pressure on the outlet side is smaller. Therefore, the half-circumference facing the outlet is set as a circle, and the other half as an ellipse. Thus, the cylindrical surface angle range is [90°, 270°], and the elliptical cylindrical surface angle range is [-90°, 90°].

[0043] like Figure 4 As shown, the valve core is optimized through the following steps.

[0044] S1: After CFD simulation of the flow field inside the sleeve control valve, the average pressure of the fluid on the valve core in the high-pressure zone was found to be 1.2 MPa, and the average pressure of the fluid on the valve core in the low-pressure zone was found to be 0.9 MPa. An upper limit for the allowable axial fluid force was set. ε =100 N, determine the radius of the flow orifice according to the flow requirements. r =2mm, total number of rows of flow holes N =11; Preset basic circumference angle β= 10°.

[0045] S2: Calculate the number of rows of cylindrical and elliptical holes, which are 5 and 6 respectively, with corresponding circumferential angle intervals of 30° and 20° respectively. S3: According to the formula , and Calculate the total unbalanced force F tot .

[0046] S4: Using Newton's iteration method F tot The solution is performed iteratively to find the value closest to zero and the optimal basic inscribed angle for the current iteration. β (k) .

[0047] S5: If there is no solution or the circumferential angular interval Δ of the hole array on the elliptical cylinder in the result is not found. θ i If the angle is less than 10°, increase the major axis by 2mm and return to step S1 for iterative solution.

[0048] The calculations are performed according to the steps above to obtain the final optimized parameters, which are some of the process quantities, as shown in Table 1.

[0049] Table 1 As shown in Table 1, by considering the length of the major axis of the elliptical cylinder... a and basic inscribed angle β Through iterative optimization, the theoretical radial unbalanced force of the valve core in this embodiment is reduced from the initial approximately 450 N to 65.2 N, a reduction of approximately 16.94% compared to before optimization, and is far less than the set upper limit of 100 N.

[0050] The embodiments described above are merely preferred embodiments of the present invention and are not intended to limit the invention. Those skilled in the art can make various changes and modifications without departing from the spirit and scope of the invention. Therefore, all technical solutions obtained through equivalent substitution or transformation fall within the protection scope of the present invention.

Claims

1. A control valve sleeve structure for preventing jamming, characterized in that, It includes a valve core (1), a sleeve (2), a flow hole (3), and an actuator connection part (4); The valve core (1) is slidably connected to the inside of the sleeve (2). The circumferential side of the valve core (1) is composed of an elliptical cylindrical section and a cylindrical section. The minor axis of the elliptical cylindrical section is equal to the radius of the cylindrical section, making the circumferential side of the valve core (1) a smooth structure. The elliptical cylindrical section of the valve core (1) is the high-pressure side, and the cylindrical section is the low-pressure side. The sleeve (2) is provided with several rows of holes along the circumference. Each row of holes includes several flow holes (3) that are opened vertically at intervals. The rows of holes on the low-pressure side are evenly distributed along the circumference. The rows of holes on the high-pressure side are distributed at equal circumferential angles and are generally biased towards the minor axis of the elliptical cylindrical section to form a basic circumferential angle. β This ensures that the radial force exerted on the valve core (1) by the fluid throughout the entire stroke is approximately balanced, thereby reducing the risk of jamming.

2. The anti-jamming control valve sleeve structure according to claim 1, characterized in that, The valve core (1) is provided with an actuator connection part (4) for connecting an external drive device. The drive device enables the valve core (1) to slide up and down along the inner wall of the sleeve (2) to change the opening status of the flow hole (3) and achieve flow regulation.

3. The anti-jamming control valve sleeve structure according to claim 1, characterized in that, The wall of the flow hole (3) is perpendicular to the wall of the sleeve (2).

4. The anti-jamming control valve sleeve structure according to claim 1, characterized in that, When the valve core (1) is in the lower limit position, it can block all the flow holes (3); when the valve core (1) is in the upper limit position, it can fully open all the flow holes (3).

5. An optimized design method for the anti-jamming control valve sleeve structure as described in any one of claims 1 to 4, characterized in that, Specifically as follows: S1: Set the length of the major axis including the elliptical cylindrical segment. a Length of the minor axis of the elliptical cylindrical segment b Flow hole (3) radius r Total number of holes N Basic inscribed angle β High-pressure side pressure p h and low-pressure side pressure p l Initial pore distribution parameters, including those included; S2: Distributed on the cylindrical section on the low-pressure side and the elliptical cylindrical section on the high-pressure side respectively. N L Group of holes and N H A set of holes, and satisfying... N L + N H = N ;make N H The value is even, and the circumferential angle interval between adjacent hole rows on the low-pressure side cylindrical section and the high-pressure side elliptical cylindrical section is calculated respectively. Δθ j and Δθi ; where subscript i , j Represent the first segment of the elliptical cylindrical surface, respectively. i The first row of holes and cylindrical sections j perforated; S3: Based on the results obtained in S2, calculate the radial force component exerted on the valve core (1) by each group of holes on the cylindrical section on the low-pressure side. F j and the radial force component exerted on the valve core (1) by each set of holes on the high-pressure side elliptical cylindrical section. F i ; S4: Radial force component obtained from S3 F j and F i Determine the total unbalanced radial force F tot And set the objective function. F tot ≈0 is used as the optimization objective; S5: Utilize optimization algorithms to... a and β Make iterative adjustments until... F tot After meeting the set precision or threshold, Δ is then calculated to meet the requirements. θ i ; S6: If the Δ obtained in S5 θ i If it is less than the set value, then increase. a The values ​​are iterated again through steps S1 to S6 until the optimal hole distribution parameters that satisfy the constraints are obtained.

6. The optimization design method according to claim 5, characterized in that, The specific formula for calculating S2 is as follows: ， ， ， 。 7. The optimization design method according to claim 5, characterized in that, In S3, the radial force component of the current iteration step , ;in, , d The area of ​​the circular surface of the flow hole (3) is indicated by the superscript. k This indicates the current iteration number.

8. The optimization design method according to claim 5, characterized in that, In S4, the total unbalanced radial force .

9. The optimization design method according to claim 5, characterized in that, In S1, the flow field inside the control valve is simulated using CFD technology to estimate the pressure difference between the high-pressure side and the low-pressure side, which serves as a reference for the distribution orifice array in S2.

10. The optimization design method according to claim 5, characterized in that, In S1, the initially set major axis length of the elliptical cylindrical segment a Not exceeding 1.5 times the minor axis length of the elliptical cylindrical segment b .

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