Global valve valve body flow path

Abstract

To provide a valve body flow path for a global valve with a low head loss coefficient ξ that meets ESG requirements. [Solution] A valve inlet and valve outlet are installed on both sides of the valve body, and a valve plug and valve seat installed in the valve chamber open and close. The inlet flow path includes the valve inlet and an inlet center line S1 which is a smooth streamline, and the fluid flows in horizontally, then is turned upward at a turning angle A of 55°≦2θ1≦105° and flows out from the central hole of the valve seat. The outlet flow path includes the valve outlet, an inner outlet, and an outlet center line S2 which is a smooth streamline that is diagonally downward. When the valve plug is opened, a radial flow path is formed between the bottom of the valve plug and the valve seat, the fluid flows out from the central hole, is turned at a turning angle B, enters the radial flow path, undergoes radial flow and diffuses C, and jet S 121 and slow flow S 122 It includes and enters the inner outlet at a turning angle D, then mixes in the outlet flow path, and 30°≦2θ 21 It flows out from the valve outlet at a deflection angle E of ≤90°.

Description

[Technical Field]

[0001] Global Valve offers control valves commonly used in pipeline systems, characterized by high sealing reliability, ease of flow adjustment, and cleanliness / residue-free operation, making them widely popular. Diaphragm valves, in particular, are especially well-suited for high-cleanliness applications and can be used to limit flow or pressure in pipeline systems. However, their drawback is that they require a relatively high pressure difference to achieve the same flow rate. Commonly seen valves can be distinguished using obturators. The first type seals using an elastic member, such as a pinch valve or a weir valve. The second type seals using a swivel member, such as a butterfly valve or a ball valve. The third type seals using a sliding member, such as a gate valve. The fourth type seals using a cover / shielding member, such as a global valve or a needle valve. The fifth type seals by deformation using an elastic piece, such as a weir valve. The flow performance of the five types of valves described above is determined by the flow coefficient C, which includes dimensions. V Value and K V It may be described using a value (flow coefficient), or it may be described using the dimensionless pressure loss coefficient ξ. For related definitions, see Reference 2 (Chapter 1, General Information, 1-1 General Guidelines, Term 8 and Term 9, P.2), among which C V The larger the value, the greater the flow rate and the smaller the resistance. Conversely, the larger the value of ξ, the greater the resistance and the smaller the flow rate, as shown below. VThe "value" refers to the situation where the diameter of the 2-inch caliber is 47 mm to 57 mm, and when the obturator is fully open, the valve body flow path has the maximum flow rate.

[0002] Type 1 valve: Flow coefficient C of the pinch-valve V The range of the value is 170 to 280, and for the flow coefficient C of the weir-valve V The range of the value is 50 to 120.

[0003] Type 2 valve: Flow coefficient C of the butterfly-valve V The range of the value is 90 to 220, and for the flow coefficient C of the ball-valve V The range of the value is 210 to 500. The obturator of the ball-valve is the central hole of the closing spherical material. If the diameter of the central hole is the same as the pipe diameter of the valve inlet and outlet, it is called a full port valve and has a high flow coefficient C V It has the characteristics of the value. Since its valve body flow path is in a straight pipe shape, when the fluid flows, its streamline is a straight line and it hardly receives obstacles. Therefore, its C V value can reach up to 500. If the central hole is smaller, the smaller its C V value will be, and its C V value may only be 210.

[0004] Type 3 valve: Flow coefficient C of the gate-valve V The range of the value is 100 to 300.

[0005] Type 4 valve: Flow coefficient C of the global valve with a vertical axis V The range of the value is 30 to 65. Among them, when the inlets and outlets are arranged in a straight line, referring to Figure 1, p.2 of Reference 3, C VThe range of values ​​is 40 to 60, and if we take an example with an inner diameter of 52.5 mm, the range of the head loss coefficient ξ is 4.5 to 10.13, and when the inlet and outlet are at a right angle, C V The range of values ​​is 60 to 100.

[0006] C of each of the above types of valves V The value is still affected by the actual pipe diameter, and when comparison is needed, the actual pipe diameter dimensions are required, and C is calculated based on the same pipe diameter. V The difference in value indicates the presence or absence of obstruction to the streamlines in accordance with the change in the flow path cross-sectional area of ​​the valve body, and in particular, the larger the radius of curvature of the streamlines, the greater the C V The value will increase. In addition, C will be triggered depending on the structural differences in application needs. V While the range of values ​​varies among different factory owners, this does not include Y-shaped global valves.

[0007] Fifth type of valve: Flow coefficient C of a weir valve V The range of values ​​is 50 to 116, and as seen in references 5 and 6, the sealing of a wear valve is completed using a single sealing curve, making it relatively difficult to achieve high reliability sealing requirements. However, both the outlet and inlet flow paths can form smooth curved lines, and numerous C V The values ​​can all reach 60-80, and the patents in Reference 5 and Reference Case 9 are C V The design allows the value to reach a level of 110-116, with a pipe diameter of 57 mm and a head loss coefficient ξ of 1.7, while the diameter of Reference 6 is 47.8 mm and its head loss coefficient ξ is 4.47.

[0008] The goal of this innovation in valve flow path is to improve the internal flow path of the vertical axis global valve, as well as the well-known conventional C VInstead of a numerical value, the dimensionless head loss coefficient ξ is used as the improvement index, the inlet and outlet are assumed to be a straight line of 2 inches (52.5 mm), and the innovation is explained using a global valve as the target. The goal of the innovation is to improve the conventional valve body flow path. For example, if the inner diameter of the 2-inch valve is 52.5 mm and the inner diameter ratio d3 / d0 = 2.0, then this innovation pursues the head loss coefficient ξ of the valve body flow path to 1.7 ≤ ξ ≤ 3.0 and 100 ≥ C V It satisfies the condition of ≥73.5 and surpasses the effectiveness of conventional global valves. [Background technology]

[0009] The present invention relates to a dimensional flow coefficient C V Value or K V This paper uses the value as a reference indicator to explain the improvement effect of the valve body flow path of the global valve, and attempts to accurately explain the improvement effect by also citing the value of the dimensionless head loss coefficient ξ. In valves with the same structure, the head loss coefficient ξ decreases in stages due to the increase in the diameter, and the difference between these two values ​​lies in the unit, C V Q is the US system flow rate Q under a pressure difference of 1 psig, and its unit is usgpm, while K V This is the flow rate Q in meters under a pressure difference ΔP = 1 bar, and its units are cmh and m. 3 It is / hour, and after both units are converted, C V Value or K V The value is a dimensional coefficient that has a positive correlation with the pipe cross-sectional area, therefore C V The value is K V The value is 1.156 times, and valves from different manufacturers have the same C V Value or identical K V When a value exists, there is a fairly high probability that the head loss coefficient ξ will have different values ​​depending on the difference in the inner diameter of the pipe, and the lower the value of the head loss coefficient ξ, the more it represents a truly reduced head loss, and the energy required for pipeline transport is truly reduced, and many valve manufacturers, m 3 / hr is used with K VBy displaying the values, users of the valve can easily and simply select and use them, as shown below.

[0010]

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[0011]

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[0012] This type of pressure difference ΔP between the valve inlet and outlet is also called head loss, and the flow coefficient C V Value or K V A higher value indicates that more flow rate can be transported in proportion to a given pressure difference, which is highly advantageous for meeting the energy-saving needs of low-head transport in pipeline systems.

[0013] The present invention can also introduce a dimensionless head loss coefficient ξ as an indicator to explain the more precise improvement effect of the valve body flow path of the global valve. The value of the head loss coefficient ξ is expressed as follows, using the pressure difference ΔP (pa) and the average flow velocity V of the pipeline.

[0014]

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[0015]

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[0016] ΔH L(m) is the water level difference and is used to describe the head loss. ξ in the equation is a dimensionless coefficient and is called the head loss coefficient, which is independent of the dimensionless coefficient of the pipe size. This coefficient is exactly equal to the value of the pressure loss coefficient ξ and can reflect the pressure loss coefficient of the internal flow path structure of the valve body. Furthermore, it can serve as a reference for determining the superiority or inferiority of the design of different internal flow path structures. Valve body flow paths with similar structures can obtain the same value of ξ, and the lower the value, the less head loss there is, the greater the flow rate, and the dynamic pressure in the pipe becomes 1 / 2 × ρ × V 2 P that satisfies the following conditions d It can also be considered as the average dynamic pressure of the streamlines in the pipe, and the relationship between the magnitudes of the pressure difference ΔP(pa) is given by the dynamic pressure P using ξ. d It may also be expressed as a multiple of ΔH, and the water level difference ΔH L (m) is the head loss, and is 1 / 2g × V 2 =H d The conditions are met, H d This is precisely dynamic head, and such head loss ΔH L (m) is the dynamic head H using ξ. d It may also be expressed as a multiple of , and each component of the internal flow path of the valve body can be, for example, a straight pipe, a curved pipe, or a right-angled pipe, each of which has its own head loss coefficient ξ, and the larger the head loss coefficient ξ, the smaller the radius of curvature of the streamlines in the pipe becomes and the less smooth it becomes. Furthermore, the head loss occurring in the components of a single pipeline connected in series can be expressed as the overall pipeline head loss coefficient ξ by adding the values ​​of ξ together. For more detailed information, please refer to Non-Patent Documents 1 and 2, which describe the associated flow loss coefficients. In Non-Patent Document 1, the symbol K is used. b The head loss coefficient is expressed using the symbol ξ, while in Non-Patent Document 2, the head loss coefficient is expressed using the symbol ξ, and in this specification, the head loss coefficient is expressed using ξ.

[0017] Although the calculation of the head loss coefficient ξ is dimensionless and independent of the pipe diameter, in practice, the fluid flow pattern within the pipe is related to the head loss coefficient ξ, and the larger the pipe diameter, the greater the radius of curvature R of the streamlines. C As this increases, the larger the pipe diameter, the lower the head loss coefficient ξ should be, and Non-Patent Literature 2 (Chapter 9 Flow through pipe fittings and labyrinth seals, Resistance Coefficients of Throttling Devices, Valves, Plugs, and Labyrinth Seals, Diagram 9-4, Standard glove valve with dividing wall, Dividing walls at angle 45°, curve 1, Table 1, D0=13mm, ξ=10.8, D0=80mm, ξ=4.0, p.290) is taken into consideration.

[0018] The formula for calculating the value of the head loss coefficient ξ is used, C V Value conversions can be performed, and examples of these formulas are shown below.

[0019]

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[0020]

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[0021]

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[0022]

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[0023] From the formula described above, the flow coefficient C V Value or K VThe value may be understood as being associated with the pipe cross-sectional area A, and when selecting and using a valve, it allows engineers to easily and intuitively understand the magnitude of the flow rate, but C V When comparing values, it is essential to clearly indicate the magnitude of the pipe diameter d0; otherwise, there is a risk of misjudging the true flow performance. Furthermore, the dimensionless head loss coefficient ξ can more accurately reflect the actual flow performance regardless of the pipe diameter, and can accurately reflect the head loss ΔP. ​​In this paper, the head loss coefficient ξ is adopted as an indicator for improving the valve body flow path.

[0024] Regarding the structure of the flow path of conventional global valves, refer to Non-Patent Documents 2 and 3. The flow path structure disclosed in Non-Patent Document 2 may be divided into structure C1, structure C2, and structure C3, while the flow path structure disclosed in Non-Patent Document 3 is structure C4.

[0025] Figure 13A shows the coordinate axes, coordinate points, and inlet centerline S1 and radial centerline S of the conventional structure C3 flow path. 12 , jet S 121 , slow flow S 122 This is a schematic diagram showing the exit centerline S2.

[0026] Figure 13B is a schematic diagram showing the mounting angle, turning angle A, turning angle B, diffusion C, turning angle D, and turning angle E of the flow path in the conventional structure C3.

[0027] Figure 14A shows the coordinate axes, coordinate points, and inlet centerline S1 and radial centerline S of the conventional structure C4 flow path. 12 , jet S 121 , slow flow S 122 This is a schematic diagram showing the exit centerline S2.

[0028] Figure 14B is a schematic diagram showing the channel turning angles A, B, diffusion C, D, and E of the conventional structure C4.

[0029] The valve body of a conventional global valve has a hollow structure containing a flow path, similar in shape to a sphere or cylinder. The structure of the flow path consists of a valve chamber, a valve plug, an inlet flow path, an outlet flow path, and a partition plate. The partition plate is used to separate the inlet flow path and the outlet flow path, and a valve seat is mounted on the horizontal surface of the partition plate. The valve seat has a sealing surface and a central hole. The inlet flow path has a valve inlet connected to the central hole. The valve seat has a concentric valve plug, valve stem and sealing device mounted inside it, and the partition plate and the valve seat are mounted on it. The valve is used to connect the inlet flow path and the outlet flow path, and an inner outlet is provided in the diameter of the valve chamber. The outlet flow path has a valve outlet connected to the inner outlet. The valve inlet and the valve outlet are connected to the valve body. Flow channel When installed on both sides, and the outlet flow path is a straight pipe or a curved pipe of the type that is angled downwards, the inner outlet is a non-standard ellipse.

[0030] Let the valve chamber diameter be d3, the valve plug outer diameter be d2, the valve seat outer diameter be d1, the valve inlet diameter be d0, and the valve outlet diameter be d0.

[0031] Let LH1 be the height of the center point P1 of the central hole, LH2 be the height of the center point P3 of the inner outlet, LH3 be the height of the sealing surface of the valve seat, and P be the height of the center point of the sealing surface. DP Let P2 be the center point of the valve inlet and P4 be the center point of the valve outlet.

[0032] The horizontal line XL1 passes through the center point P1 of the central hole, and the horizontal line XL1 and the circumference of the central hole intersect at two points, the distal point E1 and the proximal point E2, where the distal point E1 is located on the side of the valve inlet and the proximal point E2 is located on the side of the valve outlet.

[0033] The pipe axis XL2 (X-axis) passes horizontally through center point P2 and center point P4. The height indication of this innovation is based on the pipe axis XL2 connecting the valve outlet and the valve inlet, and the zero point of the Y-axis coordinate indicates the position relative to the pipe axis XL2, with positive values ​​(>0), zero (=0), and negative values ​​(<0).

[0034] The vertical line YL1 passes through the center point P1 and intersects with the pipe axis XL2 at point P 11 They intersect with each other.

[0035] The vertical line YL2 passes through the center point P4, and the vertical line YL2 and the circumference of the valve outlet intersect at two points, the distal point E5 and the proximal point E6. The height of the distal point E5 is d0 / 2, and the height of the proximal point E6 is -d0 / 2. The proximal point E6 is the lowest point of the outlet flow path.

[0036] The vertical line YL3 passes through the center point P3 and intersects with the pipe axis XL2 at point P 31 They intersect each other, and the vertical line YL3 and the circumference of the inner exit intersect each other at the two intersection points of the distal point E3 and the proximal point E4, with the height of the distal point E3 being LH4 and the height of the proximal point E4 being LH5.

[0037] The vertical line YL4 passes through the center point P2 and intersects with the circumference of the valve inlet at two points: the distal point E7 and the proximal point E8. The height of the distal point E7 is d0 / 2, and the height of the proximal point E8 is -d0 / 2. The proximal point E8 is the lowest point of the inlet flow path.

[0038] There is a horizontal distance L1 between center point P1 and center point P2, P 11 The condition P2 = L1 is satisfied, and there is a horizontal distance L2 from the center point P4 to the center point P1, and P4P 11 The condition = L2 is satisfied, there is a horizontal distance L from center point P2 to center point P4, and the condition P4P2 = L = L1 + L2 is satisfied.

[0039] The horizontal distance LL2 is between center point P4 and center point P3, and LL2 = L2 - d3 / 2 = P 31 The conditions for P4 are met.

[0040] The valve plug is cylindrical and has a flat surface at its bottom. When the global valve is closed, the valve plug is used to seal with the sealing surface. When the valve is fully open, a radial flow path with an opening of B1 is formed between the bottom surface of the valve plug and the sealing surface. The radial flow path is a conical flow path whose structure is influenced by the structure of the sealing surface, resulting in either a horizontal flow path or a 45° upward-angled flow path. In a preferred embodiment, if the flow path is horizontal, the condition B1 / d0 = 0.25 is satisfied.

[0041] The inlet passage comprises the valve inlet, the inlet center line S1, the central hole, and the upper edge line S 1a And the lower edge line S 1b This includes the following. The inlet passage enters horizontally from the valve inlet and is bent upward, and its outlet end is the central hole, the inlet center line S1 connects center point P1 and center point P2, and has an angle γ1 between center point P1 and the vertical line YL1, and when the angle γ1 ≠ 0°, the central hole is a non-standard elliptical hole, with the major axis a in the X-axis direction x It has, a x ≥d0, a x The conditions =E1E2 and E1P1≧P1E2 are satisfied, and the minor axis b in the Z-axis direction. z It has, b z When the condition = d0 is satisfied and the included angle γ1 = 0°, the central hole is a hole with diameter d0. The upper edge line S 1a The distal point E1 and the distal point E7 are connected, and the lower edge line S 1b This connects the proximal point E2 and the proximal point E8.

[0042] The radial flow channel has a radial center line S 12 The radial flow path includes an opening B1, and the radial flow path surrounds the flow path radiating from the central hole, with a height of LH6, satisfying the condition LH6 = LH3 + B1. Radial center line S 12 It connects center point P1 and center point P3, and from center point P1, it flows out in different directions in a radial manner, finally connecting to center point P3.

[0043] The aforementioned outlet passage comprises the inner outlet, the valve outlet, the outlet centerline S2, and the upper edge line S 2a And the lower edge line S 2b This includes the following. The outlet center line S2 connects center point P3 and center point P4, and has an angle γ2 between center point P3 and the vertical line YL3, satisfying the condition 0° ≤ γ2 < 90°, and when the inner outlet is a non-standard elliptical hole, the major axis a in the Y-axis direction. y It has, a y ≥d0, a y The conditions =E3E4 and E3P3≧P3E4 are satisfied, and the minor axis b in the Z-axis direction. z It has, b z When the condition =d0 is satisfied and the outlet flow path is a horizontal straight pipe, let the angle be γ2, and γ2 = 90°, a y The condition =d0 is satisfied. The upper edge line S 2a The distal point E3 and the distal point E5 are connected, and the lower edge line S 2b The proximal point E4 and the proximal point E6 are connected. The distal point E3 has a height difference H1 with respect to the sealing surface and satisfies the condition H1 = LH4 - LH3, and satisfies the condition H1 ≥ 0 when the distal point E3 is higher than the sealing surface, and H1 ≤ 0 when it is lower than the sealing surface. The center point P3 of the inner outlet has a height difference H3 with respect to the sealing surface and satisfies the condition H3 = LH2 - LH3, and satisfies the condition H3 ≥ 0 when the center point P3 is higher than the sealing surface, and H3 ≤ 0 when it is lower than the sealing surface.

[0044] The radial clearance B3 is located between the outer diameter d2 of the valve plug and the inner diameter d3 of the valve chamber, and satisfies the conditions of B3 = (d3 - d2) / 2 and 0.2 ≤ B3 / d0 ≤ 0.4. When B3 / d0 is too small, there is a problem that a stagnant space is generated in the valve chamber space above the valve plug, causing particle aggregation. The annular space B2 is between the outer diameter d1 of the valve seat and the inner diameter d3 of the valve chamber, and satisfies the condition of B2 = (d3 - d1) / 2 and 0.25 ≤ B2 / d0 ≤ 0.4. Taking the inner diameter ratio as d3 / d0, the ratio of the inner diameter d3 of the valve chamber to the valve inlet diameter d0 satisfies the condition of 1.75 ≤ d3 / d0 ≤ 2.2. The size of the valve body has a positive correlation with the inner diameter ratio d3 / d0. The larger the inner diameter ratio d3 / d0, the larger the curvature radius of the fluid, but there are problems that the volume becomes too large and the cost becomes excessively high.

[0045] Regarding the description of the valve body flow path and the fluid flow phenomenon, as follows, the terms "bending" or "flexure" are used to describe the change in the flow direction of the streamline S. Hereinafter, three center lines such as the inlet center line S1, the radial center line S 12 and the outlet center line S2 are shown as streamlines, and the description of the bending angles of these is limited only to those based on the inferable geometric shapes. To obtain further descriptions, it is necessary to use complex 3D-CFD calculations.

[0046] As the inlet center line S1, the inlet center line S1 may be a single line segment or a combination of several types of line segments. The types of line segments include arc curves, vertical line segments, diagonal line segments, horizontal line segments, etc. Among them, the vertical line segment is coaxial with the vertical line YL1, and the horizontal line segment is coaxial with the pipe axis line XL2. The inlet center line S1 has a turning angle A, and a point P 12 is provided on the pipe axis line XL2. One end of the diagonal line segment or the arc curve and the pipe axis line XL2 are 12 connected to each other at point P 12 One end of the arc curve and the pipe axis line XL2 are tangent to each other at point P 12 connected to each other at point P 12 12Draw a vertical line YL6 by passing through it, and take a point P0 on the vertical line YL6 to make the line segment P0P 12 and the line segment P0P1 have equal lengths, and the included angle 2θ1 between the line segment P0P 12 and the line segment P0P1 is equal to the turning angle A, and the mounting angle θ1 is equal to the horizontal included angle of the line segment P1P 12 . When the point P 12 and the point P2 overlap, it represents that the inlet flow path is a single arc curve or a single diagonal line segment.

[0047] The radial center line S 12 is such that all the streamlines after the fluid flows out of the central hole flow out in different directions in a radial manner and enter the radial flow path. The turning angle B is the bending angle between the inlet center line S1 and the radial center line S 12 . All the streamlines all flow through the radial flow path and the annular space B2 and undergo diffusion C, and flow towards the inner outlet no matter how many bends are made. The radial center line S 12 is such that the flow velocity of the fluid undergoing diffusion C decreases due to the increase in the area of the radial flow path after applying the turning angle B, but when flowing towards the inner outlet after several bends, it also accelerates due to the area reduction. The radial center line S 12 is affected by the relative position between the sealing surface and the inner outlet and may be a straight line or an arc, or may be a multi-curved arc.

[0048] The radial center line S 12 is driven by the pressure difference between the valve inlet and the valve outlet. Therefore, the radial center line S of the diffusion C 12 may be divided into a jet flow S 121 and a slow flow S 122 . The high-density streamlines receiving a high pressure difference gradient are the jet flow S with a relatively high flow velocity 121 , and the low-density streamlines receiving a low pressure difference gradient are the slow flow S 122 with a slightly lower flow velocity. The radial center line S 12 is such that the streamlines of the flow expand fan-shaped in the circumferential direction and are affected by the turning angle B. The jet flow S 121It spreads out in a fan shape toward the inner outlet, and slow flow S 122 is a jet S 121 The sector unfolds into a circular angle other than the sector unfolding angle, and some of the jet S 121 The remaining jet S flows directly into the inner outlet. 121 and slow flow S 122 The valve chamber is divided into two branches, and the fluid repeatedly reverses direction along its inner diameter before entering the inner outlet. Radial centerline S 12 is a jet S 121 and slow flow S 122 Before the diffusion C flows and the jet S flows into the inner outlet, both are given different deflection angles D, and the jet S 121 This involves applying a turning angle D1 and creating a slow flow S 122 The jet S is directed with a deflection angle D2. 121 and slow flow S 122 This causes varying degrees of flow interference due to the influence of the internal structure of the valve chamber, and depending on the severity, the head loss increases.

[0049] The outlet centerline S2 may be a single line segment or a combination of several line segments, and the types of line segments include circular arcs, diagonal line segments, and horizontal line segments, of which the horizontal line segments are coaxial with the pipe axis XL2. The turning angle D of the outlet centerline S2 is the radial centerline S 12 The bending angle between the outlet center line S2 and the inner outlet is such that the fluid flows out of the valve outlet after being subjected to a deflection angle E within the inner outlet and the outlet flow path, and the bending at the deflection angle D causes a head loss, and the serious head loss is due to the jet S at the inner outlet. 121 and slow flow S 122 It occurs due to flow interference between the two. The outlet center line S2 is on the pipe axis XL2, point P 34 A point is provided, and one end of the diagonal line segment and the pipe axis XL2 are at point P 34 They are connected to each other, or one end of the circular arc curve and the pipe axis XL2 are at point P 34 The turning angle E is generated only when the lines are tangent and consist only of circular arcs and diagonal line segments. The combination of line segments is suitable for casting or forging depending on the situation. If the exit center line S2 is a single circular arc or a single horizontal line, it is applicable to injection molding, and point P 34By passing through and drawing the vertical line YL5, and by taking point P5 on the vertical line YL5, the line segment P5P 34 And make it possible to make the line segment P5P3 equal in length, and the line segment P5P 34 The angle 2θ2 between and line segment P5P3 is equal to the turning angle E, and the angle of attachment θ2 is equal to line segment P3P 34 The angle of the horizontal junction is equal to the angle of the curve, and the flow of the arc has an even higher lift loss than the curved diagonal, so the diagonal line segment is at point P 34 It has a large horizontal elbow angle θ2, which increases some head loss and small circulating flow sections, point P 34 When point P4 is superimposed, it indicates that the inlet channel is a single circular arc or a single diagonal line segment.

[0050] The deflection angle A refers to the bending angle of the inlet center line S1. When fluid flows in from the horizontal valve inlet and enters the central hole upwards with a deflection angle A, the head loss coefficient ξ can reach 1.0 when the deflection angle A is right angle. Non-patent document 2 (page 169, diagram 6-5, Elbow without recess) shows that a right angle deflection angle A generates several circulating flow sections N within the inlet flow path, of which a large circulating flow section N is generated near the central hole, and the blockage of the flow path cross-sectional area becomes severe, improving the head loss. With a deflection angle A, when the deflection angle A < 90°, the condition of the included angle γ1 > 0 is satisfied, and the sealing surface of the valve seat in the horizontal plane of the central hole is a non-standard ellipse. When the diameter of the central hole is corrected to d0, the major axis a x The reduction ratio is d0 / a x Let d0 / a x The condition <1.0 is met.

[0051] The turning angle B is defined as the ratio of the entrance centerline S1 to the radial centerline S 12 This refers to the bending angle between the two, where the fluid flows upward from the central hole, enters the horizontal radial flow path with a deflection angle B, and flows in the radial direction around the circumference, and a large amount of fluid in the radial flow path flows in a direction that deflects toward the inner outlet, and when the angle γ1 > 0° and the deflection angle B < 90°, the effective cross-sectional area of ​​the flow path becomes smaller, C VThe value will also decrease. At a turning angle B, the turning angle B is affected by the turning angle A, and in particular when a large circulating flow section N is generated in the inlet flow path, it inevitably causes a shift in the streamlines, and is therefore affected by the angle of the turning angle B. When the sealing surface is an obliquely upward-facing conical surface, for example, when the turning angle B = 45°, the radial flow path can be made into a conical flow path, and the jet S 121 The material flows diagonally upward and enters the large space of the valve chamber. The flow of this diffusion C must undergo many bends in order to allow it to flow into the inner outlet, resulting in a large head loss and interference of the flow within the valve chamber.

[0052] Diffusion C is along the radial center line S 12 The distribution of streamlines S and the change in flow velocity when the fluid flows through the radial channel and the annular space B2, and the jet S 121 It enters the radial flow channel on the side closest to the inner outlet from the central hole, diffuses in a fan shape, and slows down the flow S 122 It flows out from the central hole in the other circumferential directions, enters the radial flow channel in the circumferential direction, and diffuses in a fan shape, and slow flow S 122 The water is divided into two branches within the valve chamber, and flows in a spiral pattern, repeatedly reversing direction along the circumference of the valve chamber diameter in the opposite direction to the circumference, before each branch enters the inner outlet, and a portion of the jet S 121 The remaining portion of the jet S flows directly toward the inner outlet. 121 It is also divided into two branches, and flows along the circumference of the valve chamber diameter toward the inner outlet, forming a jet S 121 and slow flow S 122 This causes mutual flow obstruction within the valve chamber, resulting in additional head loss. When diffusion C is ejected diagonally upward with a deflection angle B of 45°, the jet S 121 This causes additional head loss when the jet enters the inner outlet after being bent multiple times, and if the inner diameter ratio d3 / d0 is too small, the jet S 121 and slow flow S 122This causes mutual flow interference within the valve chamber, resulting in additional head loss. When the radial flow path is horizontal, the fluid velocity smoothly decreases due to the linear increase in the cross-sectional area of ​​the radial flow path and the annular space, and the fluid flow is also bent due to the constraint of the valve chamber diameter.

[0053] The angle of deflection D is the radial center line S. 12 This refers to the bending angle between the radial center line S2 and the exit center line S2. 12 The angle of deflection D between the jet S and the outlet center line S2 may be described using 2θ2, 2θ2 = 90° - γ2. The streamlines of the diffusion C are bent from the radial flow path and the annular space, and the streamlines before entering the inner outlet, or more clearly, one bend or multiple bends, are formed in the jet S 121 The angle of change D1 and the slow flow S 121 This includes the angle of deflection D2. The angle of deflection D1 is the jet S 121 The angle of inclination between the streamline and the outlet center line S2 of the inner outlet, and the jet S 121 The bending angle from the bend that occurs in the diffusion C to the inner outlet, and a portion of the jet S 121 The angle of deflection D2 includes the bending angle at which the flow directly penetrates the inner outlet and flows toward the valve outlet. 122 This is the angle of inclination between the streamline and the outlet center line S2 of the inner outlet, and slow flow S 122 This includes the bending angle from the bend occurring in diffusion C to the inner outlet. If the outlet center line S2 is a diagonal line at the turning angle D, the turning angle D is θ2, and if the outlet center line S2 is a circular arc, the turning angle D is 2θ2, and depending on the turning angle D of this part, the jet S 121 This causes a loss of head. The angle of deflection D is the jet S 121 The angle α1 between the outlet center line S2 and the slow flow S 122 The angle α2 between the outlet center line S2 and the jet S 121 and slow flow S 122 This is the angle that includes the angle α3 of the streamline between and , and the smaller the angle α1, angle α2, and angle α3 are, the lower the head loss coefficient ξ becomes, and the higher the angle α3 is, the higher the jet S 121 and slow flow S 122This indicates that the flow interference loss at the aforementioned internal outlet between the two is high, and the descriptions of the included angles α1, α2, and α3 can only be intuitively described using geometric structures. It is not possible to quantify and describe such 3D streamline structures using precise numerical values, and if a more detailed description is required, it is necessary to use 3D-CFD calculation software as an aid.

[0054] When the conditions are met at a turning angle D, the center point P3, the sealing surface, and the pipe axis XL2 are at the same height, the outlet flow path is a horizontal straight pipe, and the turning angle D1 = 0°, the jet S 121 The material enters the inner outlet directly and flows horizontally toward the center point P4, satisfying the conditions H1>0, H3=0, and LH3=LH2=0 (referred to as structure C2).

[0055] When the conditions are met at a turning angle D, the proximal point E4, the sealing surface, and the pipe axis XL2 are at the same height, the outlet flow path is a curved pipe sloping downwards, and the turning angle D1 = 0°, the jet S 121 The fluid enters the internal outlet directly and flows horizontally toward the distal point P4, satisfying the conditions H1>0, H3>0, LH3=0, and LH2>LH3 (referred to as structure C1).

[0056] At the turning angle D, the proximal point E4 is at the same height as the sealing surface and higher than the pipe axis XL2, the outlet flow path is a curved pipe that is angled downwards, and satisfies the conditions of turning angle D1 = 90° - γ2, H1 > 0, H3 > 0, LH3 > 0, and LH2 > LH3 (referred to as structure C3).

[0057] When the partition plate of the valve body is changed to an annular groove at a deflection angle D, the annular groove is located below the annular space, and the inner outlet is mounted on the inner wall of the annular groove, The outlet passage is a horizontal straight pipe, the distal point E3 is lower than the sealing surface, and the center point P3 is at the same height as the center point P4 of the valve outlet, and the jet S 121 The jet S enters the annular groove with a first downward turning angle D1 = 90°, and the jet S 121When the material enters the aforementioned inner outlet, a second turning angle D1 = 90° is applied, and it flows horizontally toward the center point P4, satisfying the conditions H1 < 0, H3 < 0, LH1 > 0, and LH2 = 0 (referred to as structure C4).

[0058] The deflection angle E refers to the bending angle of the outlet center line S2, and the jet S 121 and slow flow S 122 This includes applying a turning angle D1 and a turning angle D2 before entering the outlet passage, mixing within the outlet passage, and then bending before being discharged from the valve outlet. After the fluid enters the inner outlet, it flows toward the valve outlet, forming a jet S 121 and slow flow S 122 In either case, flow interference is formed within the outlet channel, causing partial head loss. If the outlet center line S2 is a diagonal line, the turning angle E is θ2. If the outlet center line S2 is a circular arc, the turning angle E is 2θ2. If the outlet channel is a horizontal straight pipe, its turning angle E is E=0. The flow in the circular arc has an even higher head loss than the bent diagonal line, so the diagonal line segment is at point P 34 This results in a large horizontal elbow angle θ2, which increases some head loss and the small circulating flow section.

[0059] The valve chamber configuration has four conventional structures, influenced by the position of the sealing surface and the configuration of the partition plate. These four structures include structures C1, C2, C3, and C4, and the partition plate in all four of these structures has a horizontal surface used for installing the valve seat. For the flow patterns of structures C1, C2, and C3, refer to Non-Patent Literature 2 (Chapter 9 Flow through pipe fittings and labyrinth seals, Resistance Coefficients of Throttling Devices, Valves, Plugs, and Labyrinth Seals, Figure 9-1 Flow pattern in throttling and device, (d) global valve, p.284), and the ratios of the relevant numerical values ​​mentioned in the following text were estimated by referring to the ratios in the figure.

[0060] Regarding structure C1, with reference to Non-Patent Literature 2 (Chapter 9 Flow through pipe fittings and labyrinth seals, Resistance Coefficients of Throttling Devices, Valves, Plugs, and Labyrinth Seals, Diagram 9-4, Standard glove valve with dividing wall, Dividing walls at angle 45°, p. 290), the partition plate around the valve seat has a large inner diameter ratio d3 / d0 of approximately 2.0 at an angle of approximately 45°, has a relatively low head loss coefficient ξ, where ξ = 4.6, the proximal point E4, the sealing surface, and the pipe axis XL2 are at the same height, the outlet flow path is a curved pipe sloping downwards, the radial flow path is a horizontal flow path, the conditions H1 > 0 and H3 > 0 are met, and the angle γ1 = 0° and γ2 = 45°. The structure described in this section applies to metal casting but not to metal forging, nor to injection molding of plastic materials.

[0061] Regarding structure C2, see Non-Patent Literature 2 (Chapter 9 Flow through pipe fittings and labyrinth seals, Resistance Coefficients of Throttling Devices, Valves, Plugs, and Labyrinth Seals, Diagram 9-4, Standard glove valve with dividing wall, Vertical dividing Referring to walls, p.290), the partition plate around the valve seat is of the vertical type and has a small inner diameter ratio d3 / d0 of approximately 1.29, has a relatively high head loss coefficient ξ, ξ=6.9, the center point P3, the sealing surface, and the pipe axis XL2 are at the same height, the outlet passage is a horizontal straight pipe, the radial passage is a 45° conical passage, satisfies the conditions LH3=0, H1>0, H3=0, and the angle γ1=0°, γ2=90°. The structure of this item is applied to metal casting but not to metal forging and not to injection molding of plastic materials.

[0062] Regarding structure C3, referring to Non-Patent Literature 2 (Chapter 9 Flow through pipe fittings and labyrinth seals, Resistance Coefficients of Throttling Devices, Valves, Plugs, and Labyrinth Seals, Diagram 9-1, Various globe and gate valves, "Rey" type global valve, p. 287), the partition plate around the valve seat is spherical with an inner diameter ratio d3 / d0 of approximately 2.0, and has a relatively low head loss coefficient ξ compared to structure C1, with ξ = 3.4, as described in Non-Patent Literature 2, "Rey" type global As shown in the valve drawing, the proximal point E4, the sealing surface, and the pipe axis XL2 are at the same height, the outlet passage is a curved pipe sloping downwards, the radial passage is a horizontal passage, the conditions LH3=0, H1>0, and H3>0 are met, the angle γ1 satisfies the condition γ1=45°, and the angle γ2 satisfies the condition γ2=45°. The structure of this item is applicable to metal casting but not to metal forging and not to injection molding of plastic materials. Regarding another similar structure, a global valve formed solely by metal forging, referencing Non-Patent Literature 2 (Chapter 9 Flow through pipe fittings and labyrinth seals, Resistance Coefficients of Throttling Devices, Valves, Plugs, and Labyrinth Seals, Diagram 9-1, Various globe and gate valves, Forged global valve, p. 287), it is subject to limitations on post-forging processing methods. Its inlet passage is a straight pipe with a deflection angle A having two bends, one of which is angled downwards at approximately 45° before being bent straight upwards, resulting in γ1=0°. Its outlet passage is a straight pipe angled downwards, with γ2=45°. Its head loss coefficient ξ is guided to reach 7.8, which is considerably higher than that of the "Rey" type global valve.

[0063] Regarding structure C4, its external shape is based on Figure 1, p.2 of Non-Patent Literature 3, and its external shape is based on Figure, p.39 of Non-Patent Literature 7, wherein an annular groove is provided in the valve chamber in place of the partition plate to communicate with the outlet passage, both the inlet passage and the outlet passage are straight pipes and installed horizontally, and there is a height difference LH3 between the position of the sealing surface and the pipe axis, the radial passage is a horizontal passage, satisfying the condition LH3>d0 / 2, the horizontal position of the sealing surface is not lower than the outer diameter of the inlet and outlet pipelines, satisfying the conditions H1<0 and H3<0, an annular groove with a width B2 is provided below the annular space, and the position of the sealing surface is higher than the distal point E3 of the inner outlet, When the fluid is discharged from the central hole, an inverted U-shaped circulating flow is created. In the conventional structure C4, the deflection angle A of the inlet channel is right-angled, and it has a relatively high head loss coefficient ξ, where ξ = 1.0 and γ1 = 0°. Looking at Fig. 9.2, p207 of Reference 1, structure C4 has a relatively large inner diameter ratio, and has a relatively low head loss coefficient ξ value of approximately 4.0 to 6.0 compared to structure C2, and the angle γ1 = 0° and γ2 = 90°. While this structure is applied to injection molding of plastic materials, in the structure of a channel for transporting highly clean fluids specifically for semiconductors, there is still a risk of aggregation when transporting granule-containing fluids, and it is also applied to metal casting and metal forging.

[0064] In structures C1, C2, and C3, the inlet channel curves downward from horizontal and then reverses upward at a turning angle A of 90°, and the channel is affected by the structure of the partition plate, and the turning angle A of the inlet center line S1 has three bending angles, the first turning angle A is approximately 45° downward, the second turning angle A is horizontally displaced, and the third angle reverses upward, and the third turning angle A of structure C3 reverses diagonally upward at 45°. Structure C2 has a rapid reduction in cross-sectional area due to the influence of the partition plate on the inlet channel before the entrance to the central hole, resulting in a rapid head loss, the inlet channel of structure C1 has a large space before entering the central hole, resulting in the next largest head loss, and structure C3 maintains a smooth cross-sectional area of ​​the inlet channel, and its inlet center line S1 is a smooth curved line, resulting in the smallest head loss.

[0065] Regarding structure C2, the inner outlet is located in the upper semicircular space of the outlet flow path, and the jet S 121 When the material is injected into the inner outlet, it creates a large circulating flow in the lower semicircular space of the outlet channel, resulting in serious head loss and particle aggregation problems.

[0066] For structures C1 and C3, when the valve seat is fully open, the fluid is ejected horizontally into the radial flow path via a deflection angle B, and its deflection angle D1 is 0°, resulting in a jet S with an opening degree B1. 121 The streamlines are concentrated towards the inner outlet by diffusion C, flowing horizontally from the bottom of the inner outlet, and the angle α1 between the outlet centerline and the stream flows toward the valve outlet at 45°. 121 The area confined to the same height at the base of the major axis of the ellipse has an additional head loss, and the jet S 121 and slow flow S 122 The flow can no longer be divided into the valve chamber, there is partial flow interference, the two merge and enter the upper half of the elliptical inner outlet at a diagonal downward angle of 45° with a deflection angle D2, α2 = 0°, and the jet S 121 and slow flow S 122There is a dramatic high-angle flow interference between the two, with α3 = 45°, and the flow enters the inner outlet, mixes and diffuses in the outlet channel, and then flows out with a deflection angle E.

[0067] Regarding structure C1, jet S 121 The deflection angle D is 0°, but an open-type stagnant flow region is induced in the lower edge elbow pipe region within the outlet flow path.

[0068] Regarding structure C2, the radial flow path of the cone, which is angled upward at 45°, is the jet S. 121 This is caused by a huge change in the flow path cross-sectional area, resulting in a huge head loss. Diffusion C jet S 121 However, in order to allow the horizontal outlet channel to enter the upper half space of the inner outlet, it is still necessary to bend it into an arc shape, but the jet S 121 This induces an open-type stagnant flow area in the lower half of the outlet flow path, and the slow flow S 122 This involves applying conical flow in the other circumferential directions of the valve seat, adding an excessively small ratio of d3 / d0, and creating a jet S 121 and slow flow S 122 This is caused to result in a sudden flow interference within the valve chamber. The area of ​​the inner outlet is 50% of the area of ​​the outlet flow path, resulting in a rapid loss of diffusion and a serious problem of particle aggregation in the open stagnant flow area.

[0069] For structure C3, when the valve seat is fully open, the deflection angle B is 45°, resulting in a larger amount of diffusing C jet S. 121 This helps to concentrate the flow in large quantities toward the side of the inner outlet, and the portion of the jet S 121 The jet S is ejected horizontally, enters the inner outlet having a 45° angle α1 with respect to the outlet centerline, and flows across the space of the outlet channel. 121 and slow flow S 122 This can cause flow interference at the inner outlet, and such flow may also lead to localized circulating flow in the lower half-layer space of the outlet channel, resulting in the remaining jet S 121 and slow flow S 122 The fluid repeatedly reverses direction as it flows within the inner diameter of the valve chamber, resulting in no layered flow and causing flow interference.

[0070] In structure C3, the radial gap ratio B3 / d0 of the valve plug is approximately 0.07, and the valve chamber space above the valve plug is raised to become a stagnant area.

[0071] Regarding structure C4, when the valve seat is fully open, the jet S121 and slow flow S122 are obstructed by the diameter inside the valve chamber and unfold in a large-angle fan shape. After the fluid passes over the outer diameter of the valve seat, both are bent downwards at a 90° turning angle D in the annular groove. The streamlines from turning angle B to turning angle D bend in an inverted U shape and enter the annular groove, flowing towards the inner outlet, and the portion of the jet S 121 and slow flow S 122 The material flows in the annular groove, repeatedly reversing in a spiral pattern, without layered flow, resulting in flow interference. Furthermore, it flows along the slope of the annular groove at an angle β toward the inner outlet, undergoing two turning angles D2 before entering the inner outlet, forming a partial jet S. 121 Furthermore, the jet is then turned horizontally by a second turning angle D1 of 90° and enters the inner outlet, causing a circulating flow section to be generated at the upper inner edge of the outlet flow path of the inner outlet, which easily leads to particle aggregation, and the partial jet S 121 and slow flow S 122 This causes serious flow interference due to the angle of the included angle α3 being excessively large at the internal outlet, and after entering the internal outlet, it is subjected to a turning angle E of 0° and flows out along the horizontal flow path.

[0072] In the four types of valve chamber structures described above, we have already presented each type of structure and the head loss coefficient ξ that can be obtained for each type, and at the same time, we have also presented each type of structure that can reduce the head loss coefficient ξ. Among these, the flow path structure of structure C3 has methods and features that are more suitable for reducing the head loss coefficient ξ, and a relatively low head loss coefficient ξ = 3.4 can be obtained, but it is still not possible to satisfy the goal of this innovation.

[0073] Having achieved its innovation goals, the present invention still needs to satisfy the following limitations. Restriction 1: The valve seat must be capable of providing highly reliable sealing performance. Restriction 2: Entrances and exits must be in the same straight line to simplify pipe installation. Restriction 3: The valve body cannot have cleanliness issues, making it impossible to have sealed retention zones, open retention zones, residual zones, or circulating flow sections, thus avoiding particle aggregation and liquid residue. Restriction 4: The inner diameter ratio of the valve body satisfies the condition 1.75 ≤ d3 / d0 ≤ 2.8. Restriction 5: Since the manufacturing method significantly limits the head loss coefficient ξ of the novel flow path, the structure of the novel flow path of the valve body must clearly specify the manufacturing method and the selection and use of materials. The criteria for comparing the inventiveness of the novel flow path must take into consideration the limitations of the manufacturing method, but minor modifications may be required depending on the different manufacturing methods and the selection and use of materials, and these minor modifications must be explained in the examples.

[0074] The following explains restrictions 1 through 5. In Restriction 1, the limiting conditions of the present invention are characterized by the global valve, and numerous methods are all C V Value or K V The value can be improved. At the same time, it is not possible to provide highly reliable sealing performance. For example, pinch valves, wear valves, and butterfly valves have slightly insufficient sealing reliability. The weakness of pinch valves and wear valves stems from the problem of uneven pressure applied to the diaphragm, while the weakness of butterfly valves stems from the sliding friction between the circumference of the butterfly plate and the valve body. Structures C1, C2, and C3 can provide highly reliable sealing performance only when manufactured using selected metal materials. When molded using plastic materials, the structure needs to be strengthened to meet the requirements for sealing performance. Structure C4 can provide highly reliable sealing performance whether molded using selected plastic materials or manufactured using selected metal materials.

[0075] Even with limitation 2, since the limitations of the present invention are a characteristic of global valves, the valve product is most easily installed with structures on the same straight line through the outlets at the application site, so structures C1, C2, C3, and C4 can all meet this requirement.

[0076] In restriction 3, the stagnant space refers to the region into which fluid flows and where no flow interference occurs. The stagnant space presents problems of contamination due to residual liquid and particle aggregation. When the radial gap B3 is too small, it also creates an open stagnant space, leading to particle aggregation. Although particle aggregation occurs, the particles are transported and output by the fluid, but this still affects the downstream manufacturing process. The residual region refers to the area where fluid flows, but liquid residue is formed in the region where the fluid cannot be completely discharged after flow stops, which leads to the need for more cleaning liquid and cleaning time during cleaning.

[0077] In the case of structure C3 of restriction 3, the horizontal jet S of the valve seat 121 The flow occurs from the bottom closest to the inner outlet towards the centerline of the outlet channel, without the formation of a circulating flow section and without particle aggregation. However, there is a problem in that there is a stagnant area in the space above the valve stopper and liquid remains in the inlet channel.

[0078] In the case of structure C4 of restriction 3, the horizontal jet S of the valve seat 121 It is bent downwards by 90° via the annular groove, and then the jet S 121 The inlet and outlet channels have a 90° angle between them and the outlet center line of the outlet channel, causing a circulating flow section to form at the upper inner edge of the outlet channel, which leads to particle aggregation. There is no problem of liquid remaining in either the inlet or outlet channel.

[0079] In restriction 4, the inner diameter ratio of structure C4 satisfies the condition 1.75 ≤ d3 / d0 ≤ 2.8. For structures injected from plastic materials, a reasonable range is set as 1.75 ≤ d3 / d0 ≤ 2.2. For metal structures of precision casting with thickness limitations, such as those also having a lining coating, a suitable range is set as 2.0 ≤ d3 / d0 ≤ 2.8. The thickness of general uncoated cast iron and forged members also approaches the condition 2.0 ≤ d3 / d0 ≤ 2.8. Regarding dimensions involved in the forming method of metal structures, the smaller the dimension, the larger the inner diameter ratio. Structures C1 and C3 both have a preferred inner diameter ratio of 2.0. If the inner diameter ratio of structure C2 is too small at 1.29, it will result in excessive head loss. If we compare an inner diameter ratio of 1.8 with an inner diameter ratio of 2.1, and based on the comparison results, comparing an inner diameter ratio of 2.1 with an inner diameter ratio of 1.8, the volume multiplier is at most 1.59 times, and the rational inner diameter ratio allows for a reduction in the size of the valve body and enables rational sector-shaped expansion of the jet S 121 This makes it possible to maintain the streamlines, and the rational fan-shaped deployment of streamlines results in the jet S 121 This represents a reduction in head loss.

[0080] In restriction 4, the value of realizing the flow path structure through innovation lies in the fact that the head loss coefficient ξ for the same inner diameter ratio d3 / d0 is lower than that of conventional technology. Taking the case where d0 = 52.5 mm as an example, a suitable embodiment satisfies the condition that the head loss coefficient ξ is 1.7 ≤ ξ ≤ 3.0. As already listed in reference 4, the larger the inner diameter ratio, the lower the head loss coefficient ξ becomes, but this has the drawback of resulting in an excessively large volume.

[0081] Restriction 5 states that the manufacturing method and material selection used for structures C1, C2, and C3 are always cast, which may be cast iron, cast copper, or stainless steel. However, structures C1, C2, and C3 are unsuitable for injection molding or extrusion molding of plastic resins, and are also unsuitable for metal forging. A common manufacturing method for structure C4 is injection molding and extrusion molding using plastic resin materials, and is also suitable for casting and forging. Regarding the selection and use of each type of material and the structure of the flow path, the limitations on their structural strength must be explained in the relevant examples. When structure C3 is forged using metal, Non-Patent Literature 2 (Chapter 9 Flow through pipe fittings and labyrinth seals, Resistance Coefficients of Throttling Devices, Valves, Plugs, and Labyrinth Seals, Diagram 9-1, Various globe and gate valves, Forged global Considering the valve (p. 287), the head loss coefficient ξ reaches 7.8, and the reason is that the smoothness and radius of curvature of the streamlines from the turning angle B, diffusion C, and turning angle D are all limited.

[0082] Under the above five constraints, constraint 2 can be easily achieved, but numerous difficulties arise in innovating the flow path structure. In terms of the head loss coefficient ξ, structure C3 is the lowest, structure C1 is the next lowest, structure C4 shows average performance, and structure C2 is the worst. Constraint 1 can be easily achieved for metal valves, but when the obliquely upward-facing central hole is adopted for valves made of plastic, the valve seat needs to be further strengthened to satisfy constraint 1. Constraint 3 cannot be satisfied for structures C1, C2, and C3. Structure C4 is fundamentally used for transporting highly clean liquids and already partially satisfies the requirements of constraint 3, transporting only liquids containing suspended particles. From a transportation standpoint, restriction 3 still has flaws but has room for improvement; restriction 4 is a reasonable restriction for any type of valve body structure; structure C2 is an undesirable design compared to restriction 4; and restriction 5 requires attention to innovation in this item, and examples of innovations must always describe the manufacturing methods to which they apply.

[0083] The goal of this innovation is to create a flow path for the innovative valve body based on structure C4, utilizing the structure of the original flow path that transports the highly clean fluid, and to obtain a head loss coefficient ξ that satisfies the condition 1.7 ≤ ξ ≤ 3.0, assuming the same inner diameter ratio d3 / d0.

[0084] Excluding the parts that reduce the head loss coefficient ξ already listed in the four types of structures above, this novel structure still requires further design of the detailed structure of the turning angles A, B, C, D and E in order to obtain a smoother streamline, among which the jet S 121 The curvature of streamlines due to diffusion C and the angle of deflection D is crucial, and the solutions for these smooth streamlines must all satisfy the following problems in order to enable the achievement of the innovation goals.

[0085] Problem 1: It is possible to maintain smooth streamlines and a good radius of curvature from the inlet channel to the outlet channel.

[0086] Problem 2: Jet S 121 The angle α1 between the streamline and the outlet centerline is reduced, satisfying the condition α1 = (90° - γ2), resulting in a slow flow S 122 The angle α2 between the streamline and the outlet centerline is reduced, and the jet S 121 and slow flow S 122 It is possible to maintain a small angle α3 between the streamlines.

[0087] (Problem description) In Problem 1, the smoothness of the streamlines between the inlet and outlet channels means that there are no problems such as the stream being perpendicular to the channel or having an insufficient radius of curvature, there are no abrupt changes in the cross-sectional area of ​​the channel, there is no generation of circulating flow sections, and there is no problem of liquid residue. Structures C1, C2, and C3 all have the problem of liquid residue in the inlet channel, followed by the jet S from the deflection angle B and diffusion C to the deflection angle D. 121 These include situations where there is no rapid diffusion in the flow path cross-sectional area, or blockage due to an insufficient inner diameter ratio, or abrupt curvature of the streamlines. In these situations, the jet S from diffusion C to diversion angle D is maintained in order to keep the head loss low. 121 This can affect the sector-shaped development of the streamlines.

[0088] In Problem 1, when the inlet center line S1 of structure C3 enters the central hole of the valve seat, the angle γ1 between the inlet center line S1 and the vertical line YL1 should not be excessively large, and an excessively large angle γ1 should be reduced by a reduction ratio d0 / a of the major axis that is too small relative to the central hole. x This causes the cross-sectional area of ​​the inlet passage to be too small, and affects the circumferential distribution of the valve seat when the fluid flows out from the central hole and is subjected to a deflection angle B.

[0089] In Problem 1, structure C2 is a jet S of diffusion C. 121The material flows along a 45° turning angle B, but at the same time, it bends again at a 45° angle D and flows towards the inner outlet. The problem is that the flow path cross-sectional area is not smooth, and if the inner diameter ratio is too small, the head loss becomes excessive. Among these, the 45° upward-angled jet S of diffusion C 121 This results in a huge head loss due to the enormous change in the flow channel cross-sectional area, and the jet S of diffusion C. 121 In order to allow entry into the upper half space of the horizontal outlet passage, it is still necessary to rotate it to a direct arc shape and then enter the inner outlet again with a turning angle D of 45°, adding to the insufficient inner diameter of the valve chamber, and the jet S 121 and slow flow S 122 This results in flow interference occurring within the valve chamber.

[0090] In Problem 1, the inlet passage of structure C4 is a horizontal straight pipe, and the position of the sealing surface of the valve seat is higher than the outer diameter of the inlet pipe. As a result, the fluid flowing in horizontally reaches the central hole of the valve seat upwards via a right angle, causing blockage of the circulating flow section. Additionally, the radius of curvature of the streamlines is too small.

[0091] In Problem 1, structure C4 is a jet S of diffusion C. 121 The nozzle enters the annular groove with a deflection angle D1 that causes it to be bent downward at a 90° angle, and the jet S 121 In order for the jet S to flow horizontally toward the aforementioned inner outlet, it is still necessary to give the annular groove two 90° bends with a deflection angle D1, and 121 The streamlines suffer from a problem where head loss occurs due to multiple curves, resulting in an insufficient radius of curvature for the streamlines.

[0092] In problem 2, jet S 121 Reducing the angle α1 between the streamline and the outlet centerline of the inner outlet reduces the jet S 121 This refers to the streamlines emerging from the central hole via a deflection angle B, passing through the radial channel and exhibiting a fan-shaped diffusion C, and flowing directly toward the inner outlet with a deflection angle D, including direct inflow into the inner outlet or inflow with a small-angle curve. Jet S of Structure C1, Structure C3121 The deflection angle D1 is 0°, and the jet S 121 The angle α1 between the inner outlet and the outlet center line S2 is approximately 45°, and the flow path inside the inner outlet is formed to penetrate the outlet center line S2 and flow toward the valve outlet. However, such a high angle α1 can cause flow obstruction and additional head loss.

[0093] In Problem 2, structure C2 has its jet S 121 Although the fluid is ejected at an upward angle of 45°, it only enters the horizontal inner outlet after multiple deflection angles D1 are applied again. However, the deflection angle E is 0°, and the angle α1 at the inner outlet, where α1 ≈ 45°, is still too high. Adding to this problem is the abrupt change in area between the inner outlet and the outlet flow path, resulting in high head loss.

[0094] In Problem 2, although structure C4 has the annular groove, its jet S 121 This involves a jet S flowing downward along the Y-axis with a single 90° turning angle D1, and a jet S with two turning angles D1. 121 The high angle α1 between the exit center line S2 satisfies the condition α1 ≈ 90°.

[0095] In Problem 2, slow flow S 122 The angle α2 between the streamline and the outlet centerline of the inner outlet is the slow flow S 122 The streamlines emerge from the central hole, forming a fan-shaped jet S 121 This refers to anything other than the circumferential direction, which is divided into two branches in the direction opposite to the circumference, and flows in a spiral manner, repeatedly reversing direction along the circumference of the inner diameter of the valve chamber, before entering the inner outlet, resulting in a slow flow S 122 The angle α2 of the streamline is an angle in three-dimensional space, and the flow, which includes circumferential bending and diagonally downward bending, is not easily described by data, but the improvement in the angle α2 can be described using the geometry of the valve chamber.

[0096] In problem 2, jet S 121 and slow flow S 122Maintaining a small angle α3 between the streamlines is important for the jet S 121 and slow flow S 122 This refers to reducing mixing losses due to alternating interference caused by the angular difference between structures C1 and C3, and the jet S 121 It flows horizontally toward the valve outlet, resulting in a slow flow S 122 The water is directed into the inner outlet at a diagonal downward direction along the outlet centerline S2, with a deflection angle D of 45° within the valve chamber, and the jet S 121 and slow flow S 122 The angle α3 between the two is α3 = 45°, and both are caused to introduce abrupt flow interference at the inner outlet and dramatic mixing within the outlet flow path, thereby increasing the head loss.

[0097] In Problem 2, the deflection angle B of structure C2 is 45°, and subject to the limitation of the insufficient inner diameter ratio, the jet S 121 A slow flow S enters the valve chamber. 122 This causes serious damage, and the jet S 121 This involves applying multiple deflection angles D within the valve chamber to create a horizontal jet S. 121 However, this causes disturbances in the included angle α3, making estimation difficult.

[0098] In Problem 2, structure C4 has an annular groove structure and slow flow S 122 This makes it possible to guide the jet to flow along the slope, reducing the angle of the two turning angles D2 and also reducing the angle of the catch α2, but the jet S 121 The two turning angles D1 as the flow descends along the Y-axis are still 90°, with an excessively large angle α1, and slow flow S 122 The jet S flows along the angle β of the slope at the bottom of the annular groove. 121 and slow flow S 122 This results in an excessively large angle α3 between the two, satisfying the condition α3 ≥ 45°, causing flow interference and a significant increase in head loss.

[0099] As can be seen from the above examination of Problem 1 and Problem 2, the entrance center line S1 and the radial center line S 12Furthermore, the aforementioned outlet centerline S2 cannot have a large curvature, and the deflection angle B, diffusion C, and deflection angle D between the streamlines must all maintain a reasonable radius of curvature. Diffusion C jet S 121 and slow flow S 122 This reduces the flow interference occurring within the valve chamber, and although the deflection angle B is a 90° bending angle, the deflection angle B is also a 360° radiative diffusion angle, which reduces the head loss, and the jet S at the deflection angle D 121 and slow flow S 122 In all cases, it is impossible to cause flow interference at the aforementioned inner outlet, and the angle of the streamlines α1, α2, and α3 are all kept from becoming excessive. The above conventional structures have excluded parts of the flow field of structure C3 that approach these requirements, but still have not achieved the innovation goal in terms of the head loss coefficient, and a comprehensive single-item strategy that requires further progress will be able to achieve the goal of a lower head loss coefficient ξ even more effectively. Excluding the above conventional strategies, there are also the following conventional technical references and conventional reference cases that can be used as practical references. References include Non-Patent Document 1, Non-Patent Document 2, and Non-Patent Document 3. Regarding Non-Patent Document 4, taking the table of Fine Thread FlareEnd Connections as an example, a 1-inch diameter valve has a medium-size 2-way valve body, and its C V The value is 3.6, and in a large-size 2-way valve body, its C V The value is 10.2, and the 1 / 2 inch diameter valve has a small size 2-way valve body, and its C V The value is 0.8, and in a medium-size 2-way valve body, its C V The value is 2.6, and from these observations, the inner diameter ratio of the valve body d3 / d0 is C V The valve chamber space, which has a positive correlation with the value and whose inner diameter ratio d3 / d0 is large, has a larger radius of curvature of the streamlines and is high C VWhile a value exists, the condition of inner diameter ratio d3 / d0 > 2.5 is met, and the dimensions of the valve body may be excessive. Conversely, the head loss coefficient ξ has an inverse correlation with the inner diameter ratio d3 / d0 between the valve chamber diameter d3 and the inner diameter d0 of the central hole. The larger the inner diameter ratio d3 / d0, the lower the head loss coefficient ξ becomes, while the smaller the inner diameter ratio d3 / d0, the higher the head loss coefficient ξ becomes. It is considered that an excessively small inner diameter ratio d3 / d0 results in an excessively large head loss coefficient ξ. Referring to Non-Patent Document 5, the DN50 with an actual inner diameter of 57 mm is C V The value is 116 cmh, and the head loss coefficient ξ is 1.7. Referring to Non-Patent Literature 6, in the specifications table for the wear-type diaphragm valve air-operated SWD Series, the model with part number SWD5*-50 is C V The value is 50, the bore is 47.8 mm, and the head loss coefficient ξ is 4.47. Referring to Non-Patent Document 7, the structure of the flow path is all structure C4, and in KH200-19P, the bore diameter is 16 mm, the inner diameter ratio is 2.09, and its C V The value is 4.5, and the head loss coefficient ξ is 5.18. Also, in the KH200-25P, the bore is 22 mm, the bore ratio is 1.88, and its C V The value is 9.1, the head loss coefficient ξ is 6.04, and furthermore, in the KH200-40P, the bore diameter is 33.7 mm, the bore ratio is 1.87, and its C V The value is 0.9, and the head loss coefficient ξ is 6.30.

[0100] (Reference case 1) As shown in Fig. 1 of "valve" in Patent Document 1, the structure of this reference example is similar to structure C2, possesses the same flow path weakness, and has a deflection angle B of 90°. Horizontal jet S 121 It flows toward the axis of the outlet channel, forming a jet S 121 Although both the deflection angle D and the deflection angle E are 0°, the excessively small radial width ratio B2 / d0 and radial gap ratio B3 / d0 cause the streamlines of diffusion C to bend excessively within the radial flow path. Jet S121 and slow flow S 122 This causes flow interference within the valve chamber, resulting in a high head loss. None of these weaknesses can solve problems 1 and 2. The radial clearance ratio B3 / d0 between the outer diameter of the valve plug and the inner diameter of the valve chamber is approximately 0.025, causing the valve chamber space above the valve plug to become a stagnant area, and the inner diameter ratio d3 / d0 is approximately 1.67, which is unfavorable for reducing head loss. This reference example can be manufactured using a casting method, but it is unsuitable for injection molding of plastic materials and also unsuitable for forging of metals.

[0101] Therefore, based on the above considerations, this reference case cannot solve the needs of Problem 1 and Problem 2. Furthermore, it cannot satisfy the requirements of Restrictions 3 and 4, and the casting method needs to be clearly specified to comply with Restriction 5. For example, it can be seen that the lifting loss coefficient ξ of structure C2 still does not meet the innovation goals.

[0102] (Reference case 2) As shown in Fig. 1 of "Valve" in Patent Document 2, the requirements of Restriction 1 and Restriction 2 are met, but the requirements of Restriction 3 are not satisfied. The structure of this cited document is similar to structure C4, and its inner diameter ratio d3 / d0 of approximately 1.71 is slightly smaller than the inner diameter ratio d3 / d0 of Restriction 4, resulting in a slightly higher head loss. The inlet passage has a deflection angle A of 90° and extends into the valve chamber to form an independent curved pipe structure. The radial gap ratio B3 / d0 of the valve plug is approximately 0.24, causing particle aggregation without creating a stagnant space. The radial width ratio B2 / d0 is a relatively small ratio value of approximately 0.268, and for the streamlines of diffusion C, only bends with even smaller radii of curvature can be provided, and the annular space is connected to the bottom space of the valve chamber, and an open stagnant flow area can be easily created in the space immediately below the independent curved pipe at the bottom of the valve chamber, and the requirements of restriction 3 cannot be satisfied.

[0103] Problem 1: The inlet channel has a curved pipe structure, a smooth cross-sectional area, a turning angle A of 90°, and a very good radius of curvature of its streamlines. The outlet pipe is a straight pipe, also has a smooth cross-sectional area, a turning angle B of 90°, and a small radius of curvature of its streamlines, and a jet S 121 The streamlines of the diffuse C in the radial flow path concentrate on the side of the inner outlet, and the streamlines of the diffuse C, obstructed by the diameter of the valve chamber, enter the annular space with a first deflection angle D of 90° downwards, resulting in a slow flow S 122 The streamlines, after passing a turning angle D2, flow downward along the slope at the bottom of the annular groove toward the inner outlet, and then flow into the inner outlet after undergoing two turning angles D2 of approximately 30°, forming a jet S 121 When the jet passes the distal point E3, it is still necessary to apply two deflection angles D1 of 90° each to allow it to enter the inner outlet. The outlet flow path is a horizontal straight pipe, and the deflection angle E is 0°, but the jet S 121 The two turning angles D1 result in a circulating flow section generated in the upper edge space of the outlet channel, creating a slow flow S 122 When the flow is directed diagonally downward, it overcomes the independent curved pipe to generate a separated flow, and the bottom of the valve chamber is brought to become an open-type retention area.

[0104] Problem 2: Jet S 121 The streamlines curve downwards with two 90° turning angles D before entering the inner outlet, resulting in a slow flow S 122 The outlet has an angle of approximately 30° between it and the outlet center line, and the outlet flow path is a straight pipe, and although the deflection angle E is 0°, the jet S 121 and slow flow S 122 A large angle of contact exists between the two, causing flow interference when the inner outlet is located, and further head loss occurs due to the circulating flow section and mixing / diffusion generated within the outlet flow path.

[0105] Therefore, from the above considerations, this reference case fails to satisfy problems 1 and 2, and also fails to satisfy the requirements of restrictions 3 and 4. For example, it can be seen that the head loss coefficient ξ of structure C4 still does not meet the innovation objectives.

[0106] (Reference case 3) As shown in Fig. 1 of the "Diaphragm Valve" in Patent Document 3, the requirements of Restrictions 2 and 4 are met, but the requirements of Restriction 3 are not satisfied. The structure of this cited document is similar to structure C4, has a cylindrical valve chamber space, and has a diaphragm that is directly sealed without a valve plug, and the diaphragm has good sealing performance and causes particle aggregation without creating a stagnant space, but there are concerns about the lifespan due to the direct pressure applied to the diaphragm and it cannot satisfy Restriction 1. The inner diameter ratio d3 / d0 that conforms to restriction 4 is approximately 1.91, the inlet passage has a deflection angle A of 90° and extends into the valve chamber to form an independent curved pipe structure, the radial width ratio B2 / d0 is approximately 0.31, which can provide a more appropriate bend for the streamlines of diffusion C, the center of the diaphragm is conical and has an internal concave ring structure formed around it when fully open, so that the distal point E3 of the inner outlet is lower than the sealing surface of the valve seat, a guide passage that is smoothly bent in an inverted U shape is formed inside the valve chamber, and the jet S 121 and slow flow S 122 In both cases, it becomes possible to smoothly apply the first turning angles D1 and D2 to allow the jet S to enter the annular groove downwards. Furthermore, it is possible to create flow interference within the annular groove, 121 When the jet passes the distal point E3, it is still necessary to apply two deflection angles D1 of 90° each to allow it to enter the inner outlet, and the outlet flow path is a horizontal straight pipe with a deflection angle E of 0°, but the two deflection angles D1 of the jet S121 result in a circulating flow section generated in the upper edge space of the outlet flow path.

[0107] Problem 1: The inlet channel is a curved pipe that bends upward from horizontal and has a smooth cross-sectional area. The structure of the outlet channel is a horizontal straight pipe, and the bottom of the annular groove has a curved surface structure. The turning angle B, diffusion C, and turning angle D are all guided by the cone and the concave ring to make a smooth bend in an inverted U shape, significantly improving the radius of curvature. As a result, the first turning angle D of the fluid is made to bend smoothly in an inverted U shape, allowing the fluid to flow smoothly downward into the annular groove. Jet S 121 and slow flow S 122 This does not create flow interference within the valve chamber, and slow flow S 122 When the flow passes over the independent curved pipe, it generates a separated flow at the bottom of the outer diameter of the valve seat and creates an open-type retention area.

[0108] Problem 2: Jet S 121 Before entering the aforementioned inner outlet, it is necessary to apply a 90° bend at a turning angle D1 again, resulting in a slow flow S 122 The inner outlet is given a bend angle D of approximately 30°, and the outlet flow path is a horizontal straight pipe, and although the angle of bend E is 0°, the jet S 121 and slow flow S 122 There is a large angle between them, causing flow interference, and mixing after entering the horizontal inner outlet results in a loss of head.

[0109] Therefore, from the above considerations, this reference case cannot satisfy Problem 1 and Problem 2, nor can it satisfy Restriction 1 and Restriction 3. For example, it can be seen that the head loss coefficient ξ of structure C4 still does not meet the innovation objective.

[0110] (Reference case 4) As shown in Fig. 1 of the "diaphragm valve" in Patent Document 4, the requirements of restrictions 1, 2, and 4 are met, but the requirement of restriction 3 is not satisfied. The structure of this cited document is similar to structure C4, having the cylindrical valve chamber space and a valve plug having a diaphragm and a spherical curved surface. The diaphragm has good sealing performance, but the narrow space on the valve plug and the radial gap ratio B3 / d0 that satisfies the condition ≤0.125 are too small, creating a stagnant space and causing particle aggregation, and the inner diameter ratio d3 / d0 that satisfies restriction 4 is about 1.85. The inlet channel has a deflection angle A of 90° and is perpendicular, and the radial width ratio B2 / d0 is relatively small, with a ratio value of approximately 0.25, and cannot provide a more appropriate bend for the streamlines of diffusion C, and when fully open, the fluid flows out along the spherical surface with a deflection angle B of 45°, exhibiting conical diffusion C, the annular groove has the sloped surface that slopes downward and surrounds the outer diameter of the valve seat, and is connected to the outside of the outer diameter of the valve seat and again communicates with the inner outlet, the distal point E3 of the inner outlet is higher than the sealing surface of the valve seat, the upper edge of the outlet channel forms an oblique line segment with a 45° angle, and the lower edge point E4 of the inner outlet and the lower edge point E6 of the valve outlet are horizontal, so that the inner outlet has a very long major axis a y To have a jet S 121 The main flow line, after being constrained by the diameter inside the valve chamber, passes through multiple bends at a deflection angle D1 and finally flows into the inner outlet at a 45° downward angle, and enters the upper half space of the outlet passage, forming a slow flow S. 122 The fluid, after being constrained by the diameter of the valve chamber, enters the annular groove 90° downward via a deflection angle D2 in which it is bent multiple times, and the 45° conical diffusion C forms a jet S 121 and slow flow S 122 This causes flow interference within the valve chamber.

[0111] If the product were to be manufactured using injection molding to meet the requirements of restrictions 1, 2, and 4, it would be necessary to manufacture a slider for the internal outlet, and cost considerations have been taken into account.

[0112] Problem 1: The inlet passage is a right-angle curved pipe with a smooth cross-sectional area, but the right-angle deflection angle A results in additional head loss. The outlet passage is a horizontal straight pipe, and the slope of the annular groove has an oblique angle β, with a deflection angle B of 45°, which greatly improves the radius of curvature, and the proximal point E4 of the inner outlet and the proximal point E6 of the valve outlet are horizontal, so slow flow S 122 To allow the flow to move away from the angle β and enable horizontal inflow into the inner outlet, it is absolutely necessary to apply two turning angles D2 with an angle of β, resulting in a slow flow S 122 When the flow overcomes the outer diameter of the valve seat, a separate flow can be generated at the bottom of the outer diameter of the valve seat, creating an open stagnation area and increasing the head loss.

[0113] Problem 2: Jet S 121 The flow is directed diagonally downward along the annular groove, maintaining a 45° angle between itself and the outlet centerline, and is then directed out horizontally by applying a 45° bend to the turning angle E, resulting in a slow flow S. 122 However, it flows diagonally downward along the annular groove, and enters the lower half space of the inner outlet with a turning angle D of approximately 30°, but a circulating flow section is generated at the proximal point E4, and a jet S 121 and slow flow S 122 The angle between the two is relatively small, and does not cause serious flow interference at the inner outlet, but more head loss occurs in the outlet flow path due to the mixing of the deflection angle E.

[0114] Therefore, from the above considerations, it can be seen that this reference case cannot satisfy problems 1 and 2, nor can it satisfy restriction 3, and although the head loss coefficient ξ is improved with respect to structure C4, it still cannot meet the innovation goal.

[0115] (Reference case 5) As shown in Fig. 1 of the "Plastic control valve" in Patent Document 5, it satisfies the requirements of Restriction 1 and Restriction 2, but its horizontal outlet passage still has a recirculation section at the upper edge of the outlet passage of the inner outlet, causing particle aggregation and failing to meet the requirement of Restriction 3, and the excessively high inner diameter ratio significantly increases the volume and fails to meet the requirement of Restriction 4. The structure of this cited document is similar to structure C4, and both the outlet passage and the inlet passage are horizontal straight pipes, have the cylindrical valve chamber space and a diaphragm with a valve plug, the diaphragm has good sealing performance, and the cylindrical valve plug has a radial gap ratio B3 / d0 of about 0.53, causing particle aggregation without creating a stagnant space and failing to meet the requirement of Restriction 4, the inner diameter ratio d3 / d0 is about 2.56, the excessively high inner diameter ratio d3 / d0 has an excessively large volume, and the inlet passage has a deflection angle A of 90° and is perpendicular As a result, the head loss increases, and the radial width ratio B2 / d0 is very large, with a ratio value of approximately 0.44. When diffusion C is unfolded, the streamlines can be ensured to have a reasonable radius of curvature, and a suitable bend is made, and when the valve is opened, the fluid flows out with a deflection angle B of 45° along the guide angle at the bottom of the valve plug, exhibiting a conical diffusion C. The bottom of the annular groove is the slope that inclines downward, and the slope surrounds the outer diameter of the valve seat, and also passes over the bottom of the outer diameter of the valve seat and enters the inner outlet. The innovation in this item can reduce the problem of the bottom of the slope of the annular groove being too short, creating a circulating flow section at the bottom of the outer diameter of the valve seat, which can lead to particle aggregation problems and jet S 121 The main stream must flow out from diffusion C with a cone angle of 45° and be deflected at an angle D1 (where the angle is ≥ 90°) in order to enter the annular groove downwards. Directly applying an inverted U-shaped smooth bend to allow entry into the annular groove is extremely difficult, and slow flow S 122 To enable downward entry into the annular groove, the fluid, which is bifurcated and rotates horizontally, undergoes circumferential flow along the diameter of the valve chamber, passing through a turning angle D2 with an angle of ≥90°, and flows to the bottom of the slope angle β along the inclined surface, forming a jet S. 121 and slow flow S 122This causes flow interference within the valve chamber, and combined with the excessive angle of deflection D, the jet S 121 Limit the flow rate.

[0116] Problem 1: The inlet channel is a right-angle curved pipe with a smooth cross-sectional area, but the right-angle turning angle A is 90°, resulting in additional head loss, and the turning angle B is 45°, resulting in jet S 121 and slow flow S 122 This can have a first turning angle D1 and a turning angle D2. To enable downward flow, both angles must be ≥90°, and the jet S 121 When the jet passes the distal point E3, it is still necessary to apply two deflection angles D1 of 90° each to allow entry into the inner outlet, and the outlet flow path is a horizontal straight pipe, with a deflection angle E of 0°, but the jet S 121 The two turning angles D1 result in a circulating flow section generated in the upper edge space of the outlet channel, creating a slow flow S 122 In order to allow entry into the outlet channel, the inner outlet may be bent twice at a turning angle D2 of approximately 45°, resulting in a slow flow S 122 When the fluid passes over the outer diameter of the valve seat, it flows along the bottom, which is angled downwards, and also passes over the bottom of the outer diameter of the valve seat and enters the inner outlet, without generating a separating flow or creating an open stagnation area.

[0117] Problem 2: Jet S 121 The flow is directed diagonally downward along the annular groove, creating a 90° angle between it and the outlet centerline, and it is necessary to apply two 90° turning angles D1. Slow flow S 122 Furthermore, it flows diagonally downward along the annular groove, forming a slow flow S with an angle of approximately 45° between it and the outlet centerline. 122 The jet S is subjected to two deflection angles D2 of approximately 45°. 121 and slow flow S 122 If the angle between the two becomes too large, flow interference occurs at the inner outlet, resulting in increased head loss.

[0118] Therefore, from the above considerations, this reference case fails to satisfy problems 1 and 2 and does not meet the requirements of restrictions 3 and 4. For example, the head loss coefficient ξ of structure C4 still does not meet the innovation goal. As a similar structure C4 in a similar reference case, the similar structure of "Diaphragm valve structure" in Patent Document 6 can be cited. This structure meets the requirements of restrictions 1, 2 and 4, and the diagonally downward bottom is directly connected to the inner outlet, making it possible to reduce the horizontal outlet flow path in the confluence section. The inner diameter ratio meets the requirement of restriction 4, and it provides some improvement to the portion perpendicular to the inlet flow path. However, it still does not produce a significant effect, and there is still a problem of particle aggregation circulating at the upper edge of the outlet flow path of the inner outlet.

[0119] (Reference case 6) As shown on page 5 of "Anti Corrosion Stop Valve" in Patent Document 7, an inner diameter ratio that is too low satisfies the requirements of Limitation 1 and Limitation 2 but does not satisfy the requirement of Limitation 4. The structure of this reference example is a metal cast valve with a corrosion-preventive lining, similar to structure C3, having a cylindrical valve chamber space, and having a valve plug and a diaphragm, the diaphragm having good sealing performance, being barrel-shaped, and the radial gap ratio B3 / d0 with respect to the diameter of the valve chamber is about 0.092, which creates a stagnant space and causes particle aggregation. The radial gap ratio B3 / d0 of the cylindrical valve plug is about 0.13, which causes particle aggregation without creating a stagnant space and does not satisfy Limitation 4, and an inner diameter ratio d3 / d0 of about 1.47, which is too low an inner diameter ratio d3 / d0 has a large head loss. The inlet channel has a smooth surface, a 90° turning angle A, and forms an arc-shaped channel. The valve has a conical surface at its bottom, which allows the turning angle B to be approximately 45°, and it has a conical streamline diffusion C, resulting in a jet S. 121 The main stream flows out from diffusion C with a cone angle of 45° and then flows again along the outlet centerline of the outlet channel which is angled downwards at 60°, making it very difficult for the jet S to flow. 121This allows the material to enter the upper half space of the inner outlet with a relatively large radius of curvature, and to flow along the upper edge of the outlet channel, creating a slow flow S. 122 It rotates within the columnar valve chamber space, and enters the inner outlet after being subjected to a turning angle D.

[0120] Problem 1: The inlet channel has a smooth cross-sectional area and is a curved pipe, and the outlet channel is a curved pipe that slopes diagonally downward from the valve chamber and changes to a horizontal outlet, and has a smooth cross-sectional area, and from the deflection angle B, diffusion C to the deflection angle D, both are limited to an insufficiently small inner diameter ratio, causing an increase in head loss, and the jet S 121 and slow flow S 122 Both methods require the application of conical diffusion C flow, are confined to the narrow valve chamber, and both cause flow interference.

[0121] Problem 2: Jet S 121 After being subjected to a turning angle D, it enters the upper half space of the inner outlet and flows along the upper edge of the outlet flow path, and then slows down S 122 The jet S enters the inner outlet by being rotated within the elongated columnar space of the valve chamber and subjected to a turning angle D. 121 and slow flow S 122 The space between the two can cause flow interference in the upper edge space of the inner outlet, resulting in a loss of head.

[0122] Therefore, from the above considerations, it can be seen that this reference case cannot satisfy the requirements of Problem 1, Problem 2, and Restrictions 3 and 4, and even with a higher head loss coefficient ξ than structure C3, it still cannot meet the innovation objectives.

[0123] (Reference case 7) As shown in Fig. 1 of the "Membrane valve" in Patent Document 8, the requirements of Limitation 1 and Limitation 2 are met, but the excessively high inner diameter ratio does not meet the requirements of Limitation 4. The structure of this cited document has a valve chamber of a circularly flattened space, sealed by a diaphragm with a valve plug, the radial gap ratio B3 / d0 of the valve plug is about 3.57, causing particle aggregation without creating a stagnant space, the excessively high inner diameter ratio d3 / d0 is about 4.88, does not meet Limitation 4, the excessively high inner diameter ratio d3 / d0 can accommodate the inlet and outlet passages being mounted simultaneously on the plane of the partition plate, and has low head loss, and both the inlet and outlet passages have a smooth surface area. The flow path is arc-shaped, and both the turning angle A and turning angle E are 90°. By having a conical surface at the bottom of the valve, the turning angle B can be made to approximately 45°, and the flow path has a conical streamline diffusion C, resulting in a jet S. 121 It flows out from diffusion C at a 45° angle, changes direction again after passing through multiple bends, and enters the outlet channel downwards, forming a jet S. 121 The main stream enters the inner outlet after being bent in an inverted U-shape. The remaining fan-shaped streamline still needs to flow horizontally around the circumference to allow it to enter the inner outlet, and such excessive bending results in a large head loss, slow flow S 122 It flows into the oblate valve chamber with a 45° conical streamline along the remaining inscribed angle, resulting in a slow flow S 122 It is divided into two branches, and enters the inner outlet downwards by swirling rotation along the inner diameter surface of the valve chamber, resulting in excessive bending and a large head loss. The excessive inner diameter ratio d3 / d0 results in a slow flow S that is swirled and repeatedly reversed. 122 This causes a decrease in flow velocity, and the inner wall of the valve chamber and the corner region of the partition plate are brought into an open stagnant area, which does not meet the requirements of restriction 3.

[0124] Problem 1: Since the streamlines have large bends at both turning angles A and B, the jet S 121 and slow flow S 122The fluid flows horizontally and circumferentially within the valve chamber, causing flow interference, and the deflection angle B, diffusion C, and deflection angle D are never smooth.

[0125] Problem 2: Jet S 121 The main stream is ejected from a cone with a turning angle of 45° upward, then bends in an inverted U-shape and enters the inner outlet downward, requiring a bend of 135° from turning angle B to the inner outlet. Finally, a slow flow S forms a 0° angle between the inner outlet and the center line of the outlet, flowing horizontally around the circumference. 122 This will cause flow interference at the inner outlet.

[0126] Therefore, from the above considerations, it can be seen that this reference case has a very large inner diameter ratio d3 / d0, which does not meet the innovation objectives, and the flow interference in Problem 1 and Problem 2 clearly cannot satisfy the requirements.

[0127] (Reference case 8) As shown in Patent Document 9, "Piston diaphragm with integal seal," the requirements of restrictions 1, 2, and 3 are met, but the excessively high inner diameter ratio does not meet the requirement of restriction 4. The structure of this cited document is derived from structure C4, but this cited document has the valve chamber in a bowl shape, and its outlet flow path is a diagonally downward flow path, which can avoid the particle aggregation problem of the original structure C4, is sealed by a diaphragm with a valve plug, and the excessively large inner diameter ratio d3 / d0 is about 3.4, which does not meet restriction 4. The bowl-shaped valve chamber has sufficient flow space and does not cause particle aggregation without creating a stagnant space. The sealing surface of the valve seat is located on the horizontal plane at the bottom of the valve chamber, the inlet passage is formed to be of equal diameter and flows horizontally from one side of the valve body, then enters the conical central hole upward with a 90° (right-angle) turning angle A, the outlet passage is inclined approximately 45° downward from the valve chamber and flows out again from the other side through a horizontal straight pipe, the inner outlet of the outlet passage is a conical pipe, and the lower edge of its opening is located on the horizontal plane at the bottom of the valve chamber, the entire cross-section of the inner outlet is a vertical elongated ellipse, the horizontal pipe of equal diameter of the outlet passage is connected to the conical pipe, and when the valve is opened, the fluid enters the bowl-shaped radial passage with a turning angle B of approximately 90° into the central hole, forming a jet S 121 The mixture C is diffused along the inner surface of the bowl shape and flows towards the inner outlet, forming a jet S. 121 The jet S enters the conical channel with a deflection angle D of approximately 45° at the inlet, and 121 After entering the outlet channel, it is directed out through a horizontal straight pipe at a deflection angle E of approximately 45°, resulting in a slow flow S. 122 The remaining flow proceeds along the inner surface of the bowl shape in the circumferential direction into the valve chamber space, and is repeatedly reversed in a spiral shape, creating a horizontal annular flow along the inner surface of the bowl shape as it moves forward, and finally merges and is rectified, and flows into the inner outlet with a diagonal downward turning angle D of approximately 45°, creating a slow flow S. 122 After entering the aforementioned outlet channel, the fluid is directed at a deflection angle E of approximately 45° and discharged through a horizontal straight pipe.

[0128] Problem 1: Since the deflection angle A is a right angle with a relatively large head loss, the conical slope of the central hole promotes a curvature of approximately 80° at the deflection angle B, thereby reducing the head loss. Diffusion C is a flow along the bowl-shaped inner surface of the valve chamber, which is a flow with a high radius of curvature, and jet S 121 and slow flow S 122 With the help of the angle of change D, numerous jets S 121 It enters the lower semi-elliptical space of the inner outlet along the horizontal plane, and slow flow S 122 The flow is divided into two branches, and after repeatedly reversing in a spiral pattern on the bowl-shaped inner surface of the valve chamber, it is redirected at an angle D of 45° and flows diagonally downward into the upper semi-elliptical space of the inner outlet.

[0129] Problem 2: Jet S 121 and slow flow S 122 After bending at the angle of deflection D, the jet S 121 It forms a 45° angle with the outlet centerline, and slow flow S 122 The direction is parallel to the outlet centerline, and the jet S 121 and slow flow S 122 This prevents significant reduction in head loss by causing flow interference within the conical flow path of the inner outlet.

[0130] Therefore, from the above considerations, it can be seen that this reference case cannot satisfy the requirements of Problem 1 and Problem 2, nor can it satisfy the requirements of Restriction 4.

[0131] (Reference case 9) As shown in Patent Document 10, "Diaphragm Valve," it does not meet the requirements of restriction 1, but meets the requirements of restrictions 2 and 3, and differs from the structure in global valves. In this reference example, the flow path design in the sealing dam is elongated elliptical, with its major axis a zThe length of the inlet and outlet passages approaches 2a0, and the area of ​​the inlet passage and the area of ​​the outlet passage remain unchanged. Therefore, the needs can still be met in accordance with the requirements of restriction 4. Regarding the explanation of restriction 5 in this reference example, the patent does not specify the method of forming the product, but manufacturers can certainly have injection-molded products. For example, as shown in reference 5, it is also applied to casting and not to forging. The structure of this reference example is a wear valve, also called a weir valve, and the sealing weir is an elongated elliptical arc sealing surface in the Z-axis direction. The diaphragm is connected in such a way that it can only perform linear press sealing in the Z-axis direction. It is not possible to provide a circular sealing line for a circular hole, and it is possible to receive a uniform force and deform uniformly, which would reduce the reliability of the sealing quality and would not satisfy the requirements of restriction 1. The inlet and outlet passages are connected on both sides of the sealing weir. Furthermore, the arcuate surfaces of the lower edges of both flow paths are directly connected horizontally to the weir body, and both the inlet and outlet flow paths are connected to the sealed weir body at an upward angle from horizontal, and the cross-sectional areas of both flow paths are designed to be equal, and the radii of curvature of the streamlines are reasonable during fluid flow, and a smooth flow path is created on the weir body. However, only the turning angles A and E need to be considered, and both of these are very desirable. When the diaphragm is opened, the single concave circular flow path formed at the weir can fully satisfy the needs of turning angle B, diffusion C, and turning angle D. The bends in the streamlines in this section are also very smooth, resulting in a very low head loss over the entire flow path. This reference example differs from a global valve in that the fluid does not flow into the space of the valve chamber, and the fluid flows within the flow path formed with the diaphragm within the flow path, eliminating the need to consider the requirements of restriction 4. As a result of adding this reference, which has a very smooth flow path and the same area for each cross-section of the flow path, the lowest head loss coefficient ξ can be obtained, and the requirements of problems 1 and 2 can be fully satisfied.

[0132] Problem 1: It is preferable that the valve inlet gradually changes from a circular shape to an upward-sloping circular shape along the Z-axis, and then elongates in the Y-axis direction to form a flattened ellipse with reduced height. The flattened ellipse of the valve body is then gradually changed to an upward-sloping circular shape, while the length along the Z-axis is reduced until it reaches the circular valve outlet. In this process, each cross-section of the flow path is maintained at the same area, and the turning angles A, B, C, and from D to E are all very smooth.

[0133] Problem 2: Jet S 121 and slow flow S 122 Both are located within the same flow path, and jet S 121 The inlet channel is given a fan shape and begins to contract via the flattened elliptical portion of the weir, thereby causing the jet S 121 The slow flow S is made to flow coaxially with the outlet centerline. 122 The inlet channel is into which a jet S 121 The same fan-shaped deployment is applied, but its position is that of the jet S 121 Located on the outside, and beginning to contract via the flattened elliptical portion of the weir, slow flow S 122 The jet S is made to flow so as to approach the outlet centerline coaxially, 121 and slow flow S 122 Both of these mixtures have low head losses.

[0134] Therefore, from the above considerations, it can be seen that in this reference case, the requirement of restriction 1 cannot be satisfied, but the requirements of restrictions 2, 3, and 4 can be satisfied. Furthermore, referring to reference 5, the actual inner diameter of DN50 of 57 mm is C VThe value is 116 cmh, and the head loss coefficient ξ is 1.7. For the deflection angle B, diffusion C, and deflection angle D, all of these are extremely difficult to achieve with a complex global valve. For example, structure C3 has a head loss coefficient ξ of 3.4, which is much higher than this reference example. However, similar to Non-Patent Document 6, which describes an example in another company where a weir seat is used for sealing, the same wear valve structure similarly fails to satisfy the requirements of Limitation 1, and its head loss coefficient ξ reaches 4.47, which is an extremely large difference compared to the head loss coefficient ξ of 1.7 in Reference Document 5. Upon investigating the cause, it was found that the channel cross-sectional area in Non-Patent Document 6 is reduced at the weir section, and the lower edges of the inlet channel and the outlet channel have excessive bends rather than being smooth. The turning angle B, diffusion C, and turning angle D at the sealed weir section are connected in a way that is not smooth and the streamlines are bent in this area, and the head loss coefficient ξ is significantly higher than that of structure C3, far exceeding that of Non-Patent Document 5. From these considerations, it is considered that a single well-known conventional structure is still insufficient to guarantee that its head loss coefficient ξ can easily satisfy the needs.

[0135] Based on the analysis of the nine reference cases disclosed in non-patent literature, including structures C1, C2, C3, and C4, partial solutions are proposed for restrictions 1, 2, 3, 4, and 5, and a perfect solution has not yet been obtained from a single reference case. Regarding the content of Problem 1, methods for maintaining a smooth flow path have already been presented; for example, structure C3 has a smooth flow path but cannot satisfy Problem 2, resulting in a jet S 121 This reduces the problem of the angle α1 between the jet S and the outlet center line becoming excessively large. 121 and slow flow S 122This also presents the problem of flow interference at the aforementioned inner outlet, and cannot satisfy the requirements of restriction 3. Excluding Reference Example 9, no single reference example flow path was found that achieves the integrity requirement, and Reference Example 9 is limited by its inability to satisfy the requirements of restriction 1 and is not the target of this innovation. Furthermore, the structure presented in Reference 6 indicates that achieving streamline smoothness in this portion of the deflection angle B, diffusion C, and deflection angle D is not easily accomplished. However, the measures presented here are all conventional technologies and can be cited separately or individually, but they can be adapted and implemented, though not easily, to achieve integrity in the valve flow path and to achieve the target of a low head loss coefficient ξ. Another crucial point of the solution to problem 2 is the jet S 121 and slow flow S 122 The goal is to reduce the problem of excessively large angle α3 between streamlines, which is not yet resolved in the current structure C3. In addition, the angle α3 of the streamlines in structure C2 is set to 0°, but this structure cannot simultaneously satisfy problems 1 and 2. A perfect solution that can simultaneously satisfy restrictions 1, 2, 3, and 4, and also simultaneously satisfy problems 1 and 2, is the crucial part that can truly achieve the target head loss coefficient ξ. All of the complete solutions described above require innovation in the structure of the valve body flow path. Hereinafter abbreviated as structure C5, it is possible to simultaneously satisfy the needs of innovation, and in addition, it is necessary to explain different materials and manufacturing processes in the examples, and it is possible to satisfy the needs listed in the manufacturing process of restriction 5. [Prior art documents] [Patent Documents]

[0136] [Patent Document 1] U.S. Industrial Design Specification No. 606867(A) [Patent Document 2] U.S. Patent No. 1,647,823(A) [Patent Document 3] U.S. Patent No. 2381544(A) [Patent Document 4] U.S. Patent No. 2,638,307(A) [Patent Document 5] U.S. Patent No. 5002086(A) [Patent Document 6] US Patent No. 11585460 (B2) [Patent Document 7] Chinese Utility Model Application No. 2083665(U) Specification [Patent Document 8] U.S. Patent No. 5083750(A) [Patent Document 9] US Patent No. 6672561 (B2) [Patent Document 10] U.S. Patent Application Publication No. 20120056120(A1) [Non-patent literature]

[0137] [Non-Patent Document 1] 1978, Author: DSMILLER, Book Title: Internal Flow System, Serial Number: TREX-130713.0001, Edition: Second Edition, Publisher: BHRA [Non-Patent Document 2] 1989, Authors: Erwin Fried and IE Idelchik, Book Title: Flow Resistance: A Design Guide for Engineers, ISBN: 0-89116-435-9, Publisher: Hemisphere Publishing Corporation [Non-Patent Document 3] 2005, SEMI F99 - Dimensional Specification of a Diaphragm Valve for a MetricPFA Tube, Issuer: EMI [Non-Patent Document 4] SWAGELOK Catalog 2021, Ultrahigh-Purity Fluoropolymer Diaphragm Valves, MS-02-171, Rev. I, March 2021, Page 5 of this reference catalog, Flow Data Flow Coefficients [Non-Patent Document 5] 2020 GFPiping Systems - IndustrialPiping Systems Catalog, handbediende-membraanafsluiters-type-514.pdf, page 3, Table KV 100 values ​​(flow characteristics)Type 514 - 517 [Non-Patent Document 6] 2022-CKD-Weir Diaphragm Valve SWD / MWD Series Catalog CC-1096T 8,page 1 [Non-Patent Document 7] 2021-Wasa Fyo Science and Technology / bueno catalog, flow control, KH200, page 40 [Overview of the project] [Problems that the invention aims to solve]

[0138] In this invention, the structure of the valve body flow path will be hereinafter abbreviated as structure C5. The objective is to satisfy the condition that the head loss coefficient ξ is 1.7 ≤ ξ ≤ 3.0, and the comparison standard is based on d0 = 52.5 mm.

[0139] Structure C5 was modified with the aim of making good use of the structural advantages of Structure C4 while avoiding its disadvantages, and pursuing the low head loss coefficient ξ described in Reference 5. Structure C5 has three novel countermeasures.

[0140] Improvement 1 improves the inlet flow path, allowing the curved circular flow path to completely avoid the circulating flow section.

[0141] Improvement 2 improves the outlet flow path, allowing the curved circular flow path to completely avoid the circulating flow section.

[0142] Improvement 3 is jet S 121 and slow flow S 122 The layered flow is improved, and the curved circular flow path can completely avoid the circulating flow section, resulting in a jet S 121 The flow direction and the outlet centerline have a lower clamping angle α1, and the jet S 121 and slow flow S 122 The streamlines have a smaller angle α3 between them to reduce flow interference at the inner outlet. The features of structure C5 will be further explained below. [Means for solving the problem]

[0143] Structure of the channel of structure C5, coordinate points and inlet centerline S1, radial centerline S 12 Refer to Figures 1A and 1B, which are schematic diagrams showing the exit centerline S2 and the turning angles A, B, C, D, and E.

[0144] Mounting angle θ and turning angles 2θ, θ1, θ2, θ of structure C5 21 θ 22 , 2θ1, 2θ2, 2θ 21 , 2θ 22 Refer to Figure 1C, a schematic diagram showing various angles including those mentioned above.

[0145] In describing the present invention, a global valve with an inner diameter of 52.5 mm will be used as an example.

[0146] In structure C5, which is an improved structure of the valve body passage of such a global valve, the structure of the valve body passage comprises a valve chamber, an annular groove, a valve seat, a valve plug, a sealing surface, a valve inlet, an inlet passage, a central hole, a valve outlet, an outlet passage, an inner outlet, and so on. The following sealing mechanism illustrates the valve plug and its diaphragm configuration.

[0147] Let the valve chamber diameter be d3, the valve plug outer diameter be d2, the valve seat outer diameter be d1, the valve inlet diameter be d0, and the valve outlet diameter be d0.

[0148] Let LH1 be the height of the center point P1 of the central hole, LH2 be the height of the center point P3 of the inner outlet, LH3 be the height of the sealing surface of the valve seat, and P be the height of the center point of the sealing surface. DP The valve has a central point P2 at the valve inlet and a central point P4 at the valve outlet.

[0149] The horizontal line XL1 passes through the center point P1 of the central hole, and the horizontal line XL1 and the circumference of the central hole intersect each other at two points, the distal point E1 and the proximal point E2, where the distal point E1 is located on the side of the valve inlet and the proximal point E2 is located on the side of the valve outlet.

[0150] The pipe axis XL2 (X-axis) passes horizontally through center point P2 and center point P4. The height indication of this innovation is based on the pipe axis XL2 connecting the valve outlet and the valve inlet, and the zero point of the Y-axis coordinate indicates the position relative to the pipe axis XL2, with positive values ​​(>0), zero (=0), and negative values ​​(<0).

[0151] The vertical line YL1 passes through the center point P1 and intersects with the pipe axis XL2 at point P 11 They intersect with each other.

[0152] The vertical line YL2 passes through the center point P4, and the vertical line YL2 and the circumference of the valve outlet intersect at two points, the distal point E5 and the proximal point E6. The height of the distal point E5 is d0 / 2, and the height of the proximal point E6 is -d0 / 2. The proximal point E6 is the lowest point of the outlet flow path.

[0153] The vertical line YL3 passes through the center point P3 of the inner outlet and intersects with the pipe axis XL2 at point P 31 They intersect each other, and the vertical line YL3 and the circumference of the inner exit intersect each other at the two intersection points of the distal point E3 and the proximal point E4, with the height of the distal point E3 being LH4 and the height of the proximal point E4 being LH5.

[0154] The vertical line YL4 is established passing through the center point P2, and the vertical line YL4 and the circumference of the valve inlet intersect each other at two points, the distal point E7 and the proximal point E8. The height of the distal point E7 is d0 / 2, and the height of the proximal point E8 is -d0 / 2, with the proximal point E8 being the lowest point of the inlet passage.

[0155] There is a horizontal distance L1 between center point P1 and center point P2, P 11 The condition P2 = L1 is satisfied, and there is a horizontal distance L2 from the center point P4 to the center point P1, and P4P 11 The condition = L2 is satisfied, there is a horizontal distance L from center point P2 to center point P4, and the condition P4P2 = L = L1 + L2 is satisfied.

[0156] The horizontal distance LL2 is between center point P4 and center point P3, and the condition LL2 = L2 - d3 / 2 is satisfied.

[0157] The valve seat has the annular groove and the valve seat installed inside it, and also has the valve plug, valve stem and sealing surface installed, and the valve plug, valve stem and sealing surface are concentric. The valve seat is used to connect the inlet passage and the outlet passage, the inlet passage enters from the horizontal valve inlet and is bent upward, and its outlet end is the central hole of the valve seat, and the inner outlet installed on the inner diameter surface of the valve seat is used to connect to the outlet passage. The valve inlet and the valve outlet are installed on both sides of the valve body, and when the outlet passage is a straight pipe or a curved pipe of the diagonal downward type, the inner outlet is a non-standard ellipse.

[0158] The annular groove is located within the valve chamber diameter and surrounds the outer diameter of the valve seat, the bottom of the annular groove is a slope with an angle β, the higher side of the slope is located on the side of the inlet passage, the lower side of the slope is located on the side of the outlet passage, and is connected to the proximal point E4 of the inner outlet.

[0159] The valve seat is installed at the outlet end of the inlet passage and is provided with the sealing surface.

[0160] The valve plug is cylindrical and has a flat surface at its bottom. When the global valve is closed, the valve plug is used to seal the sealing surface. When the valve is fully open, a radial flow path with an opening of B1 is formed between the bottom surface of the valve plug and the sealing surface, satisfying the condition 0.125 ≤ B1 / d0 ≤ 0.5. A preferred embodiment is one that satisfies the conditions B1 / d0 = 0.25 and B1 ≈ 13.14 mm.

[0161] In the aforementioned inlet passage, the inlet passage comprises the valve inlet, the inlet center line S1, the central hole, and the upper edge line S 1a And the lower edge line S 1b The entrance center line S1 includes center point P1 and center point P DP The central hole is connected to the center point P2, and has an angle γ1 between the center point P1 and the vertical line YL1. When the angle γ1 ≠ 0°, the central hole is a non-standard elliptical hole, and its major axis a in the X-axis direction. x It has, a x ≥d0, a x When the conditions =E1E2 and E1P1≧P1E2 are satisfied and the included angle γ1=0°, the central hole is a circular hole with diameter d0, and its minor axis in the Z-axis direction is b z It has, b z The condition =d0 is satisfied. The upper edge line S 1a The distal point E1 and the distal point E7 are connected, and the lower edge line S 1b This connects the proximal point E2 and the proximal point E8.

[0162] The radial flow channel has a radial center line S 12 The valve includes the opening degree B1, and when the valve is opened, the opening degree of the radial flow path, which consists of the bottom surface of the valve and the sealing surface, is B1, the radial flow path surrounds the flow path radiating from the central hole, the height of the radial flow path is LH6, and the condition LH6 = B1 + LH3 is satisfied. Radial center line S 12 It connects center point P1 and center point P3, and from center point P1, it flows out in different directions in a radial manner, finally connecting to center point P3.

[0163] The aforementioned outlet passage comprises the inner outlet, the valve outlet, the outlet centerline S2, and the upper edge line S 2a And the lower edge line S 2b The outlet center line S2 connects center point P3 and center point P4, and has an angle γ2 between center point P3 and the vertical line YL3, satisfying the condition 0° ≤ γ2 < 90°. The inner outlet is a non-standard elliptical hole, and the major axis a in the Y-axis direction. y It has, a y ≥d0, a y The conditions =E3E4 and E3P3≧P3E4 are satisfied, and the minor axis b in the Z-axis direction. z It has, b z When the condition =d0 is satisfied and the angle γ2 = 90°, the outlet passage is a horizontal straight pipe, and a y The condition =d0 is satisfied. The upper edge line S 2a The distal point E3 and the distal point E5 are connected, and the lower edge line S 2b The proximal point E4 and the proximal point E6 are connected. The distal point E3 has a height difference H1 with respect to the sealing surface and satisfies the condition LH4-LH3=H1. When the distal point E3 is higher than the sealing surface, the condition H1≧0 is satisfied, and when it is lower than the sealing surface, the condition H1≦0 is satisfied. The center point P3 of the inner outlet has a height difference H3 with respect to the sealing surface and satisfies the condition LH2-LH3=H3. When the center point P3 is higher than the sealing surface, the condition H3≧0 is satisfied, and when it is lower than the sealing surface, the condition H3≦0 is satisfied.

[0164] The radial gap B3 is located between the valve plug outer diameter d2 and the valve chamber diameter d3, satisfying the conditions B3 = (d3 - d2) / 2 and 0.2 ≤ B3 / d0 ≤ 0.4. The annular space B2 is located between the valve seat outer diameter d1 and the valve chamber diameter d3, satisfying the conditions B2 = (d3 - d1) / 2 and 0.2 ≤ B2 / d0 ≤ 0.4. The inner diameter ratio is d3 / d0, and the ratio of the valve chamber diameter d3 to the valve inlet diameter d0 satisfies the condition 1.75 ≤ d3 / d0 ≤ 2.5.

[0165] Below, entrance center line S1, radial center line S 12The three centerlines, including the exit centerline S2, are displayed as streamlines. Furthermore, the description of these bending angles is limited to those based on predictable geometry, and further descriptions are obtained using complex 3D-CFD calculations.

[0166] The inlet centerline S1 may be a single line segment or a combination of several line segments, and the types of line segments include circular arcs, vertical line segments, diagonal line segments, and horizontal line segments. Of these, the vertical line segment is coaxial with the vertical line YL1, and the horizontal line segment is coaxial with the pipe axis line XL2, and the deflection angle A is the bending angle of the inlet centerline S1 from the valve inlet to the central hole.

[0167] Radial center line S 12 All streamlines after the fluid flows out from the central hole are directed in different directions in a radial manner and enter the radial flow path, and the angle of deflection B is the radial center line S of the inlet center line S1. 12 The bending angle is between these points, and all streamlines diffuse C along the radial flow path, and regardless of how many times they are bent due to the limitations of the valve chamber diameter, they flow toward the inner outlet. Radial center line S 12 The fluid velocity of diffusion C slows down after the turning angle B is applied due to the increase in the area of ​​the radial flow path, but after several bends, it flows towards the inner outlet, and also accelerates due to the reduction in area, along the radial center line S 12 The radial flow path may be a straight line, an arc, or a multiple curved arc, depending on the relative position between the radial flow path and the inner outlet.

[0168] Radial center line S 12 The fluid is driven by the pressure difference between the valve inlet and the valve outlet, and the radial center line S of the diffusion C 12 is a jet S 121 and slow flow S 122 The flow is divided into two streams, and the dense streamline receiving a high pressure difference gradient is a jet S with a relatively high flow velocity. 121 Therefore, a low-density streamline receiving a low pressure difference gradient is a slow-flow S 122The flow velocity is somewhat low. The streamlines of the diffusion C flow unfold in a fan shape in the circumferential direction and are affected by the turning angle B, resulting in a jet S 121 The fan-shaped expansion is directed toward the aforementioned inner outlet. Then the slow flow S 122 is a jet S 121 The sector expansion is applied to the circumferential angle other than the sector expansion angle, and the jet S of the portion 121 The remaining jet S flows directly into the inner outlet. 121 and slow flow S 122 The valve chamber is divided into two branches, and the fluid repeatedly reverses direction along its inner diameter before entering the inner outlet. Radial centerline S 12 The jet S of the radial flow path is 121 and slow flow S 122 This induces the fluid in the annular space B2 of the radial gap B3 to form a bifurcated vortex flow, and the jet S 121 and slow flow S 122 The flow shear force generates thrust for the bifurcated vortex flow, and after diffusion, it finally flows into the inner outlet. Under many circumstances, in the bifurcated vortex flow of the annular space B2, there is no problem of particle aggregation, but when the width of the radial gap B3 is too small or there is an inner recess space, there is a problem of particle aggregation. The radial center line S 12 is a jet S 121 and slow flow S 122 Before the two enter the aforementioned inner outlet, each is subjected to a deflection angle D, and the jet S 121 This involves applying a turning angle D1 and creating a slow flow S 122 The jet S is directed with a deflection angle D2. 121 When the jet S crosses the annular space B2, 121 The angle of α1 decreases further as it begins to bend and enters the inner exit, which also represents a decrease in the angle of the turning angle D1.

[0169] The outlet centerline S2 may be a single line segment or a combination of several line segments, and the types of line segments include circular arcs, diagonal line segments, and horizontal line segments. Of these, the horizontal line segment is coaxial with the pipe axis XL2. The turning angle D of the outlet centerline S2 is the radial centerline S 12This is the bending angle between the outlet center line S2 and the valve outlet, and the fluid flows out from the valve outlet after being directed at the inner outlet and the outlet flow path at a deflection angle E.

[0170] The following explanation is based on the condition that the inner diameter ratio is d3 / d0 and 1.75 ≤ d3 / d0 ≤ 2.8. The features of the present invention will be further explained using different embodiments.

[0171] (First embodiment) Referring to Figures 1A to 1C and Figure 2A, a schematic diagram showing the structure and dimensions of the flow path in the first embodiment of structure C5, the inlet center line S1 consists of a horizontal line segment and a circular arc curve, and the outlet center line S2 consists of a horizontal line segment and a circular arc curve. The inlet flow path is constructed by creating a 3D inner diameter curved surface of the inlet flow path, starting from the circumference of the valve inlet and continuing along the inlet center line S1 to the circular central hole with diameter d0, and its cross-section is defined by the upper edge line S 1a and lower edge line S 1b It has the following characteristics.

[0172] The characteristics of this innovation are as follows:

[0173] The aforementioned inlet center line S1 has a straight line segment and a circular arc curve, and has a phase junction P with respect to the pipe axis XL2. 12 The aforementioned circular arc curve has one endpoint as the center point P1 and the other endpoint as the point of tangency P 12 The arc curve and the pipe axis XL2 are at a phase junction P. 12 The two surfaces are tangent to each other, and the circular arc curve has a horizontal distance L. 11 It has L 11 =P 11 P 12 The following conditions are met. The aforementioned straight line segment has one endpoint that is a point of tangency P. 12 Let the other endpoint be the center point P2, 12 Horizontal distance of P2 = L1 - L 11 The conditions are met, and point P 12 By passing through and drawing the vertical line YL6, and by taking point P0 on the vertical line YL6, the line segment P0P 12 And the line segment P0P1 can be made equal in length. 12The angle 2θ1 between and line segment P0P1 is equal to the turning angle A, and the angle of attachment θ1 is equal to line segment P1P 12 It is equal to the horizontal angle of inclusion, and the angle γ1 between the circular arc curve and the vertical line YL1 is obtained at the center point P1 of the central hole, satisfying the condition γ1 = 90° - 2θ1.

[0174] When the included angle γ1 ≠ 0°, the central hole is modified to reduce from a non-standard elongated elliptical hole to a circular hole with diameter d0, and the original major axis is a x a x = The length of E1E2 is reduced to d0. The reduction method is to replace the distal point E1 on the major axis with the distal point E1 * Take the long axis and place the proximal point E2 instead of the proximal point E2 * Take E1 * P1 = P1E2 * The condition =d0 / 2 is satisfied. Major axis a x The length reduction ratio is d0 / a x Let d0 / a x The condition =d0 / E1E2 is satisfied.

[0175] Let the angle of the turning angle A be 2θ1, satisfying the condition 55° ≤ 2θ1 ≤ 105°.

[0176] long axis a x The length reduction ratio is d0 / a x Let 0.7 ≤ d0 / a x The condition ≤ 1.0 is satisfied.

[0177] Partial jet S 121 It flows along the upper half space of the annular groove, and slow flow S 122 The jet S flows along the slope that runs through the lower half of the annular groove. 121 and slow flow S 122 This is crucial for enabling layered flow, and the upper edge line S of the outlet channel. 2a The angle of the turning angle E is 2θ 21 Let 30°≦2θ 21 The condition of ≤90° is met. Slow flow S 122 It flows into the lower half-layer space of the annular groove, and jet S 121The fluid flows into the upper half-layer space of the annular groove, the distal point E3 has a height LH4, the height difference between the distal point E3 and the sealing surface is H1, the proximal point E4 has a height LH5, the proximal point E4 is connected to the bottom of the slope of the annular groove, and satisfies the condition -0.4 ≤ LH5 / d0 ≤ 0.4, and the line segment E3E4 is the major axis a in the Y-axis direction of the inner outlet. y and a y The condition =E3E4 is satisfied.

[0178] The aforementioned outlet center line S2 has a straight line segment and a circular arc curve, and has a phase junction P with respect to the pipe axis XL2. 34 The aforementioned circular arc curve has one endpoint as the center point P3 and the other endpoint as the point of tangency P3. 34 The arc curve and the pipe axis XL2 are at a phase junction P. 34 They are tangent at a horizontal distance LL, and the arc curve is horizontal. 21 It has LL 21 =P 31 P 34 The following conditions are met. The aforementioned straight line segment has one endpoint that is a point of tangency P. 34 Let the other endpoint be the center point P4, 34 Horizontal distance of P4 = LL2 - LL 21 The conditions are met, and point P 34 By passing through and drawing the vertical line YL5, and by taking point P5 on the vertical line YL5, the line segment P5P 34 And make it possible to make the line segment P5P3 equal in length. And line segment P5P 34 The angle 2θ2 between and line segment P5P3 is equal to the turning angle E, and the angle of attachment θ2 is equal to line segment P3P 34 It is equal to the horizontal angle of inclusion, and the angle γ2 between the circular arc curve and the vertical line YL3 is obtained at the center point P3, satisfying the condition γ2 = 90° - 2θ2.

[0179] The aforementioned outlet channels are all maintained with a cross-sectional area of ​​equal diameter, and their upper edge line S 2a , lower edge line S 2b The outlet center line S2 and the three circular arc curve portions all have a common center point P5. The inner outlet is a non-standard elongated ellipse, and the major axis a of the non-standard elongated ellipse is y=E3E4, satisfying the condition E3P3>P3E4, and the minor axis b of the non-standard elongated ellipse. z = d0.

[0180] The aforementioned upper edge line S 2a And the vertical line YL5 is the phase contact point E 35 They intersect at point E 35 Let the height be d0 / 2, and line segment P5E 35 The angle between this point and the line segment P5E3 is 2θ 21 Furthermore, the angle γ between the circular arc curve and the vertical line YL3 at the distal point E3 21 Obtained γ 21 =90°-2θ 21 The condition is satisfied. 2θ 21 When the angle is equal to 90°, the longest major axis a in the inner outlet channel y This indicates that it has the upper edge line S 2a The height value LH4 of the distal point E3 can be obtained via this method. The mounting angle is θ. 21 Let's assume that.

[0181] When the height difference ratio H1 / d0 satisfies the condition H1 / d0 ≤ 0.5, the height of the distal point E3 does not become significant with respect to the difference in head loss. And the long axis ratio a y The larger / d0 is, the lower the head loss becomes, and 2θ 21 When the angle is equal to 90°, the longest major axis a is at the inner outlet. y This indicates that it has. 21 The longer the axis a, the longer the major axis a y This also indicates that the valve becomes longer and the volume of the valve body also increases.

[0182] Jet S 121 Since it flows out horizontally from the radial flow path, the valve opening B1 has a height LH6 and satisfies the condition LH6 ≈ LH3 + B1, and the long axis a y When it is possible to do so, the virtual mirror point E3 * There is a point of reflection, and its height is approximately LH6. The reflection point is E3. * The height difference between the valve seat and the sealing surface is H1 * H1 * The condition ≈B1 is satisfied, and line segment E3 *E 35 The mounting angle θ is equal to the horizontal angle of attachment. 21 * You can obtain line segment E3 * E4 introduces a new long axis a y * A line segment E3 is formed. * E 35 The angle between the point and the horizontal line is the mounting angle θ. 21 * And among them, θ 21 * ≤θ 21 The conditions are met, and the portion of the jet S 121 This is due to the direct entry from the radial flow path to the internal outlet, and the mounting angle θ. 21 * The jet S of the portion that flows directly into the inner outlet using 121 It is more appropriate to use this to describe the angle of deflection D of the jet S in this part. 121 As the jet S crosses the annular space, the streamlines begin to curve and flow easily and smoothly into the inner outlet. The above description applies to the jet S that directly enters the inner outlet. 121 This allows for a more accurate understanding of the angle of α1, and furthermore, it is understood that the actual angle of α1 is even lower.

[0183] Said lower edge line S 2b And the vertical line YL5 is the phase contact point E 46 They intersect at point E 46 Let the height of the line segment P5E be -d0 / 2. 46 The angle between this point and the line segment P5E4 is 2θ 22 Furthermore, the lower edge line S is located at the proximal point E4. 2b The angle between and the vertical line YL3 is γ 22 Obtained γ 22 =90°-2θ 22 The conditions are met, and the lower edge line S 2b The height value LH5 of the proximal point E4 can be obtained via this method. The mounting angle is θ. 22 Let's assume that.

[0184] Upper edge line S of the outlet channel 2a The angle of the turning angle E is 2θ 21 Let 30°≦2θ21 The conditions are met such that the angle is ≤90°, there is a height difference H1 between the distal point E3 and the valve seat, the conditions are -0.6 ≤ H1 / d0 ≤ 0.68, the proximal point E4 and the bottom of the slope are in contact with each other, the height of the proximal point E4 is LH5, the conditions are -0.4 ≤ LH5 / d0 ≤ 0.4, and the angle β of the slope of the annular groove is the included angle θ 22 This approximates the equation and satisfies the condition 8° ≤ β ≤ 20°.

[0185] When necessary, to further strengthen the valve seat, vertical rib plates are added to the outer diameter surface of the valve seat, and these vertical rib plates are located on the side of the inner outlet. Their lower portions are connected to the bottom of the annular groove, and both sides of the vertical rib plate are vertical arcuate surfaces, with one side of each arcuate surface on both sides in contact with the outer diameter surface of the valve seat to form a wide bottom side, and the other sides of each arcuate surface on both sides intersect to form an end with a small arcuate angle. The vertical rib plates can also act as guides for streamlines that branch out from the annular groove and flow toward the inner outlet.

[0186] As a preferred example A, 2θ 21 When the angle is equal to 90°, the following parameters can be taken:

[0187] Horizontal length LL of the exit center line S2 21 However, 2.0 ≥ LL 21 When the condition / d0≧0.5 is satisfied, the major axis a y The ratio of to the diameter d0 is 1.4 ≤ a y The condition / d0 ≤ 2.2 is satisfied.

[0188] θ² and θ 22 The angular range is as follows, where the angle of the turning angle E of the outlet channel is 2θ2, and the condition 30° ≤ 2θ2 ≤ 74° is satisfied, and the lower edge line S of the outlet channel 2b The angle of the turning angle E is 2θ 22 Let 14°≦2θ 22 The condition ≤54° is met.

[0189] As a preferred example B, 2θ 21The following parameters take place when the angle is equal to 30°.

[0190] Horizontal length LL of the exit center line S2 21 However, 2.0 ≥ LL 21 When the condition / d0≧0.5 is satisfied, the major axis a y The ratio of to the diameter d0 is 1.06 ≤ a y The condition / d0 ≤ 1.12 is satisfied.

[0191] θ² and θ 22 The angular range is as follows, where the angle of the turning angle E of the outlet channel is 2θ2, and the condition 20° ≤ 2θ2 ≤ 28° is satisfied, and the lower edge line S of the outlet channel 2b The angle of the turning angle E is 2θ 22 Let 15°≦2θ 22 The condition ≤26° is met.

[0192] (Second example) Referring to Figures 1A to 1C and Figure 2B, a schematic diagram showing the structure and dimensions of the flow path in the second embodiment of structure C5, the inlet center line S1 consists of a horizontal line segment and a circular arc, and the outlet center line S2 consists of a horizontal line segment and a diagonal line segment.

[0193] The characteristics of this innovation are as follows:

[0194] Based on the first embodiment, the outlet channel is constructed and the inner outlet is maintained in a non-standard elliptical shape, but the outlet center line S2 and the upper edge line S of the outlet channel are maintained. 2a , the lower edge line S 2b Change this to a combination of straight line segments, line segment P3P 34 The center point P3 and the point of tangency P 34 Connect them, and line segment E3E 35 The distal point E3 and the phase junction E 35 Connect them, and line segment E4E 46 The proximal point E4 and the phase junction E 46 Connecting the two. Starting from the circumference of the non-standard ellipse of the inner outlet, a 3D inner diameter curved surface diagram of the outlet flow path is created along the outlet center line S2 to reach the circular valve outlet, and its cross section is defined by the upper edge line S2a and lower edge line S 2b It has the following characteristics.

[0195] point P 34 By passing through and drawing the vertical line YL5, and by taking point P5 on the vertical line YL5, the line segment P5P 34 And make it possible to make the line segment P5P3 equal in length. And line segment P5P 34 The angle 2θ2 between and line segment P5P3 is equal to line segment P3P 34 The angle of rotation E is equal to the angle of attachment θ2, and the angle of attachment θ2 is equal to the line segment P3P 34 It is equal to the horizontal angle of reference.

[0196] The aforementioned line segment P3P 34 Let the mounting angle be θ2, and the turning angle D of the center point P3 be θ2, then θ2 = Atan(LH2 / LL 21 The conditions of ) are met.

[0197] The aforementioned line segment E3E 35 The mounting angle is θ 21 And the turning angle D of the distal point E3 is θ 21 Let θ 21 =Atan((LH4-d0 / 2) / LL 21 The conditions of ) are met.

[0198] The aforementioned line segment E4E 46 The mounting angle is θ 22 Let the turning angle D of the proximal point E4 be θ 22 Let θ 22 =Atan((LH5+d0 / 2) / LL 21 The conditions of ) are met.

[0199] The exit center line S2 is the contact point P 34 The first bending is performed with a turning angle E, so the turning angle E = θ².

[0200] The aforementioned upper edge line S 2a is phase contact E 35 The first bending is performed at a turning angle E, where the turning angle E = θ 21 That is the case.

[0201] Said lower edge line S 2b is phase contact E46 The first bending is performed at a turning angle E, where the turning angle E = θ 22 That is the case.

[0202] The angle of rotation of distal point E3 is D = θ 21 Therefore, 14°≦θ 21 The condition ≤45° is met.

[0203] Contact point E 35 The angle of rotation E = θ 21 Therefore, 14°≦θ 21 The condition ≤45° is met.

[0204] The angle of rotation at the proximal point E4 is D = θ 22 Therefore, 7°≦θ 22 The condition ≤20° is met.

[0205] Contact point E 46 The angle of rotation E = θ 22 Therefore, 7°≦θ 22 The condition ≤20° is met.

[0206] (Third embodiment) Referring to Figures 1A to 1C and Figure 2C, a schematic diagram showing the structure and dimensions of the flow path in the third embodiment of structure C5, the inlet center line S1 consists of a horizontal line segment and a circular arc, and the outlet center line S2 consists of a horizontal line segment and a diagonal line segment.

[0207] The characteristics of this innovation are as follows:

[0208] Based on the first and second embodiments, the outlet channel is constructed, and the inner outlet is maintained as a non-standard ellipse. The shape of the inner outlet is then further modified from the original non-standard ellipse to a rectangle, so that the non-standard ellipse is inscribed within the rectangle. Both have the same major axis a y The same short axis b z It has the same distal point E3 and the same proximal point E4, the four right angles of the rectangle are modified to four small rounded angles, and the outlet center line S2 and the upper edge line S of the outlet channel 2a , the lower edge line S 2bChange it to a combination of straight line segments. Line segment P3P 34 The center point P3 and the point of tangency P 34 Connect them, and line segment E3E 35 The distal point E3 and the phase junction E 35 Connect them, and line segment E4E 46 The proximal point E4 and the phase junction E 46 The two are connected. Starting from the rectangular circumference of the inner outlet, a 3D inner diameter curved surface diagram of the outlet flow path is created along the outlet center line S2 to reach the circular valve outlet, and its cross section is defined by the upper edge line S 2a and lower edge line S 2b It has the following characteristics.

[0209] point P 34 By passing through and drawing the vertical line YL5, and by taking point P5 on the vertical line YL5, the line segment P5P 34 And make it possible to make the line segment P5P3 equal in length. And line segment P5P 34 The angle 2θ2 between and line segment P5P3 is equal to line segment P3P 34 The angle of rotation E is equal to the angle of attachment θ2, and the angle of attachment θ2 is equal to the line segment P3P 34 It is equal to the horizontal angle of reference.

[0210] The aforementioned line segment P3P 34 Let the mounting angle be θ2, and the turning angle D of the center point P3 be θ2, then θ2 = Atan(LH2 / LL 21 The conditions of ) are met.

[0211] The aforementioned line segment E3E 35 The mounting angle is θ 21 And the turning angle D of the distal point E3 is θ 21 Let θ 21 =Atan((LH4-d0 / 2) / LL 21 The conditions of ) are met.

[0212] The aforementioned line segment E4E 46 The mounting angle is θ 22 Let the turning angle D of the proximal point E4 be θ 22 Let θ 22 =Atan((LH5+d0 / 2) / LL 21 The conditions of ) are met.

[0213] The exit center line S2 is the contact point P 34 The first bending is performed with a turning angle E, so the turning angle E = θ².

[0214] The aforementioned upper edge line S 2a is phase contact E 35 The first bending is performed at a turning angle E, where the turning angle E = θ 21 That is the case.

[0215] Said lower edge line S 2b is phase contact E 46 The first bending is performed at a turning angle E, where the turning angle E = θ 22 That is the case.

[0216] The angle of rotation of distal point E3 is D = θ 21 Therefore, 14°≦θ 21 The condition ≤45° is met.

[0217] Contact point E 35 The angle of rotation E = θ 21 Therefore, 14°≦θ 21 The condition ≤45° is met.

[0218] The angle of rotation at the proximal point E4 is D = θ 22 Therefore, 7°≦θ 22 The condition ≤20° is met.

[0219] Contact point E 46 The angle of rotation E = θ 22 Therefore, 7°≦θ 22 The condition ≤20° is met.

[0220] (Fourth embodiment) Refer to Figures 1A to 1C, and Figure 2D, a schematic diagram showing the structure and dimensions of the flow path in the fourth embodiment of structure C5. The inlet center line S1 consists of a horizontal line segment and a circular arc, and the outlet center line S2 consists of a horizontal line segment and a circular arc.

[0221] The characteristics of this innovation are as follows:

[0222] Based on the first embodiment, the outlet channel is constructed, the inner outlet is maintained in a non-standard elliptical shape, the distal point E3 is higher than the sealing surface of the valve seat, and when adjustment of the height of the distal point E3 is necessary, the upper edge line S of the outlet channel is set. 2a A portion of the circular arc S3 can be tangent to it, and a new distal point E3 ** They intersect at the distal point E3 ** There is a height difference H1 between the valve seat and the valve seat. ** It has H1 ** ≥B1, 0.25≦H1 ** The condition / d0 ≤ 0.5 is satisfied. And line segment E3 ** The new long axis formed at E4 is a y ** In addition, a tangent curved surface SS is created along the arc S3 of the outlet channel and the inner diameter surface, and the distal point E3 ** The angle γ between the arc S3 and the perpendicular line YL3 at that point. 21 ** It has a relatively large angle, 30°≦γ 21 ** ≤90°, θ 21 ** =90°-γ 21 ** The conditions are met. Part of the jet S 121 When the material enters the inner outlet directly, it is made possible to flow along the tangential curved surface SS, and the angle of its turning angle D1 is reduced. This item refers to the upper edge line S of the outlet flow path. 2a The purpose of the modification is to obtain a suitable height for the valve chamber while still maintaining high flow rate performance of the flow path.

[0223] Distal point E3 ** The angle of the turning angle D is θ 21 ** Let 0°≦θ 21 ** The condition ≤60° is met.

[0224] The new major axis of the ellipse is a y ** Let 2d0 ≥ a y ** The condition ≥ 1.3d0 is satisfied.

[0225] (Fifth example) Referring to Figures 1A to 1C and Figure 2E, a schematic diagram showing the structure and dimensions of the flow path in the fifth embodiment of structure C5, the inlet center line S1 consists of a horizontal line segment and a circular arc, and the outlet center line S2 consists of a horizontal line segment and a circular arc.

[0226] The characteristics of this innovation are as follows:

[0227] Based on the first embodiment, the inlet passage and the outlet passage are constructed, and the inner diameter d3 of the valve chamber and the outer diameter d1 of the valve seat are designed to be eccentric, thereby making the structure of the valve chamber a hollow circular eccentric structure, dividing the structure of the valve chamber into a valve plug chamber with a diameter of 1.8d0 and an annular chamber with a diameter of 2.2d0, setting the deviation of the concentricity between the valve plug chamber and the annular chamber to 0.2d0, setting the height of the top of the interior of the annular chamber to LH7, and positioning the valve plug chamber and the valve seat concentrically so that a vertical line YL1 passes through them. The valve chamber is used to receive the valve plug, and the horizontal distance between the center point P1 of the valve seat on the valve inlet side and the inner diameter of the annular chamber is 0.9d0, and the horizontal distance between the center point P1 of the valve seat and the inner diameter of the annular chamber on the inner outlet side is 1.3d0, and the annular chamber receives the annular space and the annular groove, and the width B2 of the annular groove changes according to the eccentric design so that it has its maximum width on the inner outlet side. There is a height difference H5 between the top of the inside of the annular chamber and the sealing surface of the valve seat, satisfying the conditions H5 = LH7 - LH3 and 0.6 ≥ H5 / d0 ≥ 0.25, and the long axis a of the inner outlet y Since is larger than the central hole diameter d0, 2.2≧a y The condition / d0≧1.3 is satisfied. In this case, although such a value can be obtained in terms of drawing and calculation, in practice, modifications based on the fifth embodiment are necessary to satisfy the needs of the actual flow path.

[0228] Since the height LH4 of the distal point E3 can also be higher than the height LH7, the condition LH4 > LH7 is satisfied. In this case, the distal point E3 is the major axis a y A new distal point E3 above ** We need to find distal point E3 **From there, a portion of the arc S3 is applied to form the upper edge line S 2a It is adjacent to the distal point E3. ** The height difference between the valve seat and the valve seat is H1 ** 0.25d0≦H1 ** It is secured such that the condition ≤ 0.5d0 is satisfied. And line segment E3 ** The new long axis formed at E4 is a y ** In addition, the inner diameter surface and tangent curved surface SS of the outlet channel created along the arc S3 are created, and the distal point E3 ** The angle γ between the arc S3 and the perpendicular line YL3 at that point. 21 ** It has a relatively large angle, 30°≦γ 21 ** The condition ≤90° is met, and the distal point E3 ** The angle of the turning angle D is θ 21 ** Let 0°≦θ 21 ** The condition ≤60° is satisfied, and the new major axis of the ellipse is a y ** Let 2.0d0≧a y ** The condition ≥ 1.3d0 is satisfied (concave arc S3 and tangent surface SS are formed in the same manner as in the fourth embodiment).

[0229] (Sixth embodiment) Based on the first embodiment, refer to Figures 1A to 1C and Figure 2F, a schematic diagram showing the structure and dimensions of the flow path in the sixth embodiment of structure C5. The inlet center line S1 consists of a horizontal line segment and a circular arc, and the outlet center line S2 consists of a horizontal line segment and a circular arc.

[0230] The characteristics of this innovation are as follows:

[0231] Based on the first embodiment, the inlet channel is constructed, and the outlet channel is constructed using the embodiment, the sealing surface of the valve seat is located outside the central hole, and a conical tube coaxial with the vertical line YL1 is installed on the central hole. The conical tube has a center point P DPThe conical tube has a height of LH3 at the sealing surface of the valve seat, a height of LH1 at the central hole, and a height h at the conical angle φ, satisfying the condition LH3 = LH1 + h. The function of the conical tube is to provide a diffusion effect for the fluid and its inlet center line S1, and to further facilitate the deflection angle B so that the fluid can enter the radial flow path. This function can further reduce head loss, and secondly, the conical tube increases the structural strength of the valve seat and enhances the reliability of the seal.

[0232] The height h of the conical tube satisfies the condition 0.06 ≤ h / d0 ≤ 0.2.

[0233] The cone angle φ of a conical tube satisfies the condition 15° ≤ φ ≤ 60°.

[0234] The above six embodiments will be described in detail below, satisfying the needs of the constraints.

[0235] Restriction 1: The valve seat provides highly reliable sealing performance, and in the first to sixth embodiments of structure C5, the angle 2θ1 of its deflection angle A satisfies the condition 55° ≤ 2θ1 ≤ 105°, providing reliable strength for the valve seat. In the sixth embodiment, the height h of the conical tube satisfies the condition 0.06 ≤ h / d0 ≤ 0.2, further increasing the strength of the valve seat. If necessary, additional vertical rib plates on the outer diameter surface of the valve seat can further improve the strength of the valve seat and enhance the reliability of the sealing performance.

[0236] Restriction 2: The inlet and outlet are on the same straight line, and the center point P2 of the valve inlet and the center point P4 of the valve outlet in the first to sixth embodiments of structure C5 pass through the pipe axis XL2.

[0237] Restriction 3: The valve body cannot have a cleanliness problem, and the inlet and outlet channels of the first, second, third, fourth, fifth, and sixth embodiments of structure C5 are all smooth curved pipes or inclined pipes. Furthermore, the valve chamber does not have a sealed retention area, an open retention area, or a circulating flow section, and problems such as particle aggregation and liquid residue are eliminated. The position of the inner outlet covers the position where the distal point E3 of the inner outlet is added to the radial flow path, the height of the proximal point E4 is LH5, and the condition -0.4 ≤ LH5 / d0 < 0.4 is satisfied, the height at which the fluid flows diagonally downward can be reduced, and after the fluid flowing into the annular groove enters the inner outlet, a swirling flow can be generated in the outlet channel, completely eliminating the circulating flow section and further eliminating problems such as particle aggregation and liquid residue.

[0238] Restriction 4: The inner diameter ratio of the valve body satisfies the condition 1.75 ≤ d3 / d0 ≤ 2.8, and the inner diameter ratio of the optimal embodiment of structure C5 is set to 2.0, so there is no problem of the volume becoming excessive. In the fifth embodiment, the valve chamber employs an eccentric design, and the inner diameter of the annular chamber is set to 2.2, and the inner diameter ratio of the valve plug chamber is set to 1.8, so there is no problem of the volume becoming excessive.

[0239] Restriction 5: The novel flow path structure of the valve body must satisfy the selection and use of a variety of manufacturing methods and materials. The first, second, third, fourth, fifth, and sixth embodiments of structure C5 can all be manufactured using metal casting. In the first embodiment, the outlet centerline and the inlet centerline can be manufactured using injection molding only if both are single arcs. The fourth embodiment is also applicable to injection molding, the fifth embodiment is also applicable to injection molding depending on the needs, and the sixth embodiment is also applicable to injection molding.

[0240] Regarding the six examples described above, we have already addressed the problems and proposed solutions, which are explained below.

[0241] In the characteristics of structure C5, both the inlet centerline and the outlet centerline are based on a curved circular flow path, the inlet centerline is a circular curve, and the outlet centerline is a circular curve or a straight line sloping downwards. The height LH4 of the distal point E3 is higher than the valve seat, the height LH5 of the proximal point E4 satisfies the condition -0.4 ≤ LH5 / d0 < 0.4, and the jet S 121 It enters the upper half space of the annular groove, and slow flow S 122 This allows the jet S to flow into the lower half of the annular groove. 121 and slow flow S 122 This allows the layered flow of the annular groove to maintain the maximum radius of curvature between the inlet centerline, the radial centerline, and the outlet centerline, while simultaneously avoiding flow interference within the valve chamber and flow interference at the inner outlet. This feature makes it possible to smooth the bends of the streamlines at the turning angle B, diffusion C and turning angle D, while simultaneously maintaining the lowest possible head loss coefficient ξ, such that 1.7 ≤ ξ ≤ 3.0, C V The condition ≥ 73.5 is met.

[0242] Problem 1: When the height difference ratio H1 / d0 of distal point E3 satisfies the condition H1 / d0 ≥ 0.5, what is the relationship between distal point E3 and the corresponding point E3? * The space between them is not an effective flow space and also results in additional head loss. E3E3 * The larger the space, the more new major axis a y * This indicates that the length becomes shorter, and the actual flow area of ​​the aforementioned inner outlet decreases.

[0243] Problem 1: New major axis a y * or major axis ratio a y * The larger / d0 is, the greater the jet S 121 and slow flow S 122 This indicates that the layered flow in the annular groove becomes preferable, reducing flow interference and decreasing head loss.

[0244] Problem 1: Mirror point E3 * Line segment E3 * E35 Mounting angle θ 21 * The mounting angle θ of line segment E3E5 21 Less than or equal to, with an mounting angle θ 21 * is a jet S 121 This represents the angle of deflection D as the jet approaches the target. 121 The mirror point E3 of the aforementioned inner outlet * When the flow path space between and the center point P3 is excessive, a new major axis a y * or aspect ratio a y * When / d0 is reduced to an excessively small value, the jet S 121 The radius of curvature is reduced, resulting in additional head loss.

[0245] Problem 1: The second and third embodiments can achieve the same effect by employing a straight line segment flow path, the fourth embodiment considers a method for correcting when the position of the distal point E3 is too high, and in the fifth embodiment, the purpose of adopting an eccentric design for the valve chamber is the jet S 121 The objective is to obtain a better radius of curvature for the streamlines, and in the sixth embodiment, the conical tube is added above the central hole. The purpose is to increase the diffusion function and the jet S 121 The key to achieving this effect is reducing the angle of the turning angle B, and all of the above embodiments can obtain the same effect.

[0246] Problem 1: From the inlet channel to the outlet channel, a smooth jet S flows through both channels. 121 It is possible to maintain streamlines and a good radius of curvature. One of the features of the first embodiment of structure C5 is that preferred embodiment A has an upper edge line S of the outlet flow path. 2a The angle of rotation E is 2θ 21 However, 2θ 21 =90°, the height of the distal point E3 is LH4, the condition LH4 > LH3 is satisfied, and the major axis ratio a y / d0 is 1.3≦a y The condition / d0 ≤ 2.2 is satisfied, and the area of ​​the inner outlet can completely cover the radial flow path. Furthermore, the area of ​​the upper half of the inner outlet is made larger than the area of ​​the lower half, and the jet S121 flows obliquely downward toward the upper half opening of the inner outlet after undergoing a fan-shaped expansion in the radial flow path and crossing the annular groove, with the jet flow S 121 When the streamline of reaches the inner outlet, it is possible to maintain a smooth radius of curvature.

[0247] Problem 1: From the inlet flow path to the outlet flow path, it is possible to maintain a good radius of curvature for the streamline of the smooth jet flow S 121 and, as one of the features of the first embodiment of structure C5, a preferred embodiment B has the upper edge line S of the outlet flow path 2a with a turning angle E of 2θ 21 where 2θ 21 = 30°, with the height of the far point E3 being LH4, satisfying the condition LH4 < LH3, and the major axis ratio a y / d0 satisfies the condition 1.06 ≦ a y / d0 ≦ 1.12, and the jet flow S 121 is subjected to a first turning angle D1 of 90° downward from the diffusion C. Then, two turning angles D1 (with an angle of 60°) are applied to the far point E3, and the turning angle E of the lower edge line S of the outlet flow path 2b has an angle 2θ 22 where 14° ≦ 2θ 22 ≦ 26°, and when the slow flow S[[ID=2-eight]] 122 flows on the slope of the annular groove, the angle when flowing into the near point E4 after applying two turning angles D2 decreases significantly. The streamline of the jet flow S 121 is enabled to avoid the streamline of the slow flow S 122 and it is possible to maintain the laminar flow in the annular groove and reduce the flow interference at the inner outlet.

[0248] Problem 1: With the height of the near point E4 being LH5, satisfying the condition -0.4 ≦ LH5 / d0 < 0.4, and the turning angle D at the near point E4 being close to the slope angle of the annular groove, the slow flow S 122 does not cause interference with the jet flow S 121 when the slow flow S 122The inclined surface of the annular groove can guide more fluid towards the lower half opening of the inner outlet.

[0249] Problem 1: From the inlet channel to the outlet channel, a smooth jet S flows through both channels. 121 It is possible to maintain a good streamline and radius of curvature, the inlet channel of structure C5 is a smooth channel, and the angle 2θ1 of the deflection angle A satisfies the condition 55° ≤ 2θ1 ≤ 105°, making it possible to maintain a smooth inlet centerline, and when the fluid enters the radial channel after passing through the deflection angle B, the deflection angle B is applied to make it smooth and to cause diffusion C within the valve chamber.

[0250] Problem 1: In the fifth embodiment, the horizontal distance between the center point P1 of the valve seat and the inner diameter of the annular chamber on the side of the inner outlet is set to 1.3d0, and furthermore, when the streamline enters the inner outlet, a sufficient bending space can be provided.

[0251] Problem 1: In the sixth embodiment, the height h of the conical hole has a conical angle φ and a diffusion function, and when the fluid flows out from the central hole, it is possible to provide an opportunity to diffuse and increase the radius of curvature of the bend, thereby reducing the angle of the deflection angle B and reducing the head loss coefficient ξ.

[0252] Problem 1: The first and second embodiments will be described. In both embodiments, the bending angle of the outlet flow path is 2θ2. In the first embodiment, the flow path is a smoothly curved flow path, and its turning angle D is 2θ2. When the fluid enters the inner outlet, there is some loss, but by setting the turning angle E to 2θ2, it does not result in any additional loss. It has a low head loss coefficient ξ. In the second embodiment, the turning angle D is θ2, which reduces the entry loss of the jet. In the second embodiment, the outlet flow path is a bend with an obtuse angle, and the angle of its turning angle E θ2 results in a slightly higher head loss coefficient ξ, while still maintaining a low head loss coefficient ξ for the overall outlet flow path.

[0253] Problem 1: Reduce the central hole from a non-standard elongated elliptical hole to a circular hole with diameter d0, and the major axis a x The length reduction ratio is 0.7 ≤ d0 / a x The condition ≤1.0 is satisfied, and the inlet channel can be maintained within the substantial cross-sectional area of ​​the central hole without being excessively reduced, and is caused to increase the head loss coefficient ξ. Only with sufficient space can a rational distribution of streamlines be maintained in the channel, and a more favorable deflection angle B be maintained when the fluid flows out of the central hole.

[0254] Problem 2: Jet S 121 The angle between the direction and the outlet center line S2 is reduced, and the jet S 121 This is achieved by performing diffusion C, which causes the streamlines to be distributed in a fan shape. The fan-shaped streamlines are distributed on the side of the inner outlet, and the jet S 121 After flowing into the annular groove, it flows diagonally downward toward the inner outlet, forming a jet S 121 The flow of the material diagonally downwards significantly reduces the angle α1 between it and the outlet centerline S2. This satisfies the condition α1 = (90° - γ2) rather than the high angle or 90° at the distal point E3.

[0255] Problem 2: Jet S 121 The angle between the direction and the axis line XL2 of the outlet flow path is reduced, and in preferred embodiment A of the first embodiment, the height LH4 of the distal point E3 of the inner outlet is higher than the height LH3 of the sealing surface of the valve seat. The condition LH4 > LH3 is satisfied, and the long axis a y The ratio of to the diameter d0 is 1.3 ≤ a y The jet S satisfies the condition / d0 ≤ 2.2. 121 When diffusion C is applied to the radial flow path and it crosses the annular groove, it is possible to allow it to flow diagonally downward with sufficient space. Furthermore, it is possible to reduce the upper half area that enters the inner outlet at the angle α1 with the outlet center line S2, and thus it is possible to significantly reduce the head loss coefficient ξ.

[0256] Problem 2: Jet S 121Reduce the included angle between the direction of and the axis center line XL2 of the outlet flow path. In the preferred embodiment B of the first embodiment, the height LH4 of the far point E3 of the inner outlet is lower than the height LH3 of the sealing surface of the valve seat, satisfying the condition of LH4 < LH3, and the long axis a y The ratio of to the diameter d0 is 1.06 ≦ a y / d0 ≦ 1.12, so that when the diffusion C of the jet flow S 121 crosses the annular groove, a first turning angle D1 of 90° downward can be applied. When passing through the far point E3, apply the second turning angle D1 in advance, and set the angle as γ 21 and satisfy the condition of 0° ≦ γ 21 ≦ 60°, and the included angle α1 between the jet flow S 121 and the outlet center line S2 can be reduced, and the head loss coefficient ξ can be reduced.

[0257] Problem 2: Reduce the included angle α2 between the streamline of the slow flow S 122 and the outlet center line S2 of the inner outlet. The streamline of the slow flow S 122 crosses the valve seat in the circumferential direction other than the fan-shaped expansion of the jet flow S 121 and enters the annular groove. Set the height of the near point E4 in the first embodiment as LH5, satisfy the condition of -0.4 ≦ LH5 / d0 < 0.4, and the near point E4 and the bottom of the annular groove are connected to each other at the bottom of the inclined surface. And the difference in the angles between the inclined angle β of the inclined surface and the turning angle D of the near point E4 is relatively close. The slow flow S 122 is bent obliquely downward with a 3D solid angle along the annular groove and enters the inner outlet. It may also reduce the included angle α2, and the streamline of the slow flow S 122 acquires a larger radius of curvature.

[0258] Problem 2: It is possible to maintain a small included angle α3 between the streamlines between the jet flow S 121 and the slow flow S 122 . After the jet flow S 121 in the first embodiment undergoes a fan-shaped expansion or when crossing the annular groove, the streamlines of a number of jet flows S 121 all flow towards the upper half area of the inner outlet. And the slow flow S 122 is the jet flow S121 After the sector-shaped expansion is carried out in the circumferential direction outside the sector-shaped expansion, it flows into the annular groove, and a large number of slow flows S 122 The streamlines flow along the slope of the annular groove and enter the lower half area of ​​the inner outlet. Jet S 121 and slow flow S 122 Before entering the aforementioned inner outlet, the jet S does not cause a sudden interference between them. 121 and slow flow S 122 The small angle α3 between the streamlines is kept relatively small, preventing the occurrence of flow interference phenomena at the inner outlet. However, the jet S 121 and slow flow S 122 In this case, a swirling flow occurs in the flow path after the material enters the inner outlet, and such swirling flow can significantly reduce the circulating flow conditions that occur in the outlet flow path, thereby significantly reducing the formation of particle aggregation. [Effects of the Invention]

[0259] Based on the above discussion of structure C5, it is essential to make the distal point E3 of the inner outlet higher than the sealing surface to have a height difference H1, and to set the height of the proximal point E4 to LH5, and satisfy the condition -0.4 ≤ LH5 / d0 < 0.4, the line segment E4E of the inner outlet 46 Mounting angle θ 22 To enable this, 7°≦θ 22 The condition of ≤20° is met, and slow flow S 122 The turning angle D2 entering the aforementioned inner outlet can be significantly reduced. Structure C5 can achieve the innovation goal, and the head loss coefficient ξ satisfies the condition ξ≦3.0, with the comparison criteria being B1 / d0=0.25, d3 / d0=2.0, and d0=52.5mm. [Brief explanation of the drawing]

[0260] [Figure 1A] This is a schematic diagram showing the structure and coordinate points of the flow channel in structure C5. [Figure 1B] This is a cross-sectional view along the IB-IB line in Figure 1A. [Figure 1C]This is a schematic diagram showing the mounting angle θ and turning angles 2θ, θ1, θ2, θ21, θ22, 2θ1, 2θ2, 2θ21, 2θ22 of structure C5, as well as streamlines S1, S12, S2, and turning angles A, B, C, D, and E. [Figure 2A] This is a schematic diagram showing the flow channel structure of the first embodiment of structure C5. [Figure 2B] This is a schematic diagram showing the flow channel structure of the second embodiment of structure C5. [Figure 2C] This is a schematic diagram showing the flow channel structure of the third embodiment of structure C5. [Figure 2D] This is a schematic diagram showing the flow channel structure of the fourth embodiment of structure C5. [Figure 2E] This is a schematic diagram showing the flow channel structure of the fifth embodiment of structure C5. [Figure 2F] This is a schematic diagram showing the flow channel structure of the sixth embodiment of structure C5. [Figure 3A] These are cross-sectional structural diagrams and streamline distribution diagrams of the conventional C4 structure. [Figure 3B] This is a top view of the fan-shaped unfolded streamline of the valve chamber in the conventional structure C4. [Figure 3C] This is a diagram showing the flow path of the conventional structure C4 viewed from a 45-degree angle. [Figure 4A] These are the cross-sectional structure diagram and streamline distribution diagram of the conventional structure C4 with Improvement 1 applied. [Figure 4B] This is a top view of the fan-shaped unfolded streamline of the valve chamber of the conventional structure C4 with Improvement 1 applied. [Figure 4C] This is a view of the flow path of the conventional structure C4 with Improvement 1 applied, seen from a 45-degree angle. [Figure 5A] These are the cross-sectional structure diagram and streamline distribution diagram of the conventional structure C4 with Improvement 2 applied. [Figure 5B] This is a top view of the fan-shaped unfolded streamline of the valve chamber of the conventional structure C4 with Improvement 2 applied. [Figure 5C] This is a view of the flow path of the conventional structure C4 with Improvement 2 applied, seen from a 45-degree angle. [Figure 6A] This shows a cross-sectional structure diagram and a streamline distribution diagram of a preferred embodiment A of structure C5 according to the first embodiment. [Figure 6B]This is a top view of the fan-shaped unfolded streamline of the valve chamber in a preferred embodiment A of structure C5 according to the first embodiment. [Figure 6C] This is a view of the flow path of a preferred embodiment A of structure C5 according to the first embodiment, seen from a 45-degree angle. [Figure 6D] This schematic diagram shows a preferred embodiment A of structure C5 according to the first embodiment, further increasing the number of vertical rib plates on the outer diameter surface of the valve seat to enhance structural strength and guiding the streamlines flowing toward the inner outlet. [Figure 7A] These are a cross-sectional structure diagram and a streamline distribution diagram of structure C5 according to the second embodiment. [Figure 7B] This is a top view of the fan-shaped unfolded streamline of the valve chamber of structure C5 according to the second embodiment. [Figure 7C] This is a view of the flow path of structure C5 according to the second embodiment, seen from a 45-degree angle. [Figure 8A] This shows a cross-sectional structure diagram and a streamline distribution diagram of structure C5 according to the third embodiment. [Figure 8B] This is a top view of the fan-shaped unfolded streamline of the valve chamber of structure C5 according to the third embodiment. [Figure 8C] This is a view of the flow path of structure C5 according to the third embodiment, seen from a 45-degree angle. [Figure 9A] This shows a cross-sectional structure diagram and a streamline distribution diagram of structure C5 according to the fourth embodiment. [Figure 9B] This is a top view of the fan-shaped unfolded streamline of the valve chamber of structure C5 according to the fourth embodiment. [Figure 9C] This is a view of the flow path of structure C5 according to the fourth embodiment, seen from a 45-degree angle. [Figure 10A] This shows a cross-sectional structure diagram and a streamline distribution diagram of structure C5 according to the fifth embodiment. [Figure 10B] This is a top view of the fan-shaped unfolded streamline of the valve chamber of structure C5 according to the fifth embodiment. [Figure 10C] This is a view of the flow path of structure C5 according to the fifth embodiment, seen from a 45-degree angle. [Figure 11A] This shows a cross-sectional structure diagram and a streamline distribution diagram of structure C5 according to the sixth embodiment. [Figure 11B] This is a top view of the fan-shaped unfolded streamline of the valve chamber of structure C5 according to the sixth embodiment. [Figure 11C] This is a view of the flow path of structure C5 according to the sixth embodiment, seen from a 45-degree angle. [Figure 12A] This shows a cross-sectional structure diagram and a streamline distribution diagram of a preferred embodiment B of structure C5 according to the first embodiment. [Figure 12B] This is a top view of the fan-shaped unfolded streamline of the valve chamber in a preferred embodiment B of structure C5 according to the first embodiment. [Figure 12C] This is a view of the flow path of a preferred embodiment B of structure C5 according to the first embodiment, seen from a 45-degree angle. [Figure 13A] This is a schematic diagram showing the coordinate axes, coordinate points, and streamlines S1, S12, S121, S122, and S2 of the flow path of a conventional structure C3. [Figure 13B] This is a schematic diagram showing the mounting angle, turning angle A, turning angle B, diffusion C, turning angle D, and turning angle E of the flow path in the conventional structure C3. [Figure 14A] This is a schematic diagram showing the coordinate axes, coordinate points, and streamlines S1, S12, S121, S122, and S2 of the flow path of a conventional structure C4. [Figure 14B] This is a schematic diagram showing the turning angles A, B, C, D, and E of the flow channel in a conventional structure C4. [Modes for carrying out the invention]

[0261] The structural features of the flow path of structure C5 in the first embodiment (see Figure 6A) are that it comprises a smoothly curved inlet flow path 6, a valve chamber 5, a horizontal radial flow path 7, an annular groove 53 with a sloped bottom 531, and a smoothly curved outlet flow path 8, wherein the radial flow path 7 is composed of the inner concave surface 542 of the bottom of the valve plug 54 and the sealing surface 510 of the valve seat 51 and has a flow path height B1, the distal point E3 of the inner outlet 82 of the outlet flow path 8 is higher than the valve seat 51 and the proximal point E4 is lower than the valve seat 51, and the inner diameter ratio d3 / d0 of the inner diameter d3 of the valve chamber 5 to the valve inlet diameter d0 satisfies the condition 1.75 ≤ d3 / d0 ≤ 2.8.

[0262] According to the structure of structure C5 in the first embodiment, the following effects can be achieved. The smoothly curved inlet channel 6 has a turning angle A (inlet centerline S1) and does not generate a circulating flow section N, and the turning angle B of the central hole 63 is jet S 121 and slow flow S 122 The fluid includes a reasonable distribution in the circumferential direction, and the fluid flows through the radial channel 7 to form a jet S. 121 The diffusion C (the radial center line S) of the sector-shaped expansion 12 ) is applied, and when it flows into the annular groove 53, the jet S 121 and slow flow S 122 In a stratified flow including the above, there is no flow interference inside the valve chamber 5, and the deflection angle D at which the fluid enters the inner outlet 82 is the jet S 121 The angle of change D1 and the slow flow S 122 This includes the turning angle D2, eliminating flow interference at the inner outlet 82. In preferred embodiment A, the inner outlet 82 has a longer longitudinal axis a y (Figure 6A) has 1.3 ≤ a y The condition / d0 ≤ 2.2 is satisfied, and the jet S 121 and slow flow S 122 It is possible to provide sufficient space for the flow into the inner outlet 82, and the smoothly curved outlet channel 8 has a deflection angle E (the outlet centerline S2), and there is no generation of an internal circulating flow section N, and the long axis a of the inner outlet 82 y The valve seat 51 is completely covered at this height, so the jet S 121 and slow flow S 122 This can enable layered flow in the space of the annular groove 53. In preferred embodiment B, the long axis a of the inner outlet 82 y (Figure 12A) shows that 1.06 ≤ a y The condition / d0 ≤ 1.12 is satisfied, and the jet S 121 This allows for the jet S to be provided with a turning angle D1 applied twice early when flowing through the distal point E3. 121 and slow flow S 122 This enables layered flow in the space of the annular groove 53, and the head loss coefficient ξ of structure C5 is based on an inner bore diameter of 52.5 mm, C V This includes satisfying the conditions ≥ 73.5 and 1.7 ≤ ξ ≤ 3.0.

[0263] Below, d0 = 52.5 mm, d3 / d0 = 2, B1 = 0.25d0 = 13.14 mm, L1 = L 12 Using the condition of =90mm, we compared 3D computational fluid dynamics (CFD) software for four different flow path structures and analyzed the flow field. V After obtaining estimated values ​​and explaining the characteristics of this novel structure, the schematic diagrams showing the flow field analysis calculations below concisely represent the contents of the diagrams by drawing streamlines using flow field analysis software, and the streamline distribution is explained by drawing eight streamlines for each example of the embodiment.

[0264] In Case A, the results of the analysis calculation of the flow field of the conventional structure C4 are shown in Figure 3A.

[0265] In Case Study B, Figure 4A is shown for the local improvement of the flow path, as calculated by analyzing the flow field of the conventional structure C4 after improvement 1 was applied.

[0266] In Case Study C, Figure 5A is referenced for another local improvement to the flow path, showing the results of the flow field analysis calculation of the conventional structure C4 with Improvement 2 applied.

[0267] In Example D, the results of the analysis calculation of the flow field of structure C5 according to the present invention are shown in Figure 6A, which illustrates the first embodiment.

[0268] Furthermore, we will continue to study and discuss the flow path analysis of structure C5 according to the present invention. In Example E, the second embodiment is shown in Figure 7A. In Example F, the third embodiment is shown in Figure 8A. In Example G, the fourth embodiment is shown in Figure 9A. In Example H, the fifth embodiment is shown in Figure 10A. In Example I, the sixth embodiment is shown in Figure 11A.

[0269] In the following, the structural parameters used in each case are the long axis a of the central hole 63. xThe height of (E1E2 in Figure 1A) is LH1, and the height of the sealing surface 510 is LH3, and it is mounted around the central hole 63, with a sealing ring 511 provided on top of it. The inlet center line S1 has an angle between the central hole 63 and the vertical line YL1 of γ1 (Figure 1C), the opening of the radial flow path is B1, the height of the radial flow path is LH6, the height of the center point P3 is LH2, the height of the distal point E3 is LH4, the height of the proximal point E4 is LH5, and the mounting angle of the line segment E3E5 is θ 21 Let the mounting angle of the P3P4 line segment be θ2, and the mounting angle of the E4E6 line segment be θ 22 The long axis of the inner outlet is a y Let the major axis a y The mirror point E3 above * The line segment E3 * E4 is the long axis a y * E3 * The mounting angle of line segment E5 is θ 21 * (Figures 1B and 1C)

[0270] <Case Study A: Flow path analysis of conventional structure C4> Refer to Figure 3A, which shows the cross-sectional structure and streamline distribution diagram of the conventional structure C4. Refer to Figure 3B, which is a top view of the fan-shaped unfolded streamline of the valve chamber 5 in the conventional structure C4. The radial center line S of the conventional structure C4 12 Refer to Figure 3C, which shows the turning angle D at the aforementioned inner outlet 82 viewed from a 45-degree angle (see Figures 1A to 1C together).

[0271] C V The value is C V The conditions ≈ 61.89 < 73.5 and ξ ≈ 4.23 > 3.0 are satisfied.

[0272] Inlet passage 6 is a horizontal straight pipe, and flows out from the central hole 63 of the valve seat 51 with the right angle 60 pointing upwards, LH3=LH1=36mm, γ1=0°, a x The condition =d0 is satisfied.

[0273] The annular groove 53 is installed between the outer diameter d1 of the valve seat 51 and the inner diameter d3 of the valve chamber 5, and the bottom of its inclined surface 531 and its proximal point E4 are at the same height.

[0274] The radial channel 7 is an annular channel that radiates horizontally with a valve opening B1.

[0275] The outlet passage 8 is a horizontal straight pipe, and the distal point E3 of the inner outlet 82 is lower than the sealing surface 510 of the valve seat 51, LH4 <LH3、LH6=49.14mm、LL2=LL 21 =78.75mm, LH4=26.25mm, H1=-9.75mm, LH2=0mm, LH5=-26.25mm, a y = 52.5 mm, a y * = 52.5 mm, θ 21 =0°, θ 21 * =0°, θ²=0°, θ 22 The condition = 0° is satisfied.

[0276] At the turning angle A and the inlet centerline S1, several circulating flow sections N in the inlet flow path 6 of the inlet centerline S1 are clearly affected by a right-angle bend of 60 degrees, as shown in the figure, along the upper edge line S 1a A large circulating flow section N exists in the region immediately adjacent to the central hole 63. In this circulating flow section N, the distribution of streamlines S is irrationally aligned with the lower edge line S 1b This causes a deflection to the side, resulting in a reduction in the effective area of ​​the inlet channel 6.

[0277] At the angle of change B, the lower edge line S 1b When the fluid on the side flows out from the central hole 63, some of the streamlines cross the circulating flow section N immediately adjacent to the central hole 63 of the inlet channel 6 and are ejected toward the distal point E1, while also flowing into the radial channel 7 and becoming a slow flow S. 122 The angle of the turning angle B is less than 90°, and some of the other streamlines S are along the lower edge line S 1b It is ejected upward along the inner wall and flows into the radial channel 7 to form the jet S. 121is formed, the angle of the turning angle B approaches 90°, and according to the area of the occupied flow path of the circulating flow region N in the figure, the flow rate of the inlet flow path 6 can be reduced, and it is not possible to flow into the radial flow path 7 with a relatively low angle of the turning angle B.

[0278] Diffusion C clearly generates a bifurcated spiral flow in the annular space B2 of the radial gap B3, but there is no problem of particle aggregation.

[0279] Diffusion C, radial center line S 12 In a sector expansion, the height LH4 of the far point E3 is lower than the height LH3 of the sealing surface 510 of the valve seat 51, satisfying the condition of LH4 < LH3, and the jet flow S 121 cannot rapidly flow into the inner outlet 82 due to the restriction of the inner diameter of the valve chamber 5, and the streamline S of the jet flow S 121 is at an angle exceeding 180° in the sector expansion in the radial flow path 7, and the sector expansion of the slow flow S 122 is expanded to the remaining circumferential angle (see Figure 3B).

[0280] The turning angle D includes the turning angle D1 of the jet flow S 121 and the turning angle D2 of the slow flow S 122 For both the jet flow S 121 and the slow flow S 122 to flow into the annular groove 53, it is necessary to apply a 90° downward bend, which is the first turning angle D.

[0281] At the turning angle D, the flow interference in the valve chamber 5 between the jet flow S 121 and the slow flow S 122 is such that for the streamline S of both the jet flow S 121 and the slow flow S 122 to enter the annular groove 53 at the first turning angle D of the streamline S, a downward bend of 90° must be applied. Some of the streamline S of the jet flow S 121 directly enters the inner outlet 82 with the shortest distance, and the flow distance of the slow flow S 122 is relatively long, and a 90° downward turning angle D needs to be applied. For the jet flow S 121 and the slow flow S 122Disturbing the layered flow in the space within the annular groove 53 and bending downward at a 90° turning angle D clearly increases flow interference inside the valve chamber 5.

[0282] At a turning angle D, the jet S 121 and slow flow S 122 Flow interference at the inner outlet 82 is due to jet S 121 The main streamline S, after being constrained by the inner diameter of the valve chamber 5, enters the annular groove 53 downwards, passes through the distal point E3, and then a second turning angle D1 is applied to the horizontal outlet flow path 8, and its bending angle also approaches 90°, satisfying the condition α1 ≈ 90°, and the jet S 121 R is a relatively small radius of curvature. C Because it requires a certain flow, it cannot directly enter the upper half space of the inner outlet 82, but rather enters by passing through the lower half space of the inner outlet 82. And such a radius of curvature R C is a jet S 121 For the streamline S to flow into the lower half space of the inner outlet 82, it is necessary to pass over the pipe axis XL2, as well as the upper edge line S within the outlet channel 8. 2a A circulating flow section N is generated on the inner diameter surface, creating a region where a single particle aggregates.

[0283] At turning angle D, slow flow S 122 The streamline S flows along the slope 531 at the bottom of the annular groove 53, satisfying the condition α2≈β, and undergoes two turning angles D2 before the proximal point E4, changing its angle from the oblique angle β to horizontal, and then enters the lower half space of the inner outlet 82. At this time, the slow flow S 122 and jet S 121 When it enters the lower half of the space of the inner outlet 82, it directly causes flow interference, satisfying the condition α3 ≈ 90°-β.

[0284] At a turning angle E, the outlet channel 8 is installed as a horizontal straight pipe, and its turning angle E is set to 0°, but the jet S 121 and slow flow S 122 When the fluid enters the inner outlet 82, there is significant interference and the creation of a circulating flow section N. As a result, the fluid needs to diffuse into the outlet channel 8, which can still lead to additional head loss.

[0285] Regarding the flow path of the conventional structure C4, when examined and discussed while referring to FIG. 3A, having a right angle of 60° at the turning angle A is a contributing factor to significant head loss, causes a reduction in the area of the flow path, and due to the flow obstruction of the central hole 63 in the circulating flow region N, the angle of the turning angle B of the streamline S approaches 90° in each case, which is also a contributing factor to head loss. And the outlet flow path 8 is installed as a horizontal straight pipe, and when the far point E3 is caused to be lower than the sealing surface 510 of the valve seat 51, when allowing the streamline S of the radial flow path 7 to be radially developed, the jet flow S 121 Since the streamline of cannot flow into the annular groove 53 directly due to the restriction of the inner diameter of the valve chamber 5, it must be bent downward by 90° inevitably. At the first turning angle D1 and the turning angle D2, the jet flow S of the part flowing directly toward the inner outlet 82 121 actually performs a reverse U-shaped rotation, which is also a contributing factor to head loss. And the jet flow S 121 When entering the inner outlet 82, it is still necessary to apply the second turning angle D1 like a fold approaching a 90° angle, which causes more head loss. Finally, the jet flow S 121 and the slow flow S 122 cause serious interference at the inner outlet 82 and result in head loss. The C value of the flow path of the structure C4 V satisfies the conditions of C V ≒61.89 < 73.5, ξ≒4.23 > 3.0, which all lead to the inability to achieve high flow rate requirements.

[0286] <Case B: Flow Path Analysis of Conventional Structure C4 (Improvement 1)> Refer to FIG. 4A, which is a cross-sectional structure diagram and streamline distribution diagram of the conventional structure C4 with Improvement 1 applied. [[ID=二十五]]Refer to FIG. 4B, which is a top view of the fan-shaped development of the streamline of the valve chamber 5 of the conventional structure C4 with Improvement 1 applied. Refer to FIG. 4C, which is a view of the turning angle D at the inner outlet 82 of the radial center line S 12 of the conventional structure C4 with Improvement 1 applied, viewed from an angle of 45 degrees (refer to FIGS. 1A to 1C together).

[0287] C V The value satisfies the condition of C V ≒69.88 < 73.5, ξ≒3.32 > 3.0.

[0288] The inlet flow path 6 is an arc-shaped curved pipe, with the turning angle A facing upward and flowing out from the central hole of the valve seat 51. LH3 = LH1 = 59.34 mm, γ1 = 23.2°, d0 / a x ≒0.911 satisfies the condition.

[0289] The annular groove 53 is installed between the outer diameter d1 of the valve seat 51 and the inner diameter d3 of the valve chamber 5, and the bottom of its inclined surface 531 and the near point E4 are at the same height.

[0290] The radial flow path 7 is an annular flow path that has a valve opening B1 and radiates horizontally.

[0291] The outlet flow path 8 is a horizontal straight pipe. The far point E3 of the inner outlet 82 is lower than the sealing surface 510 of the valve seat 51. LH4 < LH3, LH6 = 72.48 mm, LL2 = LL 21 = 52.5 mm, LH4 = 26.25 mm, H1 = -33.09 mm, LH2 = 0 mm, LH5 = -26.25 mm, a y = 52.5 mm, a y * = 52.5 mm, θ 22 = 0°, θ 21 = 0°, θ 21 * = 0°, θ2 = 0° satisfies the condition. <000250​​​​​​​The radius of curvature R c is relatively small, the flow velocity is relatively fast, and the streamlines S are relatively dense. Therefore, as shown in FIG. 4A, many streamlines S are bent from the side of the upper edge line S 1a towards the center hole 63 and flow towards the side of the near point E2 and enter the radial flow path 7 to form the jet flow S 121 while some other streamlines S are bent and flow towards the far point E1 and flow into the radial flow path 7 to form the slow flow S 122 This kind of flow causes the angle of the turning angle B to decrease slightly to a certain extent and is smooth. Although the area of the flow path decreases due to the included angle γ1, the smooth flow path only causes a certain head loss.

[0294] Diffusion C, radial center line S 12 In the fan-shaped expansion, the height LH4 of the far point E3 is lower than the height LH3 of the sealing surface 510 of the valve seat 51, satisfying the condition of LH4 < LH3. The jet flow S 121 cannot flow rapidly into the inner outlet 82 due to the restriction of the inner diameter of the valve chamber 5. The streamlines S of the jet flow S 121 have an angle of fan-shaped expansion in the radial flow path 7 that does not exceed 180°. The fan-shaped expansion of the slow flow S 122 is expanded to the remaining circumferential angle, clearly causing a two-branched spiral flow in the annular space B2 of the radial gap B3, but there is no problem of particle aggregation.

[0295] At the turning angles D and E, the outlet flow path 8 in this case is the same as the outlet flow path 8 in Case A, with flow interference in the valve chamber 5 and flow interference at the inner outlet 82, and the generation of one circulating flow region N.

[0296] Regarding the flow path of the conventional structure C4 with Improvement 1, when examined while referring to FIG. 4A, the turning angle A is an arc angle, which can significantly reduce the local head loss and can cause a reduction in the area of the flow path. However, the angles of the turning angle B that are not affected by the obstacle of the circulating flow region N all decrease to a certain extent, which is also another factor contributing to the reduction of the local head loss. And the outlet flow path 8 is installed as a horizontal straight pipe. Since the far point E3 is lower than the sealing surface 510 of the valve seat 51, when the streamlines S of the radial flow path 7 can be expanded by 360°, the jet flow S121 and slow flow S 122 The streamlines are constrained by the inner diameter of the valve chamber 5, and therefore must be bent downwards at 90° in order to flow into the annular groove 53. While this can reduce some flow interference within the valve chamber 5, it may not be effective, and the first turning angles D1 and D2 are also contributing factors to the head loss. 121 When it enters the inner outlet 82, it is still necessary to make a second turning angle D1, like a bend that approaches a 90° angle again, which results in more head loss, and finally the jet S 121 and slow flow S 122 This causes serious flow interference at the inner outlet 82 and results in a loss of head, and the flow path of the conventional structure C4 with improvement 1 is C V The value is C V The conditions ≈69.88<73.5 and ξ≈3.32>3.0 are met, and the original structure C4 of Case A is C V Although this is approximately 12.91% higher than the value, it still results in the inability to achieve the high flow rate requirement due to the limitations of the outlet flow path.

[0297] <Case Study C: Flow path analysis of conventional structure C4 (Improvement 2)> Refer to Figure 5A, which shows the cross-sectional structure and streamline distribution diagram of the conventional structure C4 with Improvement 2 applied. Refer to Figure 5B, which is a top view of the fan-shaped unfolded streamline of the valve chamber 5 of the conventional structure C4 with Improvement 2 applied. Radial centerline S of the conventional structure C4 with Improvement 2 applied 12 Refer to Figure 5C, which shows the turning angle D at the inner exit 82 viewed from a 45-degree angle (see Figures 1A to 1C together).

[0298] C V The value is C V The conditions ≈ 64.09 < 73.5 and ξ ≈ 3.94 > 3.0 are satisfied.

[0299] Inlet passage 6 is a horizontal straight pipe, and flows out from the central hole of the valve seat 51 with a right angle 60 pointing upwards, LH3=LH1=59.34mm, γ1=0°, a x The condition =d0 is satisfied.

[0300] The annular groove 53 is installed between the outer diameter d1 of the valve seat 51 and the inner diameter d3 of the valve chamber 5, and the bottom of its inclined surface 531 and its proximal point E4 are at the same height.

[0301] The radial channel 7 is an annular channel that radiates horizontally with a valve opening B1.

[0302] The outlet passage 8 is a curved pipe, and the height LH4 of the distal point E3 of the inner outlet 82 is higher than the sealing surface 510 of the valve seat 51, so LH4 > LH3, LH6 = 72.48 mm, H1 ≈ 19.41 mm, LH2 = 20.05 mm, LL2 = LL 21 =52.5mm, LH4=78.75mm, LH2=20.05mm, LH5=-12.18mm, a y =90.93mm, a y * = 84.66 mm, θ 21 =45°, θ 21 * =41.36°, θ²=22.46°, θ 22 The condition of =15.0° is met.

[0303] With a turning angle A, an inlet centerline S1, and a turning angle B, the inlet channel 6 in this case is the same as the inlet channel 6 in case A. Based on the area of ​​the occupied channel in the circulating flow section N adjacent to the central hole 63 of the inlet channel 6, it is possible to reduce the flow rate of the inlet channel 6, and it is not possible to flow into the radial channel 7 with a relatively low turning angle B.

[0304] Diffusion C, radial centerline S 12 In the sector unfolded shape, the distal point E3 is higher than the sealing surface 510 of the valve seat 51, the condition LH4 > LH3 is satisfied, the geometry of the inner outlet 82 is a non-standard ellipse, and the major axis a y The ratio of to the diameter d0 is a y The condition / d0=1.732 is satisfied, and the height of the proximal point E4 is LH5, and the condition LH5=-12.18mm is satisfied, and the jet S is influenced by the circulating flow section N that is closest to the central hole 63. 121The streamline S is clearly susceptible to the influence of a circulating flow section N similar to that in case A, but the jet S of diffusion C in this case 121 The streamline S can flow directly into the inner outlet 82, and the angle after sector formation does not exceed 180°, resulting in a slow flow S 122 The sector-shaped expansion extends to the remaining circumferential angle, clearly creating a bifurcated vortex flow in the annular space B2 of the radial gap B3, but without the problem of particle aggregation.

[0305] The angle of deflection D is equal to the jet S. 121 The angle of change D1 and the slow flow S 122 Since the deflection angle D2 is included and the distal point E3 is higher than the sealing surface 510 of the valve seat 51, the jet S 121 and slow flow S 122 The downward bend allows for a significant reduction in the angle of the turning angle D into the annular groove 53. At the first turning angle D, the conditions H1 ≈ 19.41 mm and B1 ≈ 13.14 mm indicate that the radial flow path 7 is interposed and covered between the center point P3 and the distal point E3. The angle of the turning angle D at the center point P3 satisfies the condition 2θ2 = 44.91°, and the reflection point E3 * Line segment E3 * The new long axis formed at E4 is a y * Assuming LH6 = 72.465 mm, a y * / d0=1.612, θ 21 * The condition of =41.35° is met, and numerous jets S 121 The reflection point is E3 * This indicates that the jet S flows in from the space between the central point P3 and the inner outlet 82. 121 When the vehicle enters the inner exit 82, the angle of the turning angle D satisfies the condition 44.91° < turning angle D < 82.7°, and an excessively high H1 indicates that the turning angle D has an additional head loss.

[0306] At a turning angle D, the jet S 121 and slow flow S 122 The flow interference within valve chamber 5 is due to jet S 121 and slow flow S 122For the first turning angle D of the streamline S to enable entry into the annular groove 53, a downward bend smaller than 90° can be applied. Among them, a part of the jet flow S 121 of the streamline S enters the inner outlet 82 with a smaller bending angle and the shortest distance, and the remaining jet flow S 121 has a gradually longer flow distance and needs to be turned with a relatively large downward turning angle D. The slow flow S 122 has the longest flow distance and needs to be turned with a larger downward turning angle D, so that the jet flow S 121 and the slow flow S 122 can be made to form a laminar flow in the space within the annular groove 53. The jet flow S 121 flows along the upper half space of the annular groove 53, and the slow flow S 122 flows along the inclined surface 531 along the lower half space of the annular groove 53. The jet flow S 121 and the slow flow S 122 significantly reduces the flow interference in the valve chamber 5.

[0307] At the turning angle D, the flow interference of the jet flow S 121 and the slow flow S 122 at the inner outlet 82 is such that the jet flow S 121 still flows in the upper half space of the annular groove 53 and applies the second turning angle D1, and more easily enters the upper half space of the inner outlet 82. By setting the height of the near point E4 of the inner outlet 82 as LH5 and satisfying the condition LH5 = -12.18 mm, the slope angle β of the inclined surface 531 at the bottom of the annular groove 53 can be made smaller. The slow flow S 122 flows along the inclined surface 531 along the lower half space of the annular groove 53 and applies the second turning angle D2, and can also more easily flow into the lower half space of the inner outlet 82. The included angle between the second turning angle D1 of the jet flow S 121 and the outlet center line S2 is α1, and satisfies the condition α1 ≒ 22.455° - 39.285°. The jet flow S 121 acquires a relatively large radius of curvature R C and can flow into the outlet channel 8, and such a radius of curvature R C is for a small number of jet flows S 121For only the streamlines of the jet S to flow into the lower half of the inner outlet 82, they must cross the pipe axis XL2. 121 and slow flow S 122 Flow interference at the inner outlet is significantly reduced, and the upper edge line S inside the outlet flow path 8 is reduced. 2a There is no generation of a single circulating flow section N on the inner diameter surface, and there is no problem of particle aggregation.

[0308] At turning angle D, slow flow S 122 The streamline S flows along the slope 531 at the bottom of the annular groove 53, satisfying the condition α2≈β, and also applies two turning angles D2 before the proximal point E4, and the angle is taken from the oblique angle β to the line segment E4E 46 Mounting angle θ 22 It is converted to this state and enters the lower half space of the inner outlet 82, and the jet S 121 This acquires a flow with a relatively large radius of curvature and smoothly enters the upper half space of the inner outlet 82, resulting in a slow flow S 122 Since it also smoothly enters the lower half space of the inner outlet 82, the slow flow S 122 and jet S 121 Only minor fluid interference occurs between them, satisfying the condition α3 ≈ α1 - α2.

[0309] At a turning angle E, the outlet channel 8 is installed as a curved pipe with a turning angle E of 2θ2, but a smooth curved pipe does not cause high head loss, and the jet S 121 and slow flow S 122 Although there is minor interference between the two, there is no excessive increase in head loss for the outlet channel 8, and in addition, there is no generation of a circulating flow section N, and no problem of particle aggregation.

[0310] When examining the flow path of the conventional structure C4 with Improvement 2 applied, with reference to Figure 5A, the fact that the turning angle A has a right angle of 60 is a significant cause of head loss, as well as reducing the area of ​​the flow path. Furthermore, the flow obstruction to the central hole 63 of the circulating flow section N causes the angle of the turning angle B of the streamlines S to approach 90°, which is also a cause of head loss. As a result, consistent with the situation in Figure 3A, flow interference within the valve chamber 5 excluding the circulating flow section N of the flow path is clearly reduced. The outlet channel 8 has a smooth, curved pipe structure, with the distal point E3 higher than the valve seat 51, and the long axis a y When the diameter of the central hole 63 is made larger than the diameter d0, the streamlines of the radial flow path 7 can be expanded 360°, the jet S 121 The streamlines, in order to allow entry into the upper half space of the annular groove 53, require only a small downward first turning angle D1, which clearly reduces flow interference between the jet and the slow flow at the inner outlet, and this is also referred to as a minor head loss. However, due to limitations imposed by the inlet flow path, the inherent superiority of the flow separation function of the streamlines of the jet and the slow flow cannot be fully realized. Finally, the flow path of the conventional structure C4 with Improvement 2 applied. V The value is C V The conditions ≈64.09 < 73.5 and ξ ≈ 3.94 > 3.0 are met. From this result, it can be seen that the innovation goal has still not been achieved, and the improvement of the original structure C4 is 1 C V The value is about 3.55% higher than the conventional structure C4 with improvement 1 applied. V The value is slightly smaller than expected, and its improvement effect is inferior to that of the conventional structure C4 with Improvement 1 applied.

[0311] <Case D: Flow path analysis of structure C5 according to the present invention (preferred example A of the first embodiment)> Refer to Figure 6A, which shows the cross-sectional structure and streamline distribution diagram of structure C5 according to the first embodiment. Refer to Figure 6B, which is a top view of the fan-shaped unfolded streamline of the valve chamber 5 of structure C5 according to the first embodiment. Radial center line S of structure C5 according to the first embodiment 12 Refer to Figure 6C, which shows the turning angle D at the inner exit 82 viewed from a 45-degree angle (see Figures 1A-1C and 2A together).

[0312] The innovation in this section combines the local innovations in Case B and Case C to form a complete innovation pathway.

[0313] C V The value is C V The conditions ≈ 82.89 > 73.5 and ξ ≈ 2.36 ≤ 3.0 are satisfied.

[0314] The inlet channel 6 is a curved arc-shaped pipe, with a deflection angle A facing upwards, and the fluid flows out from the central hole 63 of the valve seat 51. LH3=LH1=59.34mm, γ1≈23.2°, d0 / a x The condition ≈ 0.911 is met.

[0315] The annular groove 53 is installed between the outer diameter d1 of the valve seat 51 and the inner diameter d3 of the valve chamber 5, and the bottom of its inclined surface 531 and its proximal point E4 are at the same height.

[0316] The radial channel 7 is an annular channel that radiates horizontally with a valve opening B1.

[0317] The outlet passage 8 is a curved pipe, and the height LH4 of the distal point E3 of the inner outlet 82 is higher than the sealing surface 510 of the valve seat 51, LH4 > LH3, LH6 = 72.48 mm, LL2 = LL 21 =68.25mm, LH4=94.5mm, H1=35.16mm, LH2=29.14mm, LH5=-5.12mm, a y =99.61, a y * =77.59, θ 21 =45°, θ 21 * =34.11°, θ²=25.273°, θ 22 The condition of =17.21° is met.

[0318] With a turning angle A, an inlet center line S1, and a turning angle B, the inlet channel 6 in this case is similar to the inlet channel 6 in case B, the inlet channel 6 is an arc-shaped channel, and with a turning angle A pointing upward, it flows out from the central hole 63 of the valve seat 51, γ1 ≈ 23.2°, d0 / a x The condition of approximately 0.911 is satisfied. Although the flow enters the radial channel 7 with a relatively low deflection angle B, and the effective cross-sectional area of ​​the channel decreases, there is no curvature of the circulating flow section N and the streamlines, and the effective cross-sectional area is still much higher than that of the conventional example shown in Figure 3A.

[0319] Diffusion C, radial centerline S 12In the sector unfolded shape, the distal point E3 is higher than the sealing surface 510 of the valve seat 51, the condition LH4 > LH3 is satisfied, the geometry of the inner outlet 82 is a non-standard ellipse, and the major axis a y The ratio of to the diameter d0 is a y The condition / d0 = 1.8974 is satisfied, and the height of the proximal point E4 is LH5, and the condition LH5 = -5.12 mm is also satisfied. Diffusion C jet S 121 The streamline S can flow directly into the inner outlet 82, and the angle after sector formation does not exceed 180°, resulting in a slow flow S 122 The sector-shaped expansion extends to the remaining circumferential angle, clearly creating a bifurcated vortex flow in the annular space B2 of the radial gap B3, but without the problem of particle aggregation.

[0320] The angle of deflection D is equal to the jet S. 121 The angle of change D1 and the slow flow S 122 Since the deflection angle D2 is included and the distal point E3 is higher than the sealing surface 510 of the valve seat 51, the jet S 121 and slow flow S 122 This allows for a downward bend, which can greatly reduce the angle of the turning angle D into the annular groove 53. At the first turning angle D, the angle of the turning angle D at the center point P3 satisfies the condition 2θ² = 50.55°, and line segment E3 * The new long axis formed at E4 is a y * a y * / d0=1.48, LH6=72.465mm, a y * =77.585mm, θ 21 * The condition of =34.1° is met, and many fluids have a mirror point E3 * This indicates that the fluid flows in from the space of the inner outlet 82 between the center point P3 and the center point P3, and when the fluid can enter the inner outlet 82, the angle of the deflection angle D satisfies the condition 50.55° < deflection angle D < 68.2°. If H1 is too high, it indicates that the deflection angle D has an additional head loss, and by setting the height of the proximal point E4 of the inner outlet 82 to LH5 and satisfying the condition LH5 = -5.12 mm, the angle β of the slope 531 at the bottom of the annular groove 53 can be reduced, and some of the jet S 121The streamline S enters the inner outlet 82 with a smaller bending angle and the shortest distance. The remaining jet S 121 The flow distance gradually increases, and a relatively large downward deflection angle D is required, resulting in a slow flow S 122 The flow distance is longest, and a large downward deflection angle D is required, resulting in the jet S 121 and slow flow S 122 This enables layered flow in the space within the annular groove 53. Slow flow S 122 The streamline S flows along the slope 531 at the bottom of the annular groove 53, satisfying the condition α2≈β, and also applies two turning angles D2 before the proximal point E4, and the angle is taken from the oblique angle β to the line segment E4E 46 Mounting angle θ 22 It is converted to this state and enters the lower half space of the inner outlet 82, and the jet S 121 It flows along the upper half space of the annular groove 53. And the slow flow S 122 The jet S flows along the slope 531 that runs along the lower half space of the annular groove 53. 121 and slow flow S 122 This allows slight flow interference to occur within the valve chamber 5, and the jet S 121 Let α1 be the angle between the deflection angle D1 and the outlet centerline S2, satisfying the condition α1 ≈ 50.55° ~ 68.2°. 121 This has a relatively large radius of curvature R. C Once obtained, it can flow into the outlet channel 8, and such a radius of curvature R C is a small number of jets S 121 For only the streamlines to flow into the lower half space of the inner outlet 82, they must cross the pipe axis XL2. The upper edge line S inside the outlet channel 8 2a There is no generation of a single circulating flow section N on the inner diameter surface, and there is no problem of particle aggregation, resulting in a jet S 121 and slow flow S 122 This results in slight flow interference at the inner outlet 82.

[0321] At the turning angle E, the outlet channel 8 in this case is similar to the outlet channel 8 in case C, and the outlet channel 8 is installed as a curved pipe with a turning angle E of 2θ2, but the smooth curved pipe does not cause high head loss, and the jet S 121and slow flow S 122 Although there is minor interference between the two, there is no excessive increase in head loss for the outlet channel 8, and in addition, there is no generation of a circulating flow section N, and no problem of particle aggregation.

[0322] When examining the flow path of structure C5 according to the first embodiment, the deflection angle A is an arc angle, which significantly reduces local head loss and allows for a reduction in the flow path area. However, the angle of deflection angle B, which is not affected by the circulating flow section N, is reduced to some extent, and this is another factor contributing to the reduction in local head loss. The outlet flow path 8 is a smooth arc curved pipe structure, with the distal point E3 higher than the sealing surface 510 of the valve seat 51, and the long axis a y When the diameter of the central hole 63 is made larger than the diameter d0, the streamlines S of the radial flow path 7 can be expanded 360°, the jet S 121 The streamlines only need to be directed downwards at a small angle for the first turning, D1, in order to allow entry into the upper half space of the annular groove 53, and this also results in a minor loss of head. And the jet S 121 When it enters the inner outlet 82, it is still necessary to make a second turning angle D1, like a small bend, and this results in a slight loss of head, and finally the jet S 121 and slow flow S 122 The inner outlet 82 between and has a relatively small gripping angle α3, and the jet S 121 and slow flow S 122 This allows for the swirling flow within the outlet channel 8 between them, eliminating the circulating flow with a turning angle E of 2θ2. Finally, the flow path C of the novel structure C5 V Obtain the value, C V The conditions ≈ 82.89 > 73.5 and ξ ≈ 2.36 ≤ 3.0 are satisfied, and the conventional structure C4, improvement 1, and improvement 2 C V All values ​​are significantly higher than the actual values ​​(11% to 54%), and can fully satisfy high flow rate requirements. Referring to Figure 6D, vertical rib plates 512 are added to the outer diameter surface of the valve seat 51 to further strengthen the valve seat 51 when necessary. The vertical rib plates 512 are located on the side of the inner outlet 82, and their lower portion is connected to the bottom of the annular groove 53. Both sides of the vertical rib plates 5122 are vertical arcuate surfaces 5121 and 5122, and one side of both arcuate surfaces 5121 and 5122 on both sides is in contact with the outer diameter surface of the valve seat 51 to form a wide bottom side, while the other sides of both arcuate surfaces 5121 and 5122 on both sides intersect to form an end 5123 with a small arc angle. The vertical rib plates 512 can act as guides for the streamlines S that branch out from the annular groove 53 and flow toward the inner outlet 82.

[0323] <Case Study E: Flow path analysis of structure C5 according to the present invention (Second embodiment)> Refer to Figure 7A, which shows the cross-sectional structure and streamline distribution diagram of structure C5 according to the second embodiment. Refer to Figure 7B, which is a top view of the fan-shaped unfolded streamline of the valve chamber 5 of structure C5 according to the second embodiment. Radial center line S of structure C5 according to the second embodiment 12 Refer to Figure 7C, which shows the turning angle D at the inner exit 82 viewed from a 45-degree angle (see Figures 1A-1C and 2B together).

[0324] C V The value is C V The conditions ≈ 81.32 > 73.5 and ξ ≈ 2.45 ≤ 3.0 are satisfied.

[0325] In the second embodiment, the structure of the flow path is configured with reference to the first embodiment, and the outlet flow path 8 has a similar non-standard elliptical inner outlet 82, with its upper edge line S 2a Replace with a straight line segment E3E5, and lower edge line S 2b Replace it with a straight line segment E4E6.

[0326] The inlet passage 6 is a curved pipe with an arc shape, and the fluid flows out from the central hole 63 of the valve seat 51 with a deflection angle A facing upward, satisfying the conditions LH3=LH1=59.34mm and γ1≈23.2°.

[0327] The annular groove 53 is installed between the outer diameter d1 of the valve seat 51 and the inner diameter d3 of the valve chamber 5, and the bottom of its inclined surface 531 and its proximal point E4 are at the same height.

[0328] The radial channel 7 is an annular channel that radiates horizontally with a valve opening B1.

[0329] The outlet channel 8 is an inclined pipe, and the height LH4 of the distal point E3 of the inner outlet 82 is higher than the sealing surface 510 of the valve seat 51, LH4 > LH3, LH6 = 72.48 mm, LL2 = LL 21 =68.25mm, LH4=94.5mm, H1=35.16mm, LH2=29.14mm, LH5=-5.12mm, a y =99.61, a y * =77.59, θ 21 =45°, θ 21 * =34.11°, θ²=25.27°, θ 22 The condition of =17.21° is met.

[0330] The turning angle A, the inlet centerline S1, and the turning angle B are similar to the streamline S and turning angles A and B shown in Figure 6A.

[0331] Diffusion C, radial centerline S 12 The sector expansion is similar to the sector expansion of streamline S shown in Figure 6B.

[0332] The angle of change D satisfies the condition 25.27° < angle of change D < 34.11°, where θ² is the angle of change D, and is similar to the angle of change D of the streamline S shown in Figure 6A, and the jet S 121 The angle of change D1 and the slow flow S 122 The jet S includes the angle of deflection D2. 121 and slow flow S 122 This has only minor flow interference within the valve chamber 5, and the jet S 121 and slow flow S 122 This results in only minor flow interference at the inner outlet 82.

[0333] Referring to Figure 7A, the outlet channel 8 is a straight pipe segment installed at an angle downwards, with a turning angle E of θ2 and an elbow angle. However, even with the relatively smooth bend of the elbow angle, high head loss is not generated, there is no formation of a circulating flow section N, and there is no problem of particle aggregation.

[0334] When examining the flow path of structure C5 according to the second embodiment, by setting the deflection angle D to θ2, the jet S 121 and slow flow S 122 It is possible to introduce the jet S into the upper and lower halves of the annular groove 53 at a relatively low angle. 121 and slow flow S 122 The flow swirls within the outlet channel 8 between them, eliminating the circulating flow in the elbow angle region where the turning angle E is θ2. Finally, the flow path C of this structure C5 V Obtain the value, C V The conditions ≈ 81.32 > 73.5 and ξ ≈ 2.45 ≤ 3.0 are satisfied, and the conventional structure C4, improvement 1, and improvement 2 C V All values ​​are significantly higher than the actual values ​​(11% to 54%), and can fully satisfy high flow rate requirements.

[0335] <Case Study F: Flow path analysis of structure C5 according to the present invention (Third embodiment)> Refer to Figure 8A, which shows the cross-sectional structure and streamline distribution diagram of structure C5 according to the third embodiment. Refer to Figure 8B, which is a top view of the fan-shaped unfolded streamline of the valve chamber 5 of structure C5 according to the third embodiment. Radial center line S of structure C5 according to the third embodiment 12 Refer to Figure 8C, which shows the turning angle D at the inner exit 82 viewed from a 45-degree angle (see Figures 1A-1C and 2C together).

[0336] d0 = 52.5 mm, its C V The value is C V The conditions ≈ 84.6 > 73.5 and ξ ≈ 2.26 ≤ 3.0 are satisfied.

[0337] The structure of the flow path according to the third embodiment is configured with reference to the first embodiment, and the outlet flow path 8 has the same non-standard elliptical inner outlet 82, with its upper edge line S2a Replace with a straight line segment E3E5, and lower edge line S 2b Replace with a straight line segment E4E6, and change the shape of the inner outlet 82 to the rectangle in which a non-standard elongated ellipse is inscribed. Both have the same major axis a y The same short axis b z If it has the same distal point E3 and the same proximal point E4, and the four right angles of the rectangle are modified to four small rounded angles, and the area of ​​the rectangle is larger than the area of ​​the non-standard ellipse, then the jet S 121 and slow flow S 122 This provides an even greater advantage for the inflow, and in particular, the lower half of the space of the inner outlet 82 can be connected more smoothly to the annular groove 53.

[0338] The inlet channel 6 is a curved arc-shaped pipe, with a deflection angle A facing upwards, and the fluid flows out from the central hole 63 of the valve seat 51. LH3=LH1=59.34mm, γ1≈23.2°, d0 / a x The condition ≈ 0.911 is met.

[0339] The annular groove 53 is installed between the outer diameter d1 of the valve seat 51 and the inner diameter d3 of the valve chamber 5, and the bottom of its inclined surface 531 and its proximal point E4 are at the same height.

[0340] The radial channel 7 is an annular channel that radiates horizontally with a valve opening B1.

[0341] Outlet passage 8 includes a slanted pipe with a rectangular cross-section, and the height LH4 of the distal point E3 of the inner outlet 82 is higher than the sealing surface 510 of the valve seat 51, LH3 <LH4、LH6=72.48mm、LL2=LL 21 =68.25mm, LH4=94.5mm, H1=35.16mm, LH2=29.14mm, LH5=-5.12mm, a y =99.61, a y * =77.59, θ 21 =45°, θ 21 * =34.11°, θ²=25.273°, θ 22 The condition of =17.21° is met.

[0342] The turning angle A, the inlet centerline S1, and the turning angle B are similar to the streamline S and turning angles A and B shown in Figure 6A.

[0343] Diffusion C, radial centerline S 12 The sector expansion is similar to the sector expansion of streamline S shown in Figure 6B.

[0344] The angle of change D is similar to the angle of change D of the streamline S shown in Figure 6A, and if we let the angle of change D be θ2, the condition 25.27° < angle of change D < 34.11° is satisfied, and the jet S 121 The angle of change D1 and the slow flow S 122 Includes the angle of deflection D2 of the jet S. 121 and slow flow S 122 This has only minor flow interference within the valve chamber 5, and the jet S 121 and slow flow S 122 This results in only minor flow interference at the inner outlet 82.

[0345] Referring to Figure 8A, the outlet channel 8 is a straight pipe segment installed at an angle downwards, with a turning angle E of θ2 and an elbow angle. However, even with the relatively smooth bend of the elbow angle, high head loss is not generated, there is no formation of a circulating flow section N, and there is no problem of particle aggregation.

[0346] When examining the flow path of structure C5 according to the third embodiment, the results are similar to those of the second embodiment, but when the shape of the inner outlet 82 is rectangular, it provides more streamline space compared to the original ellipse, allowing the outlet flow path 8 to smoothly and gradually narrow in diameter from the inner outlet 82 to the valve outlet, resulting in a higher C V The value is obtained, and the jet S 121 and slow flow S 122 The flow swirls within the outlet channel 8 between them, eliminating the circulating flow in the elbow angle region where the turning angle E is θ2. Finally, the flow path C of structure C5 V Obtain the value, C V The conditions ≈84.6 > 73.5 and ξ ≈ 2.26 ≤ 3.0 are satisfied, and the conventional structure C4, improvement 1, and improvement 2 C V All values ​​are significantly higher than the actual values ​​(11% to 54%), and can fully satisfy high flow rate requirements.

[0347] <Case Study G: Flow path analysis of structure C5 according to the present invention (Fourth embodiment)> Refer to Figure 9A, which shows the cross-sectional structure and streamline distribution diagram of structure C5 according to the fourth embodiment. Refer to Figure 9B, which is a top view of the fan-shaped unfolded streamline of the valve chamber 5 of structure C5 according to the fourth embodiment. Radial center line S of structure C5 according to the fourth embodiment 12 Refer to Figure 9C, which shows the turning angle D at the inner exit 82 viewed from a 45-degree angle (see Figures 1A-1C and 2D together).

[0348] C V The value is C V The conditions ≈ 80.89 > 73.5 and ξ ≈ 2.48 ≤ 3.0 are satisfied.

[0349] The structure of the flow path according to the fourth embodiment is constructed with reference to the first embodiment.

[0350] The inlet channel 6 is a curved arc-shaped pipe, with a deflection angle A facing upwards, and the fluid flows out from the central hole 63 of the valve seat 51. LH3=LH1=59.34mm, γ1≈23.2°, d0 / a x The condition ≈ 0.911 is met.

[0351] The annular groove 53 is installed between the outer diameter d1 of the valve seat 51 and the inner diameter d3 of the valve chamber 5, and the bottom of its inclined surface 531 and its proximal point E4 are at the same height.

[0352] The radial channel 7 is an annular channel that radiates horizontally with a valve opening B1.

[0353] The outlet passage 8 is a curved pipe, and the height LH4 of the distal point E3 of the inner outlet 82 is higher than the sealing surface 510 of the valve seat 51, LH4 > LH3, LH6 = 72.48 mm, LL2 = LL 21 =52.5mm, LH4=78.75mm, H1=19.41mm, LH2=20.05mm, LH5=-12.18mm, a y =90.93, a y * =84.66, θ 21 =45°, θ 21* =0.0°, θ²=22.46°, θ 22 The condition of =15° is met.

[0354] Upper edge line S of the outlet channel 8 2a A portion of the circular arc S3 is tangent to it, and a vertical line YL3 and a new distal point E3 are added. ** They intersect at this point. Here, the arc S3 is an inwardly concave curve, and its major axis a y A new distal point E3 above ** Create and distal point E3 ** From there, an arc S3 is applied to create the upper edge line S 2a Adjacent to, distal point E3 ** The height difference between the valve seat 51 is H1 ** H1 ** The conditions ≥B1 and HL6 = 72.48mm are satisfied. And line segment E3 ** The new long axis formed at E4 is a y ** In addition, the inner diameter surface and tangent curved surface SS of the outlet channel 8 created along the arc S3 are created, and the angle γ between the arc S3 and the vertical line YL3 is calculated. 21 ** It has a relatively large angle, 30°≦γ 21 ** The condition ≤90° is met, and the distal point E3 ** The angle of the turning angle D is θ 21 ** Let 0°≦θ 21 ** The condition ≤60° is satisfied, and the new major axis of the ellipse is a y ** a y ** The condition ≈1.61d0 is satisfied.

[0355] The upper edge line S of the aforementioned outlet channel 2a The purpose of the modification is to obtain the appropriate height of the valve chamber 5, eliminate the high deflection angle D of the original distal point E3 diffusion C, and still maintain the high flow rate performance of the flow path.

[0356] The turning angle A, the inlet centerline S1, and the turning angle B are similar to the streamline S and turning angles A and B shown in Figure 6A.

[0357] Diffusion C, radial centerline S 12 The sector expansion is similar to the sector expansion of streamline S shown in Figure 6B.

[0358] The angle of deflection D is equal to the jet S. 121 and slow flow S 122 and including distal point E3 ** The angle of the turning angle D is θ 21 ** Let θ 21 ** The jet S satisfies the conditions = 0° and 25.27° < deflection angle D < 34.11°. 121 and slow flow S 122 The material is bent downwards to greatly reduce the angle of the turning angle D into the annular groove 53, and the first turning angle D is applied.

[0359] The angle of deflection D is similar to the angle of deflection D of the streamline shown in Figure 6A, and the jet S 121 The angle of change D1 and the slow flow S 122 Includes the angle of deflection D2 of the jet S. 121 and slow flow S 122 This has only minor flow interference within the valve chamber 5, and the jet S 121 and slow flow S 122 This results in only minor flow interference at the inner outlet 82.

[0360] Referring to Figure 9A, the outlet channel 8 is installed as a curved pipe with a turning angle E of 2θ. 22 However, a smooth curved pipe does not cause high head loss, and the jet S 121 and slow flow S 122 Although there is slight flow interference between them, there is no excessive increase in head loss relative to the outlet channel 8. In addition, there is no generation of circulating flow section N, and there are no problems with particle aggregation, and the jet S 121 and slow flow S 122 These interfere with each other within the valve chamber 5, and the jet S 121 and slow flow S 122 The streamline S does not cause any obvious interference inside the valve chamber 5.

[0361] When examining the flow path of structure C5 according to the fourth embodiment, some jet S121 When the streamlines flow directly into the inner outlet 82, benefits can be obtained from the circular arc S3 and the tangent surface SS, and the angle of its deflection angle D is θ 21 ** Let θ 21 ** The conditions of =0°, 25.27° < turning angle D < 34.11° are met, and finally the jet S 121 and slow flow S 122 The inner outlet 82 between and has a relatively small gripping angle α3, and the jet S 121 and slow flow S 122 This allows for the swirling flow within the outlet channel 8 between them, eliminating the circulating flow with a turning angle E of 2θ2. Finally, the flow path C of structure C5 V Obtain the value, C V The conditions ≈ 80.89 > 73.5 and ξ ≈ 2.48 ≤ 3.0 are satisfied, and the conventional structure C4, improvement 1, and improvement 2 C V Compared to the values, all are significantly higher (11% to 54%), and can fully satisfy the high flow rate requirements. In this embodiment, when the arc S3 is any other curved shape, C remains V A significant improvement in the value can be achieved.

[0362] <Case Study H: Flow path analysis of structure C5 according to the present invention (5th embodiment)> Refer to Figure 10A, which shows the cross-sectional structure and streamline distribution diagram of structure C5 according to the fifth embodiment. Refer to Figure 10B, which is a top view of the fan-shaped unfolded streamline of the valve chamber 5 of structure C5 according to the fifth embodiment. Radial center line S of structure C5 according to the fifth embodiment 12 Refer to Figure 10C, which shows the turning angle D at the inner exit 82 viewed from a 45-degree angle (see Figures 1A-1C and 2E together).

[0363] The structure of the flow path according to the fifth embodiment is constructed with reference to the first embodiment.

[0364] d0 = 52.5 mm, its C V The value is C V The conditions ≈ 83.23 > 73.5 and ξ ≈ 2.34 ≤ 3.0 are satisfied.

[0365] The inlet channel 6 is a curved arc-shaped pipe, with a deflection angle A facing upwards, and the fluid flows out from the central hole 63 of the valve seat 51. LH3=LH1=59.34mm, γ1≈23.2°, d0 / a x The condition ≈ 0.911 is met.

[0366] The annular groove 53 is installed between the outer diameter d1 of the valve seat 51 and the inner diameter d3 of the valve chamber 5, and the bottom of its inclined surface 531 and its proximal point E4 are at the same height.

[0367] The radial channel 7 is an annular channel that radiates horizontally with a valve opening B1.

[0368] The structure of the valve chamber 5 is a hollow, circular, eccentric structure, and the structure of the valve chamber 5 is divided into a valve plug chamber 55 with a diameter of 1.8d0 and an annular chamber 56 with a diameter of 2.2d0. The deviation of the concentricity between the valve plug chamber 55 and the annular chamber 56 is set to 0.2d0, and the height of the top of the interior of the annular chamber 56 is set to LH7. The valve plug chamber 55 and the valve seat 51 are concentrically arranged so that a vertical line YL1 passes through them, and the valve plug chamber 55 is used to receive the valve plug 54. Of these, the horizontal distance between the center point P1 of the valve seat 51 on the valve inlet side and the inner diameter of the annular chamber 56 is set to 0.9d0, and the horizontal distance between the center point P1 of the valve seat 51 on the inner outlet side 82 and the inner diameter of the annular chamber 56 is set to 1.3d0. The annular chamber 56 receives an annular space B2 and an annular groove 53, and the width B2 of the annular groove 53 changes so that it has its maximum width on the inner outlet side 82 according to the eccentric design.

[0369] The outlet channel 8 is a curved pipe, and the height LH4 of the distal point E3 of the inner outlet 82 is higher than the sealing surface 510 of the valve seat 51, with LH4 > LH3, LH6 = 72.48 mm, LH7 = 81.61 mm, and LL2 = LL 21 =52.5mm, LH4=78.75mm, H1=19.41mm, LH2=20.05mm, LH5=-12.18mm, a y =90.93, a y * =84.66, θ 21 =45°, θ 21 * =41.37°, θ²=22.46°, θ 22 The condition of =15° is met.

[0370] When the distal point E3 of the internal outlet 82 is higher than the apex of the annular chamber 56, the condition LH4 > LH7 is satisfied, and distal point E3 ** It is higher than the apex of the annular chamber 56, and distal point E3 ** From there, a portion of the arc S3 is applied to form the upper edge line S 2a It is adjacent to the distal point E3. ** The height difference H1 between the valve seat 51 and the sealing surface 510 ** H1 ** The condition of =13.14mm is ensured, and line segment E3 ** The new long axis formed at E4 is a y ** At the same time, the inner diameter surface and tangent curved surface SS of the outlet channel 8, which is created along the arc S3, are created, and the distal point E3 ** The angle γ between the arc S3 and the perpendicular line YL3 at that point. 21 ** It has a relatively large angle, γ 21 ** The condition of =90° is met, and the distal point E3 ** The angle of the turning angle D is θ 21 ** Let θ 21 ** The condition = 0° is satisfied, and the new major axis of the ellipse is a y ** a y ** The condition = 1.54d0 is satisfied (see also the fourth embodiment).

[0371] The turning angle A, the inlet centerline S1, and the turning angle B are similar to the streamline S and turning angles A and B shown in Figure 6A.

[0372] Diffusion C, radial centerline S 12 The sector-shaped expansion is similar to the sector-shaped expansion of the streamline S shown in Figure 6B, and since the horizontal distance from the center point P1 of the valve seat 51 to the center point P3 of the inner outlet 82 is 1.3d0, the width B2 of the annular groove 53 has its maximum width on the side of the inner outlet 82, and the jet S 121 This allows for more streamlines S to flow directly into the inner outlet 82, so the angle after sector unfolding is reduced and does not exceed 180°, resulting in a slow flow S122 The sector expansion of the sector is then expanded to the remaining circumference angle.

[0373] The angle of deflection D is similar to the angle of deflection D of the streamline shown in Figure 6C, and the jet S 121 The angle of change D1 and the slow flow S 122 Including the angle of deflection D2, and assuming the horizontal distance of line segment P1P3 is 1.3d0, the jet S 121 and slow flow S 122 In both cases, a longer diffusion distance C can be achieved. In that streamline S, the radius of curvature R C This makes it possible to obtain jet S 121 and slow flow S 122 This has only minor flow interference within the valve chamber 5, and the jet S 121 and slow flow S 122 This results in only minor flow interference at the inner outlet 82.

[0374] At the turning angle E, the outlet channel 8 is installed as a curved pipe angled diagonally downward, with a turning angle E of 2θ2, but it is relatively smooth and does not cause high head loss, resulting in a jet S 121 and slow flow S 122 Although there is minor interference between the two, there is no excessive increase in head loss for the outlet channel 8, and in addition, there is no generation of a circulating flow section N, and no problem of particle aggregation.

[0375] When examining the flow path of structure C5 according to the fifth embodiment with reference to Figure 10A, the deflection angle A is an arc angle, which significantly reduces local head loss and allows for a reduction in the flow path area. However, the angle of deflection angle B, which is not affected by the circulating flow section N, is reduced to some extent in all cases. This is another factor contributing to the reduction in local head loss, and since the horizontal distance of line segment P1P3 is 1.3d0, the jet S 121 and slow flow S 122 Both can achieve a longer diffusion distance C, and in their streamlines S, the radius of curvature R C This makes it possible to obtain the following. The outlet channel 8 has a smooth arc curved pipe structure, the distal point E3 is higher than the sealing surface 510 of the valve seat 51, and the long axis a yWhen the diameter of the central hole 63 is made larger than the diameter d0, the streamlines S of the radial flow path 7 can be expanded 360°, the jet S 121 The streamlines only require a small downward first turning angle D1 to allow entry into the upper half space of the annular groove 53, which is also referred to as a minor head loss. And the jet S 121 When it enters the inner outlet 82, it is necessary to perform a second turning angle D1, like a small bend, which is also called a minor head loss. Finally, the jet S 121 and slow flow S 122 The inner outlet 82 between has a relatively small gripping angle α3, and finally the flow path C of structure C5 V Obtain the value, C V The conditions ≈ 83.23 > 73.5 and ξ ≈ 2.34 ≤ 3.0 are satisfied, and the conventional structure C4, improvement 1, and improvement 2 C V All values ​​are significantly higher than the actual values ​​(11% to 54%), and can fully satisfy high flow rate requirements.

[0376] <Case Study I: Flow path analysis of structure C5 according to the present invention (6th embodiment)> Refer to Figure 11A, which shows the cross-sectional structure and streamline distribution diagram of structure C5 according to the sixth embodiment. Refer to Figure 11B, which is a top view of the fan-shaped unfolded streamline of the valve chamber 5 of structure C5 according to the sixth embodiment. Radial center line S of structure C5 according to the sixth embodiment 12 Refer to Figure 11C, which shows the turning angle D at the inner exit 82 viewed from a 45-degree angle (see Figures 1A-1C and 2F together).

[0377] The flow path structure shown in the sixth embodiment is constructed with reference to the first embodiment.

[0378] C V The value is C V The conditions ≈ 97.98 > 73.5 and ξ ≈ 1.69 ≤ 3.0 are satisfied.

[0379] The inlet channel 6 is a curved arc-shaped pipe, with a deflection angle A facing upward, and flows out from the central hole 63 of the valve seat 51. The sealing surface 510 of the valve seat 51 is located above the central hole 63, and a conical tube 52 coaxial with the vertical line YL1 is installed and used to connect to the central hole 63. The height h of the conical tube 52 has a conical angle φ, and its center point is P DP Let LH3 be the height of the sealing surface 510 of the valve seat 51, where LH3 = LH1 + h1, LH1 = 86.88 mm, h = 5 mm, φ = 60°, LH3 = 91.88 mm, γ1 ≈ 2.02°, d0 / a x The condition ≈ 0.999 is met.

[0380] The annular groove 53 is installed between the outer diameter d1 of the valve seat 51 and the inner diameter d3 of the valve chamber 5, and the bottom of its inclined surface 531 and its proximal point E4 are at the same height.

[0381] The radial channel 7 is an annular channel that radiates horizontally with a valve opening B1.

[0382] The outlet passage 8 is a curved pipe, and the height LH4 of the distal point E3 of the inner outlet 82 is higher than the sealing surface 510 of the valve seat 51, LH4 > LH3, LH6 = 105.02 mm, LL2 = LL 21 =78.75mm, LH4=105mm, H1=13.12mm, LH2=35.55mm, LH5=0.0mm, a y =105, a y * =105.02, θ 21 =45°, θ 21 * =45°, θ²=26.83°, θ 22 The condition of =18.43° is met.

[0383] The turning angle A, the inlet centerline S1, and the turning angle B are similar to the streamline S and turning angles A and B shown in Figure 6A, and the function of the conical tube 52 is to provide a diffusion effect for the fluid and its inlet centerline S1. Furthermore, the turning angle B can be made smoother, allowing the fluid to enter the radial flow path 7, and this function can further reduce head loss. Next, the conical tube 52 increases the structural strength of the valve seat 51 and improves the reliability of the seal.

[0384] Diffusion C, radial centerline S 12 The sector-shaped expansion is similar to the sector-shaped expansion of the streamline S shown in Figure 6B, and the conical tube 52 provides a diffusing effect on the inlet centerline S1, thereby diffusing the jet S 121 This allows for more streamlines S to flow directly into the inner outlet 82, and the angle after sector formation does not exceed 180°, resulting in a slow flow S 122 The sector expansion of the sector is then expanded to the remaining circumference angle.

[0385] The angle of deflection D is equal to the jet S. 121 The angle of change D1 and the slow flow S 122 Including the deflection angle D2, and because the distal point E3 is higher than the sealing surface 510 of the valve seat 51, the diffusing action of the conical tube 52 is applied to the jet S 121 and slow flow S 122 The material is bent downwards to greatly reduce the angle of the turning angle D into the annular groove 53, and the first turning angle D is applied.

[0386] The angle of deflection D is similar to the angle of deflection D of the streamline shown in Figure 6A, and the jet S 121 The angle of change D1 and the slow flow S 122 Including the angle of deflection D2, the jet S is affected by the diffusion action of the conical tube 52. 121 and slow flow S 122 This has only minor flow interference within the valve chamber 5, and the jet S 121 and slow flow S 122 This results in only minor flow interference at the inner outlet 82.

[0387] At the turning angle E, the outlet channel 8 is installed as a curved pipe angled diagonally downward, with a turning angle E of 2θ2, but it is relatively smooth and does not cause high head loss, resulting in a jet S 121 and slow flow S 122 Although there is minor interference between the two, there is no excessive increase in head loss for the outlet channel 8, and in addition, there is no generation of a circulating flow section N, and there is no problem of particle aggregation.

[0388] When examining the flow path of structure C5 according to the sixth embodiment with reference to Figure 11A, the angle of deflection B of the diffusion action of the conical tube 52 is reduced to a certain extent in all cases, and in conjunction with this, the jet S 121 This allows more fluid to flow directly into the inner outlet 82. Furthermore, the turning angle of the first deflection angle D1 decreases to an angle that allows it to enter the upper half space of the annular groove 53, and the jet S 121 As it enters the inner outlet 82, it is still necessary to make a second turning angle D1, like a small bend once more. Finally, the jet S 121 and slow flow S 122 The inner outlet 82 between and has a relatively small gripping angle α3, and the jet S 121 and slow flow S 122 This allows for the swirling flow within the outlet channel 8 between them, eliminating the circulating flow with a turning angle E of 2θ2. Finally, the flow path C of structure C5 V Obtain the value, C V The conditions ≈97.98 > 73.5 and ξ ≈ 1.69 ≤ 3.0 are satisfied, and the conventional structure C4, improvement 1, and improvement 2 C V All values ​​are significantly higher than the actual values ​​(11% to 54%), and can fully satisfy high flow rate requirements.

[0389] [Table 1]

[0390] [Table 2]

[0391] Examination of flow field analysis results: The following examination is conducted based on the data in Tables 1 and 2.

[0392] 1. Comparing Figure 3A showing Case A, Figure 4A showing Case B, and Figure 5A showing Case C, the inlet channel 6 and outlet channel 8 of the conventional structure both have a geometric structure with a 90° right angle, and the simulation analysis C VFrom the values, it can be found that the right-angle structure of the inlet channel 6 has the greatest effect on the flow field. In Improvement 1, the inlet channel 6 is changed to a circular arc and C V Since the value can be obtained and improved, C V The value improved from 61.89 to 69.88, and in Improvement 2, simply changing the outlet flow path 8 to an arc resulted in a value of only 64.09. V To obtain the values ​​and focus on improvement, the circulating flow section N generated in the inlet flow path 6, which is clearly perpendicular, will be given the highest priority, while flow interference at the inner outlet 82 and flow interference within the valve chamber 5 will be given the second and third priority, respectively.

[0393] 2. Comparing Figures 3B, 4B, and 5B with the conventional structure, Improvement 1, and the top view of the valve chamber 5 of Improvement 2, it can be seen that the valve seat 51 is higher than the inner outlet 82, and as the fluid flows out from the central hole 63, it is affected by the obstruction of the inner diameter of the valve chamber 5, causing it to expand in a fan shape, within which the jet S 121 The unfolding angles of all of them are angles exceeding 180°.

[0394] 3. Comparing Figure 4A showing Case B, Figure 5A showing Case C, and Figure 6A showing Case D, the C of the three V The values ​​are 69.88, 64.09, and 82.89 respectively, and only when both the inlet channel 6 and outlet channel 8 in the first embodiment are curved pipes, their C V It is indicated that the condition of a value higher than 73.5 can be satisfied, and both the flow interference in the valve chamber 5 and the flow interference at the inner outlet 82 in the first embodiment are significantly reduced, however the area of ​​the inlet flow path 6 in the first embodiment is reduced, and d0 / a x The fact that it is approximately 0.911 is also related to its C V There may be cases where it becomes impossible to improve the value any further.

[0395] 4. Comparing Figure 6A showing Example D with Figure 7A showing Example E, in the second embodiment, the outlet channel 8 of the first embodiment is changed to an inclined pipe structure, but the inner outlet 82 is still maintained as a non-standard ellipse of the same dimensions, and its C V The value is 81.32, and the elbow angle structure has a deflection angle E. The inclined tube structure is a jet S121 This presents the advantage of being able to significantly reduce the first turning angle D, but the circulating flow in the elbow angle region will result in additional losses, and although there is no problem of particle aggregation in the circulating flow in the elbow angle region, the overall C V The value will drop by 1.57.

[0396] 5. Comparing Figure 6A showing Example D, Figure 7A showing Example E, and Figure 8A showing Example F, in the third embodiment, the outlet flow path 8 of the second embodiment is changed to an inclined pipe structure, but the inner outlet 82 has the same long axis a y The same short axis b z It is a rectangle having dimensions such as C V The value is 84.6, and as the area of ​​the inner outlet 82 of the rectangle increases, more jet S 121 It is possible to further smoothly allow the fluid to flow into the inner outlet 82, and the overall C V The value improves by 3.28 compared to the second embodiment.

[0397] 6. Comparing Figure 6A, which shows Example D, with Figure 9A, which shows Example G, in the fourth embodiment, the length LL of the outlet channel 8 is... 21 In the first embodiment, LL is shortened. 21 =68.25mm, whereas in the fourth embodiment, LL 21 = 52.25 mm, and the inner outlet 82 is modified, the long axis a y distal point E3 ** Along with selecting the following, we create the concave arc line S3 and the concave surface SS, and θ 21 ** =0°, which can lead to a reduction in the head loss at the turning angle D. Overall C of the 4th embodiment V The value was 80.89, which is 2.0 lower than in the first example, LL 21 As the length decreases, so a y * Although the length can be maintained at 84.66 mm, the LH5 is too low at -12.18 mm, which is still unfavorable for fluid flow, and ultimately θ 21 ** This offsets the advantage gained by having =0°, but C remains high.V Maintain the characteristics of the value.

[0398] 7. Comparing Figure 9A showing Example G with Figure 10A showing Example H, in the fifth embodiment, the valve chamber 5 in the fourth embodiment is manufactured to have an eccentric structure, and without modifying the inner outlet 82, the horizontal distance between the center point P1 of the valve seat 51 on the inner outlet 82 side and the inner diameter of the annular chamber 56 is set to 1.3d0, so the width B2 of the annular groove 53 changes to have its maximum width on the inner outlet 82 side according to the eccentric design. Among these, the eccentric structure is the jet S 121 By providing more diffusion space, the deflection angle D of diffusion C can be made to have a smoother angle, and the overall C of the 5th embodiment V The value is 83.23, which is 2.34 higher than that of the fourth example.

[0399] 8. Comparing Figure 6A, which shows Example D, with Figure 11A, which shows Example I, in the sixth embodiment, the length LL of the outlet channel 8 in the first embodiment is different. 21 In addition to extending the length, the height of the valve seat 51 is increased, and in the sixth embodiment, LL 21 =78.75mm, LH3=91.88mm, LH1=86.88mm, d0 / a x = 0.999. Furthermore, a conical tube 52 is installed above the central hole 63, and the height h of the conical tube 52 has a conical angle φ, which can provide a more favorable diffusion effect when the fluid is subjected to a turning angle B, and the jet S 121 This results in a more smooth angle, giving the deflection angle D of diffusion C to the overall C of the sixth embodiment. V The value is 97.98, which is 15.09 higher than that of the first embodiment.

[0400] 9. Referring to Table 2, Cases D1 and D2 produce a pipe diameter d0 of 52.5 mm according to the structure of Case D, but there are cases in which the valve chamber diameter d3 is further tightened, with the valve chamber diameter d3 of 94.5 mm having an inner diameter ratio d3 / d0 of 1.8 and the valve chamber diameter d3 of 84 mm having an inner diameter ratio d3 / d0 of 1.6, and C VThe values ​​were 81.37 and 68.26 respectively, and the head loss coefficient ξ was 2.43 and 3.48 respectively. The insufficient valve chamber diameter d3 significantly reduced the width of the annular groove 53 and forced the jet S 121 When the fluid flows into the annular groove 53, the angle of deflection D increases, raising the head loss and simultaneously increasing the flow interference in the valve chamber 5 and the flow interference at the inner outlet 82. It is expected that only the effect corresponding to Case B can be achieved, and the inner diameter ratio d3 / d0 in Case D2 is 1.6, which is clearly too small.

[0401] 10. Referring to Table 2, in case D3, the pipe diameter d0 (valve inlet diameter / valve outlet diameter / center hole diameter) is 22.2 mm, the valve chamber diameter d3 is 41.74 mm, the inner diameter ratio d3 / d0 is 1.88, and the head loss coefficient ξ is 2.29. The flow field analysis results for this case show that a relatively small pipe diameter d0 of 22.2 mm is used, but the inner diameter ratio d3 / d0 is not too low even when set to 1.88, and the C is still very good. V A value of 15.06 and a head loss coefficient ξ of 2.29 can be obtained.

[0402] 11. The reliability of the flow field analysis data is shown in Table 3 below.

[0403] [Table 3]

[0404] The data in Non-Patent Document 7 shows the measured flow coefficients for products with structure C4 (KH200-19P, KH200-25P, KH200-40P). Although the analysis values ​​are slightly higher than the measured values ​​because the flow field analysis software model cannot truly reflect the flow of the valve body, the reference value of the analysis results remains unquestionable.

[0405] 12. In contrast to Non-Patent Document 7, in Case D4, the pipe diameter d0 is 33.7 mm, the valve chamber diameter d3 is 67.4 mm, the inner diameter ratio d3 / d0 is 2.0, and the flow coefficient C obtained by the flow field analysis is VThe value is 37.5, the head loss coefficient ξ is 1.95, and in case D4, a prototype flow path (3D printed) was fabricated using rapid molding, and the resulting pipe diameter d0 is 33.1 mm, and the measured flow coefficient C V The value is 31.8, and the head loss coefficient ξ is 2.53. The measured value for case D4 is clearly and significantly improved compared to the measured value for the C4 structure of the same diameter, with a ratio of 2.53:6.30 for the head loss coefficient ξ, i.e., (6.3-2.53) / 6.3=0.598, representing a relative improvement of 59.8%. The comparison of the above data has sufficiently explained the inventiveness of this novel flow path C5 structure.

[0406] 13. Regarding Non-Patent Document 7, Case D5 is a preferred embodiment B of the first embodiment, and a detailed explanation of the flow path and flow field can be seen in Figures 12A, 12B, and 12C. In Case D5, the pipe diameter d0 is 33.7 mm, the valve chamber diameter d3 is 63 mm, the inner diameter ratio d3 / d0 is 1.87, and the jet S 121 As the flow moves downward and passes through distal point E3, the angle at which the second deflection angle D1 is applied decreases to 60°, and the flow coefficient C obtained from the flow field analysis is V The value is 33.79, the head loss coefficient ξ is 2.41, and the angle of the second turning angle D1 indicates that it is possible to effectively reduce the flow interference at the inner outlet.

[0407] 14. In the derivative application of this innovation patent, both Case F and Case I are derived from Case D, and a more favorable flow coefficient C V A value may be obtained. Naturally, a more favorable flow coefficient C can be obtained by adding the inner outlet 82 of the rectangle in Example F to Example I. V While a value may be obtained, it may be limited by the casting method, and the contents of Examples D, E, F, G, H, and I in Table 1, and Examples D1, D2, D3, D4, and D5 in Table 2 can be dimensionally transformed in terms of the local characteristics of the flow path structure. In terms of structural characteristics, the flow coefficient C can be added together to be even more preferable. V The values ​​obtained, and the variations in these structures and dimensions, all fall within the scope of the present invention. [Explanation of Symbols]

[0408] 5: Valve chamber 51: Alveolar seat 510: Sealing surface 511: Sealing ring 512: Vertical rib plate 5121: Circular arc surface 5122: Circular arc surface 5123: End of small arc angle 52: Conical tube 53: Ring groove 531: Slope 54: Valve Plug 542: Concave surface 55: Valve plug chamber 56: Ring chamber 6: Inlet channel 63: Center hole 60:Right angle 7: Radial flow path 8: Outlet channel 82: Inner exit S:Streamline S1: Entrance center line S 1a : Upper edge line of the inlet channel S 1b : Lower edge line of the inlet channel S 12 :Radial center line S 121 : jet S 122 :Slow flow S2: Exit center line S 2a : Upper edge line of the outlet channel S 2b : Lower edge line of the outlet channel S3: Arc SS:Tangential surface A: Angle of deflection A B: Angle of rotation B C: Diffusion C D: Angle of rotation D D1: Jet S 121 At the turning angle D, the turning angle D1 D2: Slow flow S 122 At the turning angle D, the turning angle D2 E: Angle of rotation E d3: Valve chamber diameter d2: Valve plug outer diameter d1: Valve seat outer diameter d0: Valve inlet diameter / Valve outlet diameter / Center hole diameter P0: Point on the vertical line YL6 P1: Center point of the central hole P2: Center point of the valve inlet P3: Center point of the internal exit P4: Center point of the valve outlet P5: Point on the vertical line YL5 P DP : Center point of the sealing surface P 11 : Intersection of vertical line YL1 and pipe axis line XL2 P 12 : Phase contact point between the inlet centerline S1 and the pipe axis XL2 P 31 : Intersection of vertical line YL3 and pipe axis line XL2 P 34 : Phase contact point between the exit center line S2 and the pipe axis line XL2 XL1: Horizontal line XL2: Tube axis YL1: Vertical line passing through center point P1 YL2: Vertical line passing through center point P4 YL3: Vertical line passing through center point P3 YL4: Vertical line passing through center point P2 YL5: Intersection P 12 A vertical line passing through YL6: Intersection P 34 A vertical line passing through E1: Distal point of the central hole E1 * The distal point that modifies the central hole from a non-standard elongated elliptical hole to a circular hole when γ1≠0°. E2: Proximal point of the central hole E2 * : Proximal point that modifies the central hole from a non-standard elongated elliptical hole to a circular hole when γ1≠0° E3: Distal point of the internal exit E3 * : Long axis a of valve opening B1 y Mirror point E3 ** : The distal point of the inner outlet where the concave arc S3 is fabricated. E35 : Upper edge line S 2a The point of contact between the vertical line YL5 and the point of contact between the vertical line YL5. E4: Proximal point of the internal exit E 46 : Lower border line S 2b The point of contact between the vertical line YL5 and the point of contact between the vertical line YL5. E5: Distal point of the valve outlet E6: Proximal point of the valve outlet E7: Distal point of the valve inlet E8: Proximal point of the valve inlet LH1: Height of center point P1 LH2: Height of center point P3 LH3: Height of the sealing surface LH4: Height of distal point E3 LH5: Height of periphery E4 LH6: Height of radial channel LH7: Height of the top of the interior of the annular chamber H1: Height difference of distal point E3 relative to the sealing surface H1 * : Mirror point E3 * Height difference relative to the sealing surface H1 ** : Height difference of distal point E3** relative to the sealing surface H3: Height difference from the sealing surface at the center point P3 of the outlet H5: Height difference between the top of the annular chamber and the sealing surface of the valve seat. L: Horizontal distance between center point P2 and center point P4 L1: Horizontal distance between center point P1 and center point P2 L 11 : Horizontal distance of the circular arc curve of the entrance centerline S1 L2: Horizontal distance between center point P1 and center point P4 LL2: Horizontal distance between center point P3 and center point P4 LL 21 : Horizontal distance of the circular arc curve of the exit centerline S2 B1: Valve opening degree B2: Circular Space B3: Radial gap γ1: Angle between the entrance center line S1 and the vertical line YL1 γ2: Angle between the exit center line S2 and the vertical line YL3 γ 21 : Upper edge line S 2aThe angle between and the vertical line YL3 γ 21 ** :Angle between the concave arc S3 and the vertical line YL3 γ 22 : Lower border line S 2b The angle between and the vertical line YL3 2θ1: Angle of the turning angle A θ1: Mounting angle of the entrance center line S1 2θ2: Angle of the turning angle E 2θ 21 : Upper edge line S 2a angle 2θ 22 : Lower border line S 2b angle θ2: Mounting angle of the exit center line S2 θ 21 : Upper edge line S 2a Mounting angle θ 21 * : Mirror point E3 * Mounting angle obtained θ 21 ** :Distal point E3 ** Mounting angle obtained θ 22 : Lower border line S 2b Mounting angle β: Angle of slope 531 a x : Long axis of the central hole (not shown in the diagram) a y :Inner / outlet long axis b z :Inner exit short axis b z : Short axis of the central hole (not shown in the diagram) a y * : Mirror point E3 * The long axis of the inner and outer outlets obtained by a y ** :Distal point E3 ** The long axis of the inner and outer outlets obtained by h: height of the cone tube φ: cone angle N: Circulation flow section

Claims

1. A valve body passage having a low head loss coefficient ξ that conforms to ESG requirements, wherein the structure of the valve body passage comprises a valve chamber, an annular groove, a valve seat, a valve plug, a sealing surface, a valve inlet, an inlet passage, a central hole, a valve outlet, an outlet passage, and an inner outlet, Let the inner diameter of the valve chamber be d ３ and the outer diameter of the valve stem be d ２ and the outer diameter of the valve seat be d １ and let the valve inlet diameter, valve outlet diameter, and center hole diameter all be d 0 The sealing surface of the valve seat is located outside the center hole, and the height of the center point P １ of the center hole is LH １ and the height of the center point P ３ of the inner outlet is LH ２ and the height of the sealing surface of the valve seat is LH ３ and a sealing convex ring is provided, and the valve inlet has a center point P ２ and the valve outlet has a center point P ４ and has horizontal line XL １ The center point P of the central hole is １ It passes through the horizontal line XL １ The circumference of the central hole and the distal point E located on the side of the valve inlet are the same. １ and the proximal point E located on the side of the valve outlet. ２ At the two intersection points, they intersect with each other, Tube axis XL ２ (X-axis) is center point P ２ and center point P ４ The pipe passes horizontally, and the height indicator is the pipe axis XL connecting the valve outlet and the valve inlet. ２ Using this as a reference, the zero point of the Y-axis coordinate is the pipe axis XL ２ When displaying the position relative to a value, there are positive values ​​(>0), zero values ​​(=0), and negative values ​​(<0). vertical line YL １ The center point P １ Passing through the aforementioned pipe axis XL ２ and intersection point P １１ They interacted with each other, vertical line YL ２ The center point P is ４ It passes through the vertical line YL ２ The circumference of the valve outlet is at the distal point E ５ and the proximal point E, which is the lowest point of the outlet flow path. ６ At the two intersection points, they intersect with each other, vertical line YL ３ The central point P of the inner outlet is ３ Passing through the aforementioned pipe axis XL ２ and intersection point P ３１ They intersect at the perpendicular line YL ３ The circumference of the aforementioned inner outlet is the distal point E ３ and proximal point E ４ At the two intersection points, they intersect with each other, and at the distal point E ３ The height of LH ４ And the proximal point E ４ The height of LH ５ year, vertical line YL ４ The center point P is ２ It is established by passing through and the vertical line YL ４ The circumference of the valve inlet is defined as distal point E ７ and the proximal point E, which is the lowest point of the inlet channel. ８ At the two intersection points, they intersect with each other, center point P １ and center point P ２ and horizontal distance L １ It has P １１ P ２ = L １ The following conditions are met, and the center point P ４ From the center point P １ Up to horizontal distance L ２ It has P ４ P １１ = L ２ The following conditions are met, and the center point P ２ From the center point P ４ The horizontal distance L is to P ４ P ２ =L=L １ +L ２ The following conditions are met, and the center point P ４ From the center point P ３ Up to horizontal distance LL ２ It has LL ２ = L ２ -d ３ The condition of / 2 is met, The valve seat has the annular groove, the valve plug, the valve stem, and the sealing surface installed inside it, and the valve plug, the valve stem, and the sealing surface are concentric, and the valve seat is used to connect the inlet passage and the outlet passage, the inlet passage enters from the horizontal valve inlet and is bent upward, and its outlet end is the central hole of the valve seat, the inner outlet installed on the inner diameter surface of the valve seat is used to connect to the outlet passage, the valve inlet and the valve outlet are installed on both sides of the valve body passage, and when the outlet passage is a straight pipe or a curved pipe of a diagonal downward type, the inner outlet may be a non-standard ellipse. The annular groove is located within the valve chamber diameter and surrounds the outer diameter of the valve seat, the bottom of the annular groove is a slope with an angle β, the higher side of the slope is located on the side of the inlet passage, the lower side of the slope is located on the side of the outlet passage, and the proximal point E of the inner outlet is located therein. ４ They are connected to each other, The valve seat is installed at the outlet end of the inlet passage and has the sealing surface provided. The valve plug is cylindrical and has a flat surface at its bottom. When the global valve is closed, the valve plug is used to seal the sealing surface. When the valve is fully open, the bottom surface of the valve plug and the sealing surface are connected by an opening of B. １ A radial channel is formed having 0.125 ≤ B １ / d ０ Satisfying the condition ≤ 0.5, The inlet flow path includes the valve inlet, the inlet center line S １ the center hole, the upper edge line S １ａ the lower edge line S １ｂ The inlet center line S １ is connected to the center point P １ the center point P ＤＰ the center point P ２ and still has an included angle γ １ between the center point P １ and the vertical line YL １ When the included angle γ1≠0°, the center hole is a non-standard elliptical hole, having a major axis a ｘ in the X-axis direction, and a ｘ ≧d ０ a ｘ =E １ E ２ E １ P １ ≧P １ E ２ satisfies the condition. When the included angle γ1 = 0°, the center hole is a circular hole with a diameter of d ０ having a minor axis b ｚ in the Z-axis direction, and b ｚ =d ０ satisfies the condition. The upper edge line S １ａ connects the far point E １ and the far point E ７ The lower edge line S １ｂ connects the near point E ２ and the near point E ８ ​ The radial flow path has a radial center line S １２ And the opening degree B １ The valve is opened, and the opening of the radial flow path, which consists of the bottom surface of the valve and the sealing surface, is set to B １ The radial channel surrounds the channel from which the central hole is radiated, and the height of the radial channel is LH ６ Toshi, LH ６ = B １ +LH ３ The following conditions are met, and the radial center line S １２ The center point P is １ and center point P ３ Connecting the two, the center point P １ From there, it flows out in different directions using a radial method, finally reaching the central point P. ３ It is connected up to, The aforementioned outlet passage comprises the internal outlet, the valve outlet, and the outlet center line S. ２ And, upper edge line S ２ａ And the lower edge line S ２ｂ and the exit center line S ２ The center point P is ３ and center point P ４ Connecting and, at the center point P ３ and the aforementioned vertical line YL ３ and the included angle γ ２ It has 0°≦γ ２ When the condition of <90° is met and the inner outlet is a non-standard elliptical hole, the major axis a in the Y-axis direction ｙ It has, a ｙ ≥ d ０ a ｙ = E ３ E ４ , E ３ P ３ ≥P ３ E ４ The following conditions are met, and the minor axis b in the Z-axis direction. ｚ It has, b ｚ = d ０ The conditions are met, and the included angle γ ２ = When the angle is 90°, the outlet passage is a horizontal straight pipe, a ｙ = d ０ The above conditions are met, and the upper edge line S ２ａ The distal point E ３ and the distal point E ５ Connecting the two, the lower edge line S ２ｂ The proximal point E ４ and the aforementioned proximal point E ６ Connecting the two, the distal point E ３ The height difference H is relative to the sealing surface. １ It has LH ４ -LH ３ = H １ The conditions are met, and distal point E ３ When H is higher than the sealing surface, １ ≥ 0, when it is lower than the sealing surface, H １ The condition ≤ 0 is satisfied, and the center point P of the inner outlet is satisfied. ３ The height difference H is relative to the sealing surface. ３ It has LH ２ -LH ３ = H ３ The following conditions are met, and the center point P ３ When H is higher than the sealing surface, ３ ≥ 0, when it is lower than the sealing surface, H ３ Satisfying the condition ≤ 0, Radial gap B ３ The outer diameter d of the valve plug is ２ and valve chamber diameter d ３ Located between B ３ = (d ３ -d ２ ) / 2, 0.2 ≤ B ３ / d ０ Satisfying the condition ≤ 0.4, Ring space B ２ The outer diameter d of the valve seat is １ and the valve chamber diameter d ３ Between, B ２ = (d ３ -d １ ) / 2, 0.25 ≤ B ２ / d ０ The condition ≤ 0.4 is satisfied, and the inner diameter ratio is d. ３ / d ０ The valve chamber diameter d ３ and the valve inlet diameter d ０ The ratio is 1.75 ≤ d ３ / d ０ Satisfying the condition ≤ 2.8, The aforementioned entrance centerline S １ , the radial center line S １２ , exit center line S ２ The three central lines are defined as streamlines, and their bending angles are limited to those based on predictable geometric shapes. Further descriptions are obtained using 3D-CFD calculations. The aforementioned entrance centerline S １ This is a line segment that includes a circular arc, a vertical line segment, a diagonal line segment, and a horizontal line segment, and is either a single line segment or a combination of several line segments, wherein the vertical line segment is the vertical line YL １ It is coaxial with the pipe axis XL ２ It is coaxial with the entrance center line S, and the turning angle A is the same as the entrance center line S. １ This is the bending angle from the valve inlet to the central hole, The radial center line S １２ The streamlines after the fluid has flowed out of the central hole are those that flow out radially in different directions and enter the radial flow path, and the angle of change B is the same as the inlet center line S １ The radial center line S １２ The bending angle is between these points, and all streamlines flow via the horizontal radial direction. Diffusion C flows towards the inner outlet, and along the radial center line S １２ The fluid velocity of diffusion C slows down after the turning angle B is applied due to the increase in the area of ​​the radial flow path, but when it flows towards the inner outlet after bending, it accelerates due to the reduction in area, and the radial center line S １２ This is influenced by the relative position between the sealing surface and the inner outlet, and is either a straight line, an arc, or a multi-curved arc. The radial center line S １２ The fluid is driven by the pressure difference between the valve inlet and the valve outlet, and the radial center line S of the diffusion C １２ is a jet S １２１ and slow flow S １２２ The flow is divided into two streams, and the dense streamline that receives a high pressure difference gradient becomes the jet S with a high flow velocity. １２１ Therefore, the low-density streamline receiving the low pressure difference gradient is the jet S １２１ Slower flow velocity S １２２ The streamlines of the diffusion C flow unfold in a fan shape circumferentially and are affected by the angle of deflection B, resulting in the jet S １２１ It spreads out in a fan shape toward the inner outlet, and slow flow S １２２ is a jet S １２１ The sector is unfolded to a circumferential angle other than the sector unfolding angle, and the radial center line S １２ is a jet S １２１ and slow flow S １２２ Before the two flows into the aforementioned inner outlet, they are each subjected to a deflection angle D, and the jet S １２１ This involves applying a turning angle D1 and creating a slow flow S １２２ Apply a turning angle D2, The aforementioned exit centerline S ２ This is a line segment that includes a circular arc, a diagonal line segment, and a horizontal line segment, and is either a single line segment or a combination of several line segments, wherein the horizontal line segment is the pipe axis XL ２ It is coaxial with the exit center line S ２ The turning angle D is the radial center line S. １２ and the aforementioned exit center line S ２ This is the bending angle between the two, and the fluid flows out from the valve outlet after being subjected to a deflection angle E within the inner outlet and the outlet passage. The inlet flow path starts from the circumference of the valve inlet and extends to the inlet center line S. １ Diameter d along the line ０ The cross-section of the inlet channel up to the circular central hole is defined by the upper edge line S １ａ and lower edge line S １ｂ Having, The aforementioned entrance centerline S １ It has a straight line segment and a circular arc curve, and the pipe axis XL ２ P is the point of contact. １２ The aforementioned circular arc curve has one endpoint and center point P １ The other end point is the point of tangency P. １２ And the phase contact point P １２ The aforementioned circular curve and the pipe axis XL ２ The point of contact with the other, and the circular curve is the horizontal distance L １１ It has L １１ = P １１ P １２ The conditions are met, and the straight line segment has one endpoint at point P. １２ Let the other endpoint be the center point P. ２ P １２ P ２ Horizontal distance = L １ -L １１ The conditions are met, and point P １２ Passing through the vertical line YL ６ The vertical line YL ６ Point P is the center of the circle above. ０ By taking this, line segment P ０ P １２ and line segment P ０ P １ To make it possible to equalize the line segment P ０ P １２ and line segment P ０ P １ The angle between and 2θ １ This is equal to the turning angle A, and the mounting angle θ １ is line segment P １ P １２ It is equal to the horizontal angle of the central hole P. １ The aforementioned circular arc curve and the vertical line YL １ The angle γ with １ Obtained γ １ = 90° - 2θ １ The conditions must be met, When the included angle γ1 ≠ 0°, the central hole is moved from the non-standard elliptical hole to a diameter d ０ Modify it to reduce the size of the circular hole, and the original major axis is a ｘ a ｘ = E １ E ２ The length of d ０ The reduction is performed by placing the distal point E on the long axis. １ Instead, distal point E １ ＊ Take the long axis and the proximal point E ２ Instead, proximal point E ２ ＊ Take E １ ＊ P １ = P １ E ２ ＊ = d ０ The condition of / 2 is satisfied, and the major axis a ｘ The length reduction ratio is d ０ / a ｘ to, d ０ / a ｘ = d ０ / E １ E ２ The conditions are met, and the major axis a ｘ The length reduction ratio is d ０ / a ｘ Let 0.7 ≤ d ０ / a ｘ The condition ≤ 1.0 is satisfied, Distal point E ３ is, height LH ４ It has distal point E ３ The height difference between the sealing surface and the above is H １ And the proximal point E ４ is, height LH ５ It has line segment E ３ E ４ The major axis a in the Y-axis direction of the inner outlet is ｙ and a ｙ = E ３ E ４ The conditions must be met, The aforementioned exit centerline S ２ It has a straight line segment and a circular arc curve, and the pipe axis XL ２ P is the point of contact. ３４ The aforementioned circular arc curve has one endpoint and center point P ３ The other end point is the point of tangency P. ３４ And the phase contact point P ３４ The aforementioned circular curve and the pipe axis XL ２ The point of contact with the other, and the arc curve has a horizontal distance LL ２１ It has LL ２１ = P ３１ P ３４ The conditions are met, and the straight line segment has one endpoint at point P. ３４ Let the other endpoint be the center point P. ４ P ３４ P ４ Horizontal distance = LL ２ -LL ２１ The conditions are met, and point P ３４ Passing through the vertical line YL ５ The vertical line YL ５ Point P is the center of the circle above. ５ By taking this, line segment P ５ P ３４ and line segment P ５ P ３ To make it possible to equalize the line segment P ５ P ３４ and line segment P ５ P ３ The angle between and 2θ ２ This is equal to the turning angle E, and the mounting angle θ ２ is line segment P ３ P ３４ It is equal to the horizontal angle of the center point P. ３ The aforementioned circular arc curve and the vertical line YL ３ The angle γ with ２ Obtained γ ２ = 90° - 2θ ２ The conditions are met, and the exit center line S ２ When the flow consists of a straight line segment and a circular arc, the outlet flow path is maintained with a cross-sectional area of ​​equal diameter, and its upper edge line S ２ａ , lower edge line S ２ｂ and the aforementioned exit center line S ２ All three arc curves are parallel to each other, and the three circular arcs share a common center point P. ５ It has and the inner outlet is a non-standard elongated ellipse, and the major axis a of the non-standard elongated ellipse ｙ = E ３ E ４ E ３ P ３ >P ３ E ４ The conditions are met, and the minor axis b of the non-standard elongated ellipse ｚ = d ０ That is, The aforementioned upper edge line S ２ａ and vertical line YL ５ This refers to the phase contact point E ３５ They intersect at point E ３５ The height of d ０ Let / 2, and line segment P ５ E ３５ and line segment P ５ E ３ The angle enclosed by is 2θ ２１ Furthermore, the distal point E ３ The aforementioned circular arc curve and the vertical line YL ３ The angle γ with ２１ Obtained γ ２１ = 90° - 2θ ２１ The above conditions are met, and the upper edge line S ２ａ via distal point E ３ Height value LH ４ To make it possible to acquire, The lower edge line S ２ｂ and vertical line YL ５ This refers to the phase contact point E ４６ They intersect at point E ４６ The height is -d ０ Let / 2, and line segment P ５ E ４６ and line segment P ５ E ４ The angle enclosed by is 2θ ２２ Furthermore, the proximal point E ４ The lower edge line S ２ｂ and vertical line YL ３ The angle γ with ２２ Obtained γ ２２ = 90° - 2θ ２２ The conditions are met, and the lower edge line S ２ｂ via proximal point E ４ Height value LH ５ To make it possible to acquire, Jet S １２１ and slow flow S １２２ This enables layered flow in the annular groove, reducing flow interference within the valve chamber and flow interference at the inner outlet, and the upper edge line S of the outlet flow path. ２ａ The angle of the turning angle E is 2θ ２１ Let 30° ≤ 2θ ２１ A valve body flow path for a global valve, characterized by satisfying the condition of ≤90°.

2. The center point of the aforementioned central hole is the pipe axis XL ２ Height LH １ It has an angle 2θ of its turning angle A. １ 55° ≤ 2θ １ The valve body flow path of the global valve according to claim 1, characterized in that it satisfies the condition ≤ 105°.

3. Jet S １２１ When diffusion C flows to the annular groove, the first turning angle D1 is applied, and distal point E ３ When passing through, a second turning angle D1 is applied, and the angle γ ２１ 0°≦γ ２１ The valve body flow path of the global valve according to claim 1, characterized in that it satisfies the condition of ≤60°.

4. Proximal point E ４ The height is LH ５ And the bottom of the slope of the annular groove is connected to each other, -0.4 ≤ LH ５ / d ０ The valve body flow path of the global valve according to claim 1, characterized in that it satisfies the condition ≤ 0.

4.

5. Lower edge line S of the outlet channel ２ｂ The angle of rotation E is 2θ ２２ 14° ≤ 2θ ２２ The valve body flow path of the global valve according to claim 1, characterized in that it satisfies the condition of ≤54°.

6. Height difference ratio H １ / d ０ However, H １ / d ０ When the condition ≤ 0.5 is met, LH ６ ≒LH ３ +B １ The following conditions are met, and the reflection point E ３ ＊ The height difference between the valve seat and the valve seat is H １ ＊ Toshi, H １ ＊ ≒B １ The conditions are met, and the jet S １２１ The mirror point E ３ ＊ and center point P ３ Between these two points, the water flows into the aforementioned internal outlet, and the reflection point E ３ ＊ Mounting angle θ ２１ ＊ is line segment E ３ ＊ E ３５ Equal to the horizontal angle of , 2θ ２１ ＊ ≤ 2θ ２１ The valve body flow path of the global valve according to claim 1, characterized in that it satisfies the following conditions.

7. The angle β of the slope of the annular groove is the included angle θ ２２ The valve body flow path of the global valve according to claim 1, characterized in that it approximates and satisfies the condition 8° ≤ β ≤ 20°.

8. The valve body flow path of the global valve according to claim 1, characterized in that the radial flow path includes the inner concave surface of the bottom of the valve plug and the sealing surface of the valve seat.

9. In the aforementioned outlet channel, the inner outlet is maintained in a non-standard elliptical shape, and the outlet center line S of the outlet channel ２ , the upper edge line S ２ａ , the lower edge line S ２ｂ Change it to a combination of straight line segments, and line segment P ３ P ３４ The center point P is ３ and the point of contact P ３４ Connect and line segment E ３ E ３５ The distal point E ３ and phase contact point E ３５ Connect and line segment E ４ E ４６ is the proximal point E ４ and phase contact point E ４６ Connecting the two, and starting from the circumference of the non-standard ellipse of the inner outlet, the center line S of the outlet ２ The cross-section of the inner diameter curved surface of the outlet passage, along the upper edge line S, reaches the circular valve outlet. ２ａ and lower edge line S ２ｂ It has and point P ３４ Passing through the vertical line YL ５ The vertical line YL ５ Point P is above. ５ By taking this, line segment P ５ P ３４ and line segment P ５ P ３ To make it possible to equalize the line segment P ５ P ３４ and line segment P ５ P ３ The angle between and 2θ ２ is line segment P ３ P ３４ Equals to the turning angle E, and the mounting angle θ ２ is line segment P ３ P ３４ The valve body flow path of the global valve according to claim 1, characterized in that it is equal to the horizontal angle of reference.

10. The shape of the inner outlet is modified from the non-standard ellipse to a rectangle, and the non-standard ellipse is inscribed in the rectangle, and both share the same major axis a. ｙ The same minor axis b ｚ It has the same distal point E ３ The same as the aforementioned proximal point E ４ The four right angles of the rectangle are modified into small rounded corners, and the outlet center line S of the outlet channel ２ , the upper edge line S ２ａ , the lower edge line S ２ｂ Change it to a combination of straight line segments, and line segment P ３ P ３４ The center point P is ３ and the point of contact P ３４ Connect and line segment E ３ E ３５ The distal point E ３ and phase contact point E ３５ Connect and line segment E ４ E ４６ is the proximal point E ４ and phase contact point E ４６ Connecting the two, and starting from the inner outlet, the center line S of the outlet ２ The cross-section of the inner diameter curved surface of the outlet passage, along the upper edge line S, reaches the circular valve outlet. ２ａ and lower edge line S ２ｂ It has and point P ３４ Passing through the vertical line YL ５ The vertical line YL ５ Point P is above. ５ By taking this, line segment P ５ P ３４ and line segment P ５ P ３ To make it possible to equalize the line segment P ５ P ３４ and line segment P ５ P ３ The angle between and 2θ ２ is line segment P ３ P ３４ Equals to the turning angle E, and the mounting angle θ ２ is line segment P ３ P ３４ The valve body flow path of the global valve according to claim 1, characterized in that it is equal to the horizontal angle of reference.

11. The aforementioned line segment P ３ P ３４ The mounting angle is θ ２ Let P be the center point. ３ The angle of rotation D is θ ２ Let θ ２ = Atan(LH ２ / LL ２１ The conditions of the line segment E are met. ３ E ３５ The mounting angle is θ ２１ And distal point E ３ The angle of rotation D is θ ２１ Let θ ２１ = Atan((LH ４ -d ０ / 2) / LL ２１ The conditions of the line segment E are met, ４ E ４６ The mounting angle is θ ２２ And proximal point E ４ The angle of rotation D is θ ２２ Let θ ２２ = Atan((LH ５ +d ０ / 2) / LL ２１ The conditions of the above are met, and the exit center line S ２ P is the phase contact point ３４ The first bending is performed at a turning angle E, where the turning angle E = θ ２ The upper edge line S ２ａ is phase contact E ３５ The first bending is performed at a turning angle E, where the turning angle E = θ ２１ The lower edge line S ２ｂ is phase contact E ４６ The first bending is performed at a turning angle E, where the turning angle E = θ ２２ And the distal point E ３ The angle of deflection D = θ ２１ Therefore, 14°≦θ ２１ The condition ≤45° is satisfied, and the phase contact E ３５ The angle of rotation E = θ ２１ Therefore, 14°≦θ ２１ The condition ≤45° is satisfied, and the proximal point E ４ The angle of deflection D = θ ２２ Therefore, 7°≦θ ２２ The condition ≤20° is satisfied, and the phase contact E ４６ The angle of rotation E = θ ２２ Therefore, 7°≦θ ２２ The valve body flow path of the global valve according to claim 9 or claim 10, characterized in that it satisfies the condition of ≤20°.

12. Distal point E of the ellipse ３ Height H １ When adjustment is needed, the upper edge line S of the outlet flow path. ２ａ A part of the circular arc S is tangent to it. ３ In addition to applying this, the vertical line YL ３ and a new distal point E ３ ＊＊ They intersect at the distal point E ３ ＊＊ Arc S ３ The included angle γ ２１ ＊＊ is 30°≦γ ２１ ＊＊ The condition ≤90° is satisfied, and the arc S ３ By creating the inner diameter upper edge curved surface and tangential curved surface SS of the outlet channel which are created along the line, a portion of the jet S １２１ When the material is brought directly into the inner exit, it is made possible to flow along the tangent curved surface SS, and the angle θ of its turning angle D1 ２１ ＊＊ Reduce, 0°≦θ ２１ ＊＊ The valve body flow path of the global valve according to claim 1, characterized in that it satisfies the condition of ≤60°.

13. Distal point E ３ ＊＊ There is a height difference H between the valve seat and the valve seat. １ ＊＊ It has H １ ＊＊ ≥ B １ , 0.5≧H １ ＊＊ / d ０ The condition ≥ 0.25 is satisfied, and the new major axis of the ellipse is a ｙ ＊＊ and 2d ０ ≥ a ｙ ＊＊ ≥ 1.3d ０ The valve body flow path of the global valve according to claim 12, characterized in that it satisfies the following conditions.

14. In the aforementioned inlet and outlet passages, the inner outlet is maintained in a non-standard elliptical shape, and the valve chamber diameter d ３ and the outer diameter d of the valve seat １ This means that by designing it to be eccentric, the structure of the valve chamber becomes a hollow circular eccentric structure, and the structure of the valve chamber has a diameter of 1.8d ０ The valve chamber and a diameter of 2.2d ０ The valve chamber is divided into an annular chamber and the valve chamber, and the deviation of the center between the valve chamber and the annular chamber is 0.2d ０ The height of the top of the interior of the annular chamber is LH ７ The valve chamber and the valve seat are separated by a vertical line YL １ The valves are arranged concentrically so as to penetrate each other, and the valve chamber is used to receive the valve plug, with the center point P of the valve seat on the side of the valve inlet. １ The horizontal distance between the annular chamber and the inner diameter of the annular chamber is 0.9d ０ The center point P of the valve seat １ The horizontal distance between the annular chamber and the inner diameter on the side of the inner outlet is 1.3d ０ The annular chamber receives the annular space and the annular groove, and the width of the annular groove changes according to the eccentric design so that it has its maximum width on the side of the inner outlet, and there is a height difference H between the top of the inside of the annular chamber and the sealing surface of the valve seat. ５ It has H ５ =LH ７ -LH ３ , 0.6≧H ５ / d ０ The valve body flow path of the global valve according to claim 1, characterized in that it satisfies the condition ≥ 0.

25.

15. Distal point E ３ Height LH ４ Height LH ７ When it is higher than, LH ４ >LH ７ The following conditions are met, and in this case, distal point E ３ For example, the major axis a ｙ A new distal point E above ３ ＊＊ We need to find distal point E ３ ＊＊ From a part of the arc S ３ Apply the upper edge line S ２ａ Adjacent to, distal point E ３ ＊＊ The height difference between the valve seat and the sealing surface is 0.25d ０ ≤ H １ ＊＊ ≤0.5d ０ The line segment E is secured to satisfy the following conditions. ３ ＊＊ E ４ The long axis formed by a ｙ ＊＊ And also, the arc S ３ The inner diameter surface and tangential curved surface SS of the outlet channel are created along the line, and the distal point E ３ ＊＊ Arc S ３ and vertical line YL ３ The angle γ with ２１ ＊＊ is 30°≦γ ２１ ＊＊ The condition ≤90° is met, and distal point E ３ ＊＊ The angle of the turning angle D is θ ２１ ＊＊ Let 0° ≤ θ ２１ ＊＊ The condition ≤60° is satisfied, and the new major axis of the ellipse is a ｙ ＊＊ 2.0d ０ ≥ a ｙ ＊＊ ≥ 1.3d ０ The valve body flow path of the global valve according to claim 14, characterized in that it satisfies the following conditions.

16. The sealing surface of the valve seat is located outside the central hole, and a vertical line YL is drawn above the central hole. １ A coaxial conical tube is installed, and the conical tube has a center point P ＤＰ The valve seat has a height of LH ３ The height of the central hole is set to LH １ The height h of the conical tube has a cone angle φ, and LH ３ =LH １ The condition +h is satisfied, and the function of the conical tube is the fluid and its inlet center line S １ The valve body flow path of a global valve according to claim 1, which provides a diffusion effect, allows for smoother deflection angle B to enter the radial flow path, further reduces head loss, and the conical tube increases the structural strength of the valve seat and enhances the reliability of the seal.

17. The height h of the cone tube is 0.06 ≤ h / d ０ The valve body flow path for a global valve according to claim 16, characterized in that it satisfies the condition ≤ 0.2 and the cone angle φ of the conical tube satisfies the condition 15° ≤ φ ≤ 60°.

18. The valve body flow path of a global valve according to claim 1, characterized in that a vertical rib plate is added to the outer diameter surface of the valve seat to reinforce the strength of the valve seat, the vertical rib plate is located on the side of the inner outlet and its lower portion is connected to the bottom of the annular groove, both sides of the vertical rib plate are vertical arcuate surfaces, one side of both arcuate surfaces on both sides is in contact with the outer diameter surface of the valve seat to form a wide bottom side, the other sides of both arcuate surfaces on both sides intersect with each other to form an end with a small arcuate angle, and the vertical rib plate acts as a guide for the streamlines that branch out into two from the annular groove and flow toward the inner outlet.

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