Improved valve body flow channel of stop valve

Abstract

The invention discloses an improved valve body flow channel of a stop valve with a low lift loss coefficient xi and meeting ESG requirements. The valve body flow channel comprises a valve chamber, an annular groove, an inlet flow channel, a valve inlet, a valve seat, an outlet flow channel and a valve outlet. Wherein the center line of the inlet is provided with a bent arc smooth streamline, the angle of the rotating angle A is 2theta 1, and 2theta is larger than or equal to 55 degrees and smaller than or equal to 105 degrees; the bottom of the annular groove is provided with an inclined surface with an inclined angle beta; an outlet center line S2 of the outlet flow channel is a smooth streamline obliquely downwards, an inner outlet is formed in the inner diameter of the valve chamber, the angle of a corner E of an upper edge line S2a of the outlet flow channel is 2theta 21, 30 degrees < = 2theta 21 < = 90 degrees, a near end point E4 is communicated with the bottom of the inclined plane, and the height LH5 / d0 < = 0.4 of the near end point E4 is 0.4 < = LH5 / d0 < = 0.4; the jet flow S121 and the slow flow S122 can enter the outlet flow channel after passing through the diffusion C to form a rotation angle D, flow division is generated, and no flow interference is generated in the valve chamber and the inner outlet.

Description

Technical Field

[0001] The globe valve is a control valve commonly used in pipeline systems. It is popular for its high sealing reliability, easy flow adjustment, and clean and residue-free characteristics. In particular, the diaphragm valve is more suitable for high-clean applications and can be used for limited flow or pressure control in pipeline systems. However, its disadvantage is that a higher pressure difference is required to obtain the same flow. Common valves can be distinguished by closing parts (obturators). The first type uses elastic deformation seals, such as pinch valves and weir valves. The second type uses rotating parts to seal, such as butterfly valves and ball valves. The third type uses sliding parts to seal, such as gate valves. The fourth type uses covering parts to seal, such as globe valves and needle valves. The fifth type uses elastic sheet deformation seals, such as weir valves. The flow performance of the above five types of valves can be expressed by the dimensioned flow coefficient C v Value and K v It can be described by the flow coefficient or the dimensionless pressure loss coefficient ξ. For the relevant definition, please refer to chapter 1, “General information, 1-1 general guidelines term 8 and term 9”, P.2 of reference document 2; C v The larger the value, the greater the flow rate and the smaller the resistance. The larger the ξ value, the greater the resistance and the smaller the flow rate. The following C v The value refers to the condition where the valve body flow channel has the maximum flow rate when the closing member (obturator) is fully open with a 2-inch diameter, 47mm to 57mm:

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

[0003] The second type of valve: butterfly valve (butterfly-valve) flow coefficient C v The value range is 90 to 220; the flow coefficient C of the ball valve vThe value range is 210 to 500. The closing member (obturator) of the ball valve is a closing ball with a center hole. If the diameter of the center hole is the same as the diameter of the valve inlet and outlet pipes, it is called a full port valve, which has a high flow coefficient C v The valve body has a straight tube shape, and the fluid flow line is straight and almost uninterrupted. v The value can be as high as 500. The smaller the center hole, the higher the C v The smaller the value, the smaller the C v The value may only be 210.

[0004] The third type of valve: the flow coefficient C of the gate valve v The value range is 100 to 300.

[0005] The fourth type of valve: the flow coefficient C of the vertical axis stop valve (global valve) v The value range is 30 to 65, where the entrance and exit are in a straight line, see Figure 1 of Reference 3, p. 2, C v The value range is 40~60. Taking the inner diameter of 52.5mm as an example, the head loss coefficient ξ is 4.5~10.13. When the inlet and outlet are at right angles, C v The value range is 60 to 100.

[0006] C of the above valves v The value is still affected by the actual inner diameter of the pipe. When comparing, the actual inner diameter of the pipe is required. v The difference in the value represents the change in the cross-sectional area of ​​the valve body flow channel and whether the streamline is disturbed, especially the larger the curvature radius of the streamline C v The larger the value, the greater the structural difference in application requirements. v The value range varies among manufacturers and does not include Y-type stop valves.

[0007] The fifth type of valve: the flow coefficient C of the gate valve v The value range is 50~116, please refer to reference 5 and reference 6. Since the seal of the weir valve is completed by a sealing curve, it is difficult to achieve high reliability sealing requirements, but its outlet flow channel and inlet flow channel can be formed into a smooth curved line. Most C v The values ​​can reach 60 to 80. The patent design C of reference document 5 and reference case 9 v The value can reach 110-116, but its pipe diameter is 57mm, and its head loss coefficient ξ is 1.7. The diameter of reference document six is ​​47.8mm, and its head loss coefficient ξ is 4.47.

[0008] The valve body flow channel of the present invention aims to improve the internal flow channel of the vertical axis stop valve, and uses the dimensionless head loss coefficient ξ as the improvement index to replace the existing C v The invention is described by taking a 2-inch, 52.5 mm stop valve with the inlet and outlet in the same straight line as the target. The invention aims to improve the flow passage of the existing valve body. If a 2-inch inner diameter of 52.5 mm and an inner diameter ratio of d3 / d0 = 2.0 is taken as an example, the invention pursues the head loss coefficient of the valve body flow passage ξ1.7≤ξ≤3.0, 100≥C v ≥73.5, surpassing the effect of existing stop valves. Background Art

[0009] The content of the present invention is a dimensional flow coefficient C v Value or K v The value is used as a reference indicator to illustrate the effect of improving the valve body flow channel of the stop valve. The dimensionless head loss coefficient ξ value is also used to accurately illustrate the improvement effect. The head loss coefficient ξ of valves with the same structure will gradually decrease as the diameter size increases. The difference between these two values ​​is in units, C v It is the US flow rate Q at 1 psig pressure difference, in usgpm, K v It is the metric flow rate Q under the pressure difference ΔP = 1 bar, in cmh, After the units are converted, C v The value is K v 1.156 times the value, due to C v Value or K v The value is a dimensionless coefficient that is positively correlated with the cross-sectional area of ​​the pipeline, that is, valves from different manufacturers have the same C v Value or K v When the value is set, it is very likely that the difference in the inner diameter of the pipe will result in different head loss coefficient ξ values. The lower the head loss coefficient ξ value, the lower the head loss and the less energy required for pipeline transportation. Many valve manufacturers will use To represent K v The values ​​are expressed as follows to facilitate valve users to select more concisely:

[0010] This pressure difference ΔP between the inlet and outlet of the valve body is also called pressure loss (head loss). v Value or K v The higher the value, the more flow can be transported under a certain pressure difference, which is very beneficial to the energy-saving needs of low-lift transportation in the pipeline system.

[0011] The present invention can also introduce a dimensionless head loss coefficient ξ value as an indicator to illustrate a more accurate effect of improving the valve body flow channel of the stop valve. The head loss coefficient ξ value is described by using the pressure difference ΔP (pa) and the average flow V of the pipeline:

[0012]

[0013] ΔH L (m) is the water level difference used to describe the head loss. The ξ in the formula is a dimensionless coefficient called the head loss coefficient. It is a dimensionless coefficient that is independent of the size of the pipeline. This coefficient is completely equivalent to the pressure loss coefficient ξ, which can reflect the pressure loss coefficient of the internal flow channel structure of the valve body. It can also be used as a reference for the design of different internal flow channel structures. The valve body flow channels with similar structures can obtain the same ξ value. The lower the value, the less pressure loss and the greater the flow rate. is the dynamic pressure P in the pipe d , which can also be regarded as the average dynamic pressure of the streamline in the pipeline, that is, the pressure difference ΔP (pa) can be expressed as dynamic pressure P d multiples of, and the potential difference ΔH L (m) is the head loss, H d It is the dynamic head, so the head loss ΔH L (m) can also be expressed as dynamic head H using ξ d Multiples of, and each section of the flow channel inside the valve body, such as straight pipes, elbows, right angles, etc., will have its own head loss coefficient ξ. The larger the head loss coefficient ξ, the smaller the curvature radius of the streamline in the pipeline, and the more uneven it is. In addition, the pressure loss generated by a series of pipeline components can also add up the ξ values ​​to represent the head loss coefficient ξ of the entire pipeline. For more details, please refer to the 1978 reference document 1 and the 1989 reference document 2 for related flow loss coefficient descriptions. Reference document 1 uses K b The symbol is used to represent the head loss coefficient. Reference document 2 uses the symbol ξ to represent the head loss coefficient. The present invention uses ξ to represent the head loss coefficient.

[0014] Although the calculation of the head loss coefficient ξ is dimensionless and has nothing to do with the pipe diameter, in fact, the flow pattern of the fluid in the pipe is related to the head loss coefficient ξ, because the larger the pipe diameter, the smaller the streamline curvature radius R. CIncrease, so that the larger the pipe diameter, the lower the head loss coefficient ξ, see reference document 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.

[0015] The calculation formula of the head loss coefficient ξ can be used to calculate C V The value conversion formula is as follows:

[0016]

[0017] From the above formula, we can understand the flow coefficient C V Value or K v The value is with the pipe cross-sectional area A, which is convenient for engineers to intuitively understand the flow size when selecting the valve, but in comparison with C V When measuring the value, the pipe diameter d0 must be clearly indicated, otherwise it is easy to misjudge the actual flow performance. The dimensionless head loss coefficient ξ is independent of the pipe diameter and can better reflect the actual flow performance and accurately reflect the pressure loss ΔP condition. The present invention will use the head loss coefficient ξ as an indicator for improving the valve body flow channel.

[0018] The flow channel structure of the existing stop valve can be found in reference document 2 and reference document 3. The flow channel structure of reference document 2 can be divided into structure C1, structure C2 and structure C3, and the flow channel structure of reference document 3 is structure C4.

[0019] Fig.13A The coordinate axes, coordinate points, inlet centerline S1, radial centerline S 12 , jet S 121 , Slow Flow 122 , schematic diagram of exit center line S2.

[0020] Fig. 13B This is a schematic diagram of the existing structure C3 flow channel and its installation angle, corner A, corner B, diffusion C, corner D, and corner E.

[0021] Fig.14A The coordinate axes, coordinate points, inlet centerline S1, radial centerline S 12 , jet S121 , Slow Flow 122 , schematic diagram of exit center line S2.

[0022] Fig. 14B This is a schematic diagram of the corner A, corner B, diffusion C, corner D, and corner E of the existing structure C4 flow channel.

[0023] The valve body of the existing globe valve has a hollow structure similar to a sphere or a cylinder containing a flow channel. The structure of the flow channel is composed of a valve chamber, a valve plug, an inlet flow channel, an outlet flow channel, and a partition. The partition is used to separate the inlet flow channel from the outlet flow channel. A valve seat is installed on the horizontal surface of the partition. The valve seat has a sealing surface and a center hole. The inlet flow channel has a valve inlet connected to the center hole. The valve chamber has the concentric valve plug and valve shaft and a sealing device installed inside, and the partition and the valve seat are installed to connect the inlet flow channel and the outlet flow channel. The inner diameter of the valve chamber is provided with an inner outlet. The outlet flow channel has a valve outlet connected to the inner outlet. The valve inlet and the valve outlet are respectively installed on both sides of the valve body. When the outlet flow channel is a straight pipe or a circular arc bend in a downward inclined form, the inner outlet is a non-standard elliptical shape.

[0024] The inner diameter of the valve chamber is d3, the outer diameter of the valve plug is d2, the outer diameter of the valve seat is d1, the valve inlet diameter is d0, and the valve outlet diameter is d0.

[0025] The center point P1 of the center hole has a height of LH1, the center point P3 of the inner outlet has a height of LH2, the sealing surface of the valve seat has a height of LH3, and the center point P DP ; The center point of the valve inlet is P2, and the center point of the valve outlet is P4.

[0026] A horizontal line XL1 passes through the center point P1 of the center hole, and the horizontal line XL1 intersects with the circumference of the center hole at two intersection points, the distal end point E1 and the proximal end point E2. The distal end point E1 is located at the valve inlet side, and the proximal end point E2 is located at the valve outlet side.

[0027] A tube axis XL2 (X-axis) passes horizontally through the center point P2 and the center point P4. The height marking of the present invention is based on the tube axis XL2 connecting the valve outlet and the valve inlet. The coordinate zero point of the Y-axis will have positive values ​​(>0), zero values ​​(=0) and negative values ​​(<0) when indicating the position relative to the tube axis XL2.

[0028] A vertical line YL1 passes through the center point P1 and intersects the tube axis XL2 at the intersection point P 11 .

[0029] A vertical line YL2 passes through the center point P4, and the vertical line YL2 intersects the valve outlet circumference at two intersection points, the distal end point E5 and the proximal end point E6. The height of the distal end point E5 is d0 / 2, the height of the proximal end point E6 is -d0 / 2, and the proximal end point E6 is the lowest point of the outlet flow channel.

[0030] A vertical line YL3 passes through the center point P3 and intersects the tube axis XL2 at the intersection point P 31 , and the vertical line YL3 intersects with the inner outlet circle at two intersection points, the distal end point E3 and the proximal end point E4, the height of the distal end point E3 is LH4 and the height of the proximal end point E4 is LH5.

[0031] A vertical line YL4 passes through the center point P2 and intersects the valve inlet circle at two intersection points, the distal end point E7 and the proximal end point E8. The height of the distal end point E7 is d0 / 2, the height of the proximal end point E8 is -d0 / 2, and the proximal end point E8 is the lowest point of the inlet flow channel.

[0032] There is a horizontal distance L1 between the center point P1 and the center point P2. 11 P2=L1; there is a horizontal distance L2 between the center point P4 and the center point P1, P4P 11 =L2; there is a horizontal distance L between the center point P2 and the center point P4, P4P2=L=L1+L2;

[0033] There is a horizontal distance LL2 from the center point P4 to the center point P3, LL2 = L2-d3 / 2 = P 31 P4;

[0034] The valve plug is cylindrical and has a flat surface at the bottom. When the stop valve is closed, the valve plug is used to couple and seal with the sealing surface. When the valve is fully open, the bottom surface of the valve plug and the sealing surface form a radial flow channel with an opening B1. The structure of the radial flow channel is affected by the structure of the sealing surface and is a horizontal flow channel or a 45-degree upward conical flow channel. The preferred embodiment is a horizontal flow channel, and B1 / d0=0.25.

[0035] The inlet flow channel includes the valve inlet, an inlet center line S1, the center hole, an upper edge line S 1a With the edge line S 1b The inlet flow channel enters the valve inlet horizontally and turns upward and forms the center hole at its outlet; the inlet center line S1 connects the center point P1 and the center point P2 and forms an angle γ1 with the vertical line YL1 at the center point P1; when the angle γ1≠0°, the center hole will be a non-standard elliptical hole with a major axis a in the X-axis direction. x , a x ≥d0,a x =E1E2, E1P1≥P1E2, with a short axis b in the Z direction z , b z=d0; when the angle γ1 = 0°, the center hole will be a circular hole with a diameter of d0. 1a Connecting the distal end point E1 and the distal end point E7, the lower edge line S 1b The proximal end point E2 and the proximal end point E8 are connected.

[0036] The radial flow channel includes a radial center line S 12 , opening B1, the height of the radial flow channel surrounding the central hole is LH6, LH6 = LH3 + B1. Radial centerline S 12 , connecting the center point P1 and the center point P3; it flows out from the center point P1 in a radial manner in different directions and finally connects to the center point P3.

[0037] The outlet flow channel includes the inner outlet, the valve outlet, an outlet center line S2, an upper edge line S 2a With the edge line S 2b The outlet center line S2 connects the center point P3 and the center point P4, and has an angle γ2 with the vertical line YL3 at the center point P3, 0°≤γ2<90°. The inner outlet is a non-standard elliptical hole with a major axis a in the Y-axis direction. y , a y ≥d0,a y =E3E4, E3P3≥P3E4, with a short axis b in the Z direction z , b z = d0, when the outlet flow channel is a horizontal straight pipe, the angle is γ2, γ2 = 90°, a y = d0. The upper edge line S 2a Connecting the distal end point E3 and the distal end point E5, the lower edge line S 2b Connect the proximal end point E4 and the proximal end point E6. The distal end point E3 has a height difference H1 relative to the sealing surface, H1 = LH4-LH3, when the distal end point E3 is higher than the sealing surface, H1≥0, otherwise H1≤0; the inner outlet center point P3 has a height difference H3 relative to the sealing surface, H3 = LH2-LH3, when the P3 point is higher than the sealing surface, H3≥0, otherwise H3≤0.

[0038] A radial clearance B3 is located between the outer diameter d2 of the valve plug and the inner diameter d3 of the valve chamber, B3 = (d3-d2) / 2, 0.2≤B3 / d0≤0.4; If it is too small, the valve chamber space above the valve plug will have a stagnant space and cause particle condensation problems. An annular space B2, between the valve seat outer diameter d1 and the valve chamber inner diameter d3, B2 = (d3-d1) / 2, 0.25≤B2 / d0≤0.4. An inner diameter ratio d3 / d0, the ratio of the valve chamber inner diameter d3 to the valve inlet diameter d0, 1.75≤d3 / d0≤2.2; the size of the valve body is positively correlated with the inner diameter ratio d3 / d0, and the larger the inner diameter ratio d3 / d0, the larger the curvature radius of the fluid, but there are problems of excessive volume and high cost.

[0039] Regarding the description of the flow channel of the valve body and the flow phenomenon of the fluid, the word "turn" or "bend" will be used to indicate the description of the change of flow direction of the streamline S. The inlet center line S1, the radial center line S 12 The three center lines including the outlet center line S2 represent the streamlines, and the description of these turning angles is limited to the basis of the inferred geometric shapes. Further description will require complex 3D-CFD calculations to obtain.

[0040] The inlet center line S1 can be a single line segment or a combination of several line segments. The line segment types include: arc curve, vertical line segment, oblique line segment, horizontal line segment, etc., wherein the vertical line segment is coaxial with the vertical line YL1, and the horizontal line segment is coaxial with the tube axis XL2. The inlet center line S1 has an angle A, and a point P is set on the tube axis XL2. 12 , one end of the oblique line segment or arc curve is connected to the tube axis XL2 at point P 12 , one end of the arc curve is tangent to the tube axis XL2 at point P 12 ; The line segment combination is suitable for casting or forging as appropriate; if the inlet center line S1 is a single arc curve or a single horizontal straight line, it is suitable for injection molding; through point P 12 Draw a vertical line YL6 and take a point P0 on the vertical line YL6 so that the line segment P0P 12 is the same length as line segment P0P1, while line segment P0P 12 The angle 2θ1 between the line segment P0P1 is equal to the rotation angle A, and the placement angle θ1 is equal to the line segment P1P 12 The horizontal angle of point P 12 When it overlaps with point P2, it means that the inlet flow channel is a single arc curve or a single oblique line segment.

[0041] The radial center line S 12 After the fluid flows out of the center hole, all streamlines will flow out in different directions in a radial manner and enter the radial flow channel. The turning angle B is from the inlet center line S1 to the radial center line S 12 All streamlines will flow through the radial flow channel and the annular space B2 to diffuse C and will flow toward the inner outlet after several turns.12 The flow rate of the fluid in diffusion C slows down after turning corner B because the area of ​​the radial flow channel increases, but when it flows toward the inner outlet after several turns, it accelerates because the area decreases; the radial centerline S 12 Affected by the relative position between the sealing surface and the inner outlet, it can be a straight line or an arc, or a multi-bend arc.

[0042] The radial center line S 12 Since the fluid is driven by the pressure difference between the valve inlet and the valve outlet, the radial center line S of the diffusion C 12 Can be divided into jet S 121 With slow flow S 122 The dense streamlines that are subjected to the high pressure gradient are the jets S 121 The low-density streamline with higher flow velocity and low pressure gradient is a slow flow. 122 Its flow rate is slightly lower. The radial center line S 12 The streamlines of the diffusion C flow will fan out in the circumferential direction and be affected by the angle B. The jet S 121 will fan out toward the inner outlet, and the slow flow S 122 The fan-shaped expansion will be performed at a circular angle other than the fan-shaped expansion angle of the jet; some jets S 121 will flow directly into the inner outlet, and the remaining jet S 121 With slow flow S 122 The valve will be divided into two streams in the valve chamber, tumbling along the inner diameter and entering the inner outlet. 12 , jet S 121 With slow flow S 122 Before the diffusion C flow and the flow into the inner outlet, they will make different angles of turn D, jet S 121 The corner is D1, the slow flow is S 122 is the turning angle D2; jet S 121 With slow flow S 122 The flow interference will be affected by the internal structure of the valve chamber and will cause different degrees of flow interference, and the head loss will increase depending on the severity.

[0043] The outlet centerline S2 can be a single line segment or a combination of several line segments, and the line segment types include: arc curve, oblique line segment, horizontal line segment, etc., wherein the horizontal line segment is coaxial with the tube axis XL2. The outlet centerline S2, the turning angle D is the radial centerline S 12 The fluid makes a turn at angle E between the inner outlet and the outlet flow channel and then flows out of the valve outlet; the turn at angle D will cause head loss, and serious head loss will occur in the jet S at the inner outlet. 121 With slow flow S 122The outlet center line S2 and the pipe axis XL2 are provided with a point P 34 , one end of the oblique line segment is connected to the tube axis XL2 at point P 34 , or one end of the arc curve is tangent to the tube axis XL2 at point P 34 ; Angle E is generated only when there is an arc curve or an oblique line segment; Line segment combinations are suitable for casting or forging as appropriate; If the outlet center line S2 is a single arc curve or a horizontal straight line, it is suitable for injection molding; Through point P 34 Draw a vertical line YL5 and take a point P5 on the vertical line YL5 so that the line segment P5P 34 is the same length as line segment P5P3, while line segment P5P 34 The angle 2θ2 between the line segment P5P3 is equal to the rotation angle E, and the placement angle θ2 is equal to the line segment P3P 34 The horizontal angle of the arc segment is 20°; since the flow of the arc will not have a higher head loss than the inclined line with a turning, the inclined line segment at point P 34 There will be a large horizontal elbow angle θ2, which will increase some head loss and small recirculation area; when point P 34 When it overlaps with point P4, it means that the inlet flow channel is a single arc curve or a single oblique line segment.

[0044] Angle A refers to the turning angle of the inlet centerline S1. The fluid flows into the horizontal valve inlet and turns upward at Angle A to enter the center hole. When Angle A is a right angle, the head loss coefficient can be as high as ξ=1.0. Please see Reference Document 2, p169, "diagram 6-5, Elbow without recess". The right-angle Angle A will produce several recirculation areas N in the inlet flow channel, among which a large recirculation area N will be generated near the center hole and block the flow channel cross-sectional area, seriously increasing the head loss. Angle A, when Angle A < 90 degrees, the angle γ1 > 0, the sealing surface of the valve seat of the center hole in the horizontal plane will become a non-standard ellipse. When the diameter of the center hole is corrected to d0, the major axis a x The reduction ratio is d0 / a x , d0 / a x <1.0.

[0045] The angle B refers to the angle between the inlet centerline S1 and the radial centerline S 12 The fluid flows upward from the central hole and turns into the horizontal radial channel at angle B and flows in the radial direction of the circumference. Most of the fluid in the radial channel will flow toward the inner outlet. When the angle γ1>0 degrees and the turning angle B<90°, the effective cross-sectional area of ​​the channel will decrease and C vAngle B, Angle B will be affected by the turn A, especially when the inlet flow channel produces a large recirculation area N, which will force the streamline to deviate and affect the angle of the angle B. Angle B, when the sealing surface is an inclined upward conical surface, for example, angle B = 45°, making the radial flow channel a conical flow channel, the jet S 121 It will flow upward obliquely into the large space of the valve chamber, and the flow of the diffuser C must make more turns before flowing into the inner outlet, which will cause a large head loss and flow interference in the valve chamber.

[0046] Diffusion C, the radial center line S 12 The distribution and velocity changes of streamlines S when the fluid flows through the radial flow channel and the annular space B2, and the jet S 121 The slow flow S enters the radial flow channel from the central hole near the inner outlet and diffuses in a fan-shaped manner in the circumferential direction. 122 The flow from the central hole in other circumferential directions into the radial flow channel is fan-shaped and diffused in the circumferential direction, and the slow flow S 122 In the valve chamber, the two jets are divided into two streams, which flow in opposite directions along the inner diameter of the valve chamber and then enter the inner outlet respectively; the partial jet S 121 will flow directly to the inner outlet, and the remaining part of the jet S 121 It will also be divided into two streams and flow along the inner diameter circumference of the valve chamber to the inner outlet; the jet S 121 With slow flow S 121 The flow interference will occur in the valve chamber, resulting in additional head loss. Diffusion C, angle B is 45°, when the jet S is sprayed upward 121 It will make multiple turns before entering the inner outlet, resulting in additional head loss. If the inner diameter ratio d3 / d0 is too small, the jet S 121 With slow flow S 121 Flow interference will occur in the valve chamber, resulting in additional head loss; when the radial flow channel is horizontal, the flow rate of the fluid will smoothly slow down due to the linear increase in the cross-sectional area of ​​the radial flow channel and the annular space, and the flow of the fluid will also be obstructed by the inner diameter of the valve chamber, resulting in a turning point.

[0047] The angle D refers to the radial center line S 12 The radial center line S 12 The angle D with the outlet centerline S2 can be described by 2θ2, 2θ2 = 90°-γ2. The streamlines of the diffuser C will turn from the radial flow channel to the annular space. The streamlines before entering the inner outlet may make a more obvious turn or multiple turns, including the jet S 121 Corner D1 and slow flow S 121 Corner D2. Corner D1, jet S 121 The turning angle between the streamline and the outlet center line S2 of the inner outlet, including the jet S 121At the turning angle from the diffusion C to the inner outlet, part of the jet S 121 The turning angle of the valve outlet directly passing through the inner outlet. 122 The turning angle between the streamline and the outlet center line S2 of the inner outlet, including the slow flow S 122 The turning angle from the divergence C to the inner outlet. Angle D, if the outlet centerline S2 is a slant line, the turning angle D is θ2. If the outlet centerline S2 is a circular arc, the turning angle D = 2θ2. This part of the turning angle D will make the jet S 121 The head loss occurs. 121 The angle α1 with the outlet center line S2, slow flow S 122 The included angle α2 with the outlet centerline S2, the jet S 121 With slow flow S 122 The streamline angle α3 between them, the smaller the angle α1, angle α2, and angle α3, the lower the head loss coefficient ξ, and the higher the angle α3, the higher the jet S 121 With slow flow S 122 The higher the flow interference loss is at the inner outlet; the description of angle α1, angle α2, and angle α3 can only be described intuitively by geometric structure, but cannot be described by precise numerical quantification of such 3D streamline structure. If a more detailed description is required, 3D-CFD calculation software is needed to assist.

[0048] Angle D, when the center point P3, the sealing surface and the pipe axis XL2 are at the same height and the outlet flow channel is a horizontal straight pipe, the angle D1 = 0°, the jet S 121 Directly enter the inner outlet and flow horizontally toward the center point P4; H1>0, H3=0, LH3=LH2=0. Structure C2.

[0049] Angle D, when the proximal end point E4, the sealing surface and the pipe axis XL2 are at the same height and the outlet flow channel is a downward bend, the angle D1 = 0°, the jet S 121 Directly enter the inner outlet and flow horizontally toward the distal point P4; H1>0, H3>0, LH3=0, LH2>LH3. Structure C1.

[0050] Angle D, when the proximal end point E4 is at the same height as the sealing surface and higher than the pipe axis XL2, the outlet flow channel is an inclined downward bend pipe, and the angle D1 = 90-γ2; H1>0, H3>0, LH3>0, LH2>LH3. Structure C3.

[0051] At the turning angle D, when the partition of the valve body becomes an annular groove, the annular groove is located below the annular space and the inner outlet is installed on the inner wall of the annular groove, the outlet flow channel becomes a horizontal straight pipe, the far end point E3 is lower than the sealing surface, the center point P3 is at the same height as the center point P4 of the valve outlet, and the jet S 121It will make a downward first turn D1 = 90° to enter the annular groove and 121 When entering the inner outlet, it makes a second turn D1 = 90° and flows horizontally toward the center point P4; H1 < 0, H3 < 0, LH1 > 0, LH2 = 0. Structure C4.

[0052] The turning angle E refers to the turning point of the outlet centerline S2, including the jet S 121 With slow flow S 122 After making the turns D1 and D2, the fluid enters the outlet flow channel, and also includes mixing in the outlet flow channel and then turning to flow out of the valve outlet. After the fluid enters the inner outlet, it flows to the valve outlet. The jet S 121 With slow flow S 122 It will also form flow interference in the outlet flow channel and cause partial head loss; if the outlet center line S2 is a slant line, the turning angle E = θ2; if the outlet center line S2 is a circular arc curve, the turning angle E = 2θ2; if the outlet flow channel is a horizontal straight pipe, the turning angle E = 0; the flow of the circular arc will not have a higher head loss than the slant line with a turning point. The slant line segment at point P 34 There will be a large horizontal elbow angle θ2, which will increase some head loss and small recirculation area.

[0053] The shape of the valve chamber is affected by the position of the sealing surface and the shape of the partition. There are four existing structures, namely, structure C1, structure C2, structure C3, and structure C4. The partitions of these four structures all have a horizontal surface for setting the valve seat. The flow patterns of structures C1, C2, and C3 can be found in reference document 2, "Chapter 9Flow throughpipe fittings and labyrinth seals, Resistance Coefficients of ThrottlingDevices, Valves, Plugs, and Labyrinth Seals, Figure 9-1Flow pattern in throttlingand device, (d) global valve", p. 284. The relevant numerical ratios mentioned in the following text are estimated based on the reference figure ratio.

[0054] Structure C1, see reference document 2, "Chapter 9Flow 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 around the valve seat has an angle of about 45 degrees and a large inner diameter ratio d3 / d0 of about 2.0, which will have a lower head loss coefficient ξ=4.6, near the end point E4, the sealing surface is at the same height as the pipe axis XL2 and the outlet flow channel is a downward bend, the radial flow channel is a horizontal flow channel, H1>0, H3>0, and the angle γ1=0°, γ2=45°, this structure is suitable for metal casting, not suitable for metal forging, and not suitable for plastic injection molding.

[0055] Structure C2, see reference document 2, "Chapter 9Flow 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 walls", p. 290, the partition around the valve seat is vertical and has a small inner diameter ratio d3 / d0 of about 1.29 and a higher head loss coefficient ξ=6.9, the center point P3, the sealing surface and the pipe axis XL2 are at the same height and the outlet flow channel is a horizontal straight pipe, the radial flow channel is a 45-degree conical flow channel, LH3=0, H1>0, H3=0, and the angle γ1=0°, γ2=90°, this structure is suitable for metal casting, not suitable for metal forging, not suitable for plastic injection molding.

[0056] Structure C3, see reference document 2, "Chapter 9Flow 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 diaphragm around the valve seat is spherical with an inner diameter ratio of About 2.0, with respect to structure C1, it has a lower head loss coefficient ξ, ξ=3.4, as shown in the figure of the "Rey" type global valve in reference document 2, the proximal end point E4, the sealing surface is at the same height as the pipe axis XL2, and the outlet flow channel is an inclined downward bend pipe, the radial flow channel is a horizontal flow channel, LH3=0, H1>0, H3>0, and the angle γ1, γ1=45°, the angle γ2, γ2=45°, this structure is suitable for metal casting, not for metal forging, not for plastic injection molding; another stop valve with a similar structure but limited to metal forging, see reference document 2, "Chapter 9Flow through pipe fittings and labyrinth seals, Resistance Coefficients of Throttling Devices, Valves, Plugs, and Labyrinth Seals, Diagram9-1, Various globe and gate valves, Forged global valve", p.287, limited by the processing method after forging, its inlet flow channel is a straight pipe with two turns at corner A, one is about 45 degrees down and then turns straight up, γ1 = 0°, and its outlet flow channel is a straight pipe down, γ2 = 45°, resulting in a head loss coefficient ξ as high as 7.8, much higher than that of the "Rey" type global valve.

[0057] Structure C4, its appearance diagram sees Figure 1 of reference document 3, p.2, and its appearance diagram sees Figure 7, p.39. An annular groove is provided in the valve chamber to replace the partition to connect the outlet flow channel. The inlet flow channel and the outlet flow channel are both straight pipes and are arranged horizontally, and the sealing surface position has a height difference LH3 with the pipe axis. The radial flow channel is a horizontal flow channel, LH3>d0 / 2, that is, the horizontal position of the sealing surface is not lower than the outer diameter of the inlet and outlet pipes, H1<0, H3<0, and the annular groove with a width of B2 is provided below the annular space. The sealing surface position is higher than the distal end point E3 of the inner outlet. , so that the fluid will make a ∩-shaped reflux when flowing out of the center hole. The turning angle A of the inlet flow channel of the existing structure C4 is a right angle with a higher head loss coefficient ξ, ξ=1.0, γ1=0°, see Fig9.2, p207 of reference document 1; structure C4 has a larger inner diameter ratio, and has a lower head loss coefficient ξ value of about 4.0~6.0 relative to structure C2, and the angle γ1=0°, γ2=90°; this structure is suitable for plastic injection molding, and is a flow channel structure specially designed for semiconductor high-purity fluid transportation, but there is still concern about condensation when transporting fluid containing particles. It is also suitable for metal casting and metal forging.

[0058] Structure C1, structure C2, structure C3, the inlet flow channel turns downward from the horizontal and then reverses upward with an angle A of 90 degrees, and the flow channel is affected by the baffle structure, and the angle A of the inlet centerline S1 has three turning angles, one angle A is about 45 degrees downward, the second angle A is horizontal, and the third angle is reversed upward; the third angle A of structure C3 is reversed 45 degrees upward; the inlet flow channel of structure C2 before the entrance of the center hole is affected by the baffle so that the cross-sectional area is drastically reduced and there is a drastic head loss; the inlet flow channel of structure C1 has a large space before entering the center hole and has a secondary large head loss; structure C3 maintains a smooth cross-sectional area of ​​the inlet flow channel and its inlet centerline S1 is a smooth curved line with minimal head loss.

[0059] Structure C2, the inner outlet is located in the upper semicircular space of the outlet flow channel, the jet S 121 When spraying into the inner outlet, a large amount of backflow will be caused in the lower semicircular space of the outlet flow channel, resulting in serious head loss and particle condensation problems.

[0060] Structure C1 and structure C3, when the valve seat is fully open, the fluid passes through the corner B and is ejected horizontally in the radial flow channel. The angle D1 is zero degrees, and the jet S with an opening of B1 121 The streamlines are concentrated toward the inner outlet with diffusion C, and flow horizontally from the bottom of the inner outlet and form an angle α1 of 45 degrees with the center line of the outlet to flow toward the valve outlet. The jet S 121 The area of ​​the same height B1 that will be confined to the bottom of the major axis of the ellipse will have additional head loss; the jet S 121 With slow flow S 122There is some flow interference in the valve chamber that cannot be divided, and the two flows converge at an angle D2 of 45 degrees and enter the upper half of the elliptical inner outlet, α2 = 0°, and the jet S 121 With slow flow S 122 There is a severe high-angle flow interference, α3 = 45°, entering the inner outlet and making a turn E to flow out after mixing and diffusing in the outlet flow channel.

[0061] Structure C1, jet S 121 The turning angle D is zero degree, but it will induce an open stagnant zone in the lower edge elbow area of ​​the outlet flow channel.

[0062] Structure C2, the radial flow channel with the cone tilted upward at 45 degrees leads to the jet S 121 There will be a huge change in the cross-sectional area of ​​the flow channel, resulting in a huge head loss, and the jet S of the diffuser C 121 It is also necessary to make an arc-shaped turn to enter the upper half of the inner outlet of the horizontal outlet flow channel, but the jet S 121 It will induce an open stagnant flow area in the lower half of the outlet flow channel. 122 Conical flow is performed in other circumferential directions of the valve seat, and the small d3 / d0 ratio causes the jet S 121 With slow flow S 122 Severe flow interference occurs in the valve chamber, the inner outlet area is 50% of the outlet flow channel, there is a rapid diffusion loss, and there will be an open stagnant area with serious particle condensation problems.

[0063] Structure C3, when the valve seat is fully open, the angle B is 45°, which helps to spread the jet S of C more. 121 A large amount of flow will be concentrated toward the inner outlet side, and part of the jet S 121 The horizontal jet is ejected at an angle of 45 degrees to the center line of the outlet, entering the inner outlet and crossing the space of the outlet flow channel, resulting in a jet S 121 With slow flow S 122 There is flow interference at the inner outlet, and such flow will also cause local backflow in the radial space below the outlet flow channel; the rest of the jet S 121 With slow flow S 122 The inner diameter tumbling flow within the valve chamber does not produce stratified flow and flow interference.

[0064] In structure C3, the radial clearance ratio B3 / d0 of the valve plug is about 0.07, resulting in the valve chamber space above the valve plug becoming a stagnation area.

[0065] Structure C4, jet S 121 With slow flow S 122When the valve seat is fully open, it will be blocked by the inner diameter of the valve chamber and will expand in a large angle fan-shaped. After the fluid passes the outer diameter of the valve seat, it will make a 90-degree downward turn at the annular groove (anulus). From the corner B to the corner D, the streamline will make a ∩-shaped turn, enter the annular groove and flow to the inner outlet. Part of the jet S 121 With slow flow S 122 The flow will spirally roll in the annular groove without stratified flow, which will produce flow interference, and flow toward the inner outlet along the inclined surface of the annular groove at an inclined angle β, making a secondary turn D2 to enter the inner outlet; part of the jet S 121 The second turn D1 is 90 degrees and turns horizontally to enter the inner outlet, resulting in a reflow zone at the upper edge of the inner outlet flow channel, which is prone to particle condensation, and part of the jet S 121 Follow Slow Flow 122 At the inner outlet, serious flow interference occurs because the angle α3 is too large. After entering the inner outlet, the liquid turns at an angle E of 0 degrees and flows out along the horizontal flow channel.

[0066] Various structures and the head loss coefficient ξ that may be obtained have been disclosed from the above four structures of the valve chamber, and various structures that may reduce the head loss coefficient ξ have also been disclosed. Among them, the flow channel structure of structure C3 discloses more methods and features that are consistent with reducing the head loss coefficient ξ, and also obtains a lower head loss coefficient ξ=3.4, but it still fails to meet the objectives of the present invention.

[0067] To achieve the goal of innovation, the present invention must still meet the following restrictions:

[0068] Limitation 1: The valve seat must be able to provide high reliability sealing performance.

[0069] Restriction 2: The entrance and exit are in the same straight line to facilitate piping installation.

[0070] Limitation 3: The valve body must not have cleanliness issues, and must not have closed retention areas, open retention areas, residual areas or reflux areas to avoid particle condensation, liquid residue, etc.

[0071] Restriction 4: The inner diameter ratio of the valve body is 1.75≤d3 / d0≤2.5.

[0072] Limitation 5: The structure of the innovative flow channel of the valve body must specify the manufacturing method and material selection, because the manufacturing method will greatly limit the head loss coefficient ξ of the innovative flow channel. In other words, the comparison benchmark of the progressiveness of the innovative flow channel must consider the limitations of the manufacturing method. However, there will be detailed modifications in different manufacturing methods and material selections. These detailed modifications must be explained in the embodiments.

[0073] Limitations:

[0074] Limitation 1 is the limiting condition of the present invention for the characteristics of the stop valve, because many methods can improve C v Value or K v value, but it cannot provide high reliability performance in sealing at the same time. For example, the reliability of sealing of clamping valves, weir valves, butterfly valves, etc. is slightly insufficient. The weakness of clamping valves and weir valves comes from the problem of uneven pressure on the diaphragm, and the weakness of butterfly valves comes from the sliding friction between the circumference of the butterfly plate and the valve body; Structure C1, Structure C2, and Structure C3 can only provide high reliability sealing performance when metal materials are used for manufacturing. When plastic molding is used, the sealing performance of the structure needs to be enhanced to meet the requirements; Structure C4 can provide high reliability sealing performance when plastic molding or metal materials are used.

[0075] The second limitation, which is also the limitation condition of the present invention, is the characteristic of the stop valve, because the valve product is most easily installed in a structure where the inlet and outlet are in the same straight line; structures C1, C2, C3, and C4 can all meet this requirement.

[0076] Limitation three, which is also a limitation of the present invention, is that the retention space refers to an area where fluid can flow in but no flow occurs. The stagnant space has problems of liquid residue contamination and particle condensation. If the radial gap B3 is too small, an open retention space will be generated, causing particle condensation problems. Although the condensed particles will be transported out by the fluid, they will still affect the downstream process. The residual area refers to an area where fluid flows but the fluid cannot be completely discharged after the flow stops, resulting in liquid residue, which requires more clean liquid and cleaning time during cleaning.

[0077] Limitation 3: In structure C3, the horizontal jet S of the valve seat 121 Flowing toward the center line of the outlet flow channel from the bottom near the inner outlet side, no backflow zone is generated and no particles will condense, but there is a retention area in the space above the valve plug and there is a liquid residue problem in the inlet flow channel.

[0078] Limitation 3: In structure C4, the horizontal jet S of the valve seat 121 After passing through the annular groove and turning 90 degrees downward, the jet S 121 The inner outlet forms a 90-degree angle with the outlet center line of the outlet channel, which will cause a recirculation zone at the inner upper edge of the outlet channel and cause particle condensation problems. There will be no liquid residue problems in both the inlet channel and the outlet channel.

[0079] Limitation 4: The inner diameter ratio of structure C4 is 1.75≤d3 / d0≤2.5. For plastic injection molding structures, 1.75≤d3 / d0≤2.0 is a reasonable range. For precision cast metal structures with thickness restrictions on lining coating, 2.0≤d3 / d0≤2.5 is a suitable range. Generally, the thickness of uncoated cast iron parts and forgings is close to 2.0≤d3 / d0≤2.5. C1 and structure C3 both have a good inner diameter ratio of 2.0. The inner diameter ratio of structure C2 is 1.29, which is too small, resulting in excessive head loss. If the inner diameter ratio is 1.8 and the inner diameter ratio is 2.1, the volume multiple of the inner diameter ratio of 2.1 and the inner diameter ratio of 1.8 is up to 1.59 times; a reasonable inner diameter ratio can reduce the valve body size and maintain the jet S 121 The streamlines are reasonably fanned out, and the fan-shaped expansion of reasonable streamlines represents the jet S 121 The head loss is reduced.

[0080] Limitation four, the value of the innovation of the flow channel structure is that the head loss coefficient ξ is lower than the prior art at the same inner diameter ratio d3 / d0. Taking d0=52.5mm as an example, the preferred embodiment is the head loss coefficient ξ, 1.7≤ξ≤3.0. Reference document four has disclosed that the larger the inner diameter ratio, the lower the head loss coefficient ξ, but it has the disadvantage of being too large in size.

[0081] Limitation 5. The commonly used manufacturing method and material selection for structures C1, C2 and C3 is casting, which may be cast iron, cast copper or stainless steel. However, structures C1, C2 and C3 are not suitable for plastic injection molding or extrusion molding, nor are they suitable for metal forging. The common manufacturing method for structure C4 is injection molding and extrusion molding with plastic materials, which are also suitable for casting and forging. The selection of each material and the flow channel structure must be reinforced in the relevant embodiments according to its structural strength limitation. When structure C3 is formed by metal forging, refer to reference document 2, "Chapter 9Flow throughpipe fittings and labyrinth seals, Resistance Coefficients of ThrottlingDevices, Valves, Plugs, and Labyrinth Seals, Diagram 9-1, Various globe and gatevalves, Forged global valve", p. 287, its head loss coefficient ξ will be as high as 7.8, because the smoothness and curvature radius of the streamlines from corner B, diffuser C and corner D will be limited.

[0082] Among the above five restrictions, restriction 2 can be easily achieved but adds a lot of difficulties to the innovation of flow channel structure; in terms of head loss coefficient ξ, structure C3 has the lowest, structure C1 is second, structure C4 performs generally, and structure C2 is the worst; restriction 1 is easily achieved for metal valves, but for valves made of plastic, the valve seat needs to be further strengthened when the inclined center hole is used; restriction 3 cannot be met for structures C1, C2 and C3. Structure C4 was originally used for high-purity liquid transportation and has met some of the requirements of restriction 3. It is just that restriction 3 still has defects in the transportation of liquids containing suspended particles, but the relative problem is improveable; restriction 4 is a reasonable restriction for valve bodies of any structure, and structure C2 is a bad design for restriction 4; restriction 5 must be paid attention to in this innovation, and the innovative implementation examples must explain the relatively applicable manufacturing methods.

[0083] The object of the present invention is to innovate the flow channel of the valve body based on the structure C4, and to innovate using the original flow channel structure for high-purity fluid transportation, and to obtain the head loss coefficient ξ, 1.7≤ξ≤3.0, under the premise of the same inner diameter ratio d3 / d0.

[0084] In addition to the above four structures that have been disclosed to reduce the head pressure loss coefficient ξ, the structure of the present invention must also be designed for the detailed structure of the corner A, corner B, diffuser C, corner D and corner E to obtain a smoother streamline, among which the jet S 121 The streamline bending part formed by the diffuser C and the corner D is the most critical, and the solutions for these smooth streamlines must meet the following issues in order to achieve the goal of innovation:

[0085] Question 1: The streamlines can be smooth and have a good curvature radius from the inlet flow channel to the outlet flow channel.

[0086] Problem 2: Reduce the jet S 121 The angle between the streamline and the center line of the outlet is α1, α1 = (90-γ2), which reduces the slow flow S 122 The angle α2 between the streamline and the center line of the outlet can maintain the jet S 121 With slow flow S 122 The smallest angle between the streamlines is α3.

[0087] Problem Description:

[0088] Problem 1: The streamlines of the inlet and outlet channels are smooth, which means that the channels cannot have right angles or too small a radius of curvature, and the cross-sectional area of ​​the channels will not change abruptly, and there will be no recirculation zone or liquid residue. Structures C1, C2, and C3 all have liquid residue problems in the inlet channels. Secondly, the jet S from corner B and diffuser C to corner D 121There should not be a rapid expansion of the flow channel cross-sectional area, blockage due to a small inner diameter ratio, or a sharp bend in the streamline, which will affect the jet S from the diffuser C to the corner D. 121 The streamlines are fanned out to maintain low head losses.

[0089] Problem 1: When the inlet center line S1 of structure C3 enters the center hole of the valve seat, the angle γ1 between the inlet center line S1 and the vertical line YL1 cannot be too large. A too large angle γ1 will cause the center hole to have an excessively small major axis reduction ratio d0 / a. x , which results in the problem that the cross-sectional area of ​​the inlet flow channel is too small, and affects the distribution of the fluid in the circumferential direction of the valve seat when it flows out of the center hole and makes a turn B.

[0090] Question 1: Although the jet S of structure C2 diffuses 121 It flows along the 45-degree corner B and makes another 45-degree turn at corner D to flow to the inner outlet. The problem is that the flow channel cross-sectional area is not smooth and the inner diameter ratio is too small, resulting in excessive head loss. Among them, the 45-degree upward jet S of the diffuser C 121 There will be huge changes in the cross-sectional area of ​​the flow channel, resulting in huge head loss, and the jet S of the diffuser C 121 It is also necessary to directly make a circular arc turn and enter the inner outlet again at an angle D of 45 degrees to enter the upper half of the horizontal outlet flow channel. In addition, the small inner diameter of the valve chamber will also cause the jet S 121 With slow flow S 122 A flow interference occurs in the valve chamber.

[0091] Problem 1: The inlet flow channel of structure C4 is a horizontal straight pipe and the sealing surface of the valve seat is higher than the outer diameter of the inlet pipe. The fluid flowing in horizontally reaches the center hole of the valve seat at a right angle upward, which will cause the backflow area to be blocked and the streamline curvature radius to be too small.

[0092] Question 1: Diffusion C jet S of structure C4 121 It makes a 90-degree downward turn at angle D1 to enter the annular groove, and the jet S 121 In the annular groove, a secondary turn D1 of 90 degrees is required to flow to the horizontal inner outlet. The jet S 121 The streamline passing through multiple bends will cause head loss and the problem of streamline curvature radius being too small.

[0093] Problem 2: Reduce the jet S 121 The angle α1 between the streamline of the inner outlet and the center line of the inner outlet is the angle between the streamline of the inner outlet and the center line of the inner outlet. 121 The streamlines flow through the corner B from the central hole, through the radial flow channel, fan-shaped diffusion C, and make a corner D to flow directly to the inner outlet, including directly flowing into or making a small angle bend to flow into the inner outlet. The jet S of structure C1 and structure C3 121The angle D1 is zero degrees, that is, the jet S 121 The angle α1 with the outlet centerline S2, The flow channel inside the inner outlet can pass through the outlet centerline S2 and flow toward the valve outlet, but such a high angle α1 will cause flow interference and additional head loss.

[0094] Question 2: Although the jet S of structure C2 121 It sprays upward at a 45-degree angle, and then makes multiple turns D1 before entering the horizontal inner outlet. Its turn angle E is zero, that is, there is still an excessively high angle α1 at the inner outlet. In addition, the problem of a rapid area change between the inner outlet and the outlet flow channel still causes high head loss.

[0095] Question 2: Although structure C4 has the annular groove, its jet S 121 There is a primary turn D1 of 90 degrees flowing downward along the Y axis, and a secondary turn D1 jet S 121 The high angle α1 between the outlet centerline S2,

[0096] Problem 2: Slow Flow 122 The angle α2 between the streamline of the inner outlet and the center line of the inner outlet is the angle between the streamline of the inner outlet and the center line of the inner outlet. 122 The streamlines emerge from the central hole, forming a fan-shaped jet S 121 In other circumferential directions, it is divided into two streams, which flow in opposite directions along the inner diameter of the valve chamber and then enter the inner outlet, slow flow S 122 The streamline angle α2 is a three-dimensional angle, including the flow of circumferential turning and oblique downward turning, which is not easy to describe with data, but the geometric shape of the valve chamber can be used to describe the improvement of the angle α2.

[0097] Problem 2: Maintaining the jet S 121 With slow flow S 122 The small angle α3 between the streamlines is to reduce the jet S 121 With slow flow S 122 The mixing loss caused by the mutual interference caused by the angle difference between the two jets S of structure C1 and structure C3 121 The flow is horizontal to the valve outlet, slow flow S 122 It will make a 45-degree turn D in the valve chamber and flow obliquely downward along the outlet centerline S2 into the inner outlet. 121 With slow flow S 122 The included angle α3 between them is α3 = 45°, and the two have violent flow interference at the inner outlet and violent mixing in the outlet flow channel, resulting in increased head loss.

[0098] Problem 2: The turning angle B of structure C2 is 45 degrees and is limited by the small inner diameter ratio, resulting in the jet S 121 In this valve chamber, a slow flow S 122 Severe disturbance, although the jet S 121 Multiple corners D are made in the valve chamber to form a horizontal jet S 121 , which makes the angle α3 confusing and difficult to estimate.

[0099] Question 2: Structure C4 has an annular groove structure that can guide the slow flow S 122 Flowing along the slope reduces the angle of the secondary turning angle D2 and also reduces the angle α2, but the jet S 121 The secondary turning angle D1 of the downward flow along the Y axis is still 90 degrees with an excessively large angle α1, while the slow flow S 122 Flowing along the bottom slope of the annular groove at an angle β, resulting in the jet S 121 With slow flow S 122 If there is still an excessively large angle α3, α3 ≥ 45°, flow interference will result in a significant increase in head loss.

[0100] From the discussion of Question 1 and Question 2 above, it can be known that the inlet centerline S1 and the radial centerline S 12 , the outlet centerline S2 cannot have a large bend, and the corners B, diffusion C, and corner D between the streamlines need to maintain a reasonable radius of curvature to reduce the jet S of the diffusion C. 121 With slow flow S 122 The flow interference generated in the valve chamber, although the corner B is a 90-degree turn, the corner B is also a 360-degree radiation diffusion to reduce the head loss, and the jet S of the corner D 121 With slow flow S 122 No flow interference can occur at the inner outlet, and the streamline angles α1, α2, and α3 cannot be too large. The above existing structures, except for the flow field of structure C3, are partially close to these requirements, but the head loss coefficient has not yet reached the innovation goal. A more advanced and comprehensive solution can further achieve the goal of low head loss coefficient ξ. In addition to the above existing solutions, the following prior art reference documents and existing reference cases are also available for reference.

[0101] Reference Document 1

[0102] 1978, author DSMILLER, book title internal flow system, number TREX-130713.0001, edition second edition, publisher BHRA.

[0103] Reference Document 2

[0104] 1989, authors Erwin Fried and IE Idelchik, book title Flow Resistance: A Design Guide for Engineers, ISBN number 0-89116-435-9, publisher Hemisphere Publishing Corporation.

[0105] Reference Document 3

[0106] 2005. SEMI F99—Dimensional Specification of a Diaphragm Valve for a Metric PFA Tube. Publisher: EMI.

[0107] Reference Document 4

[0108] 2021 SWAGELOK Catalog, Ultrahigh-Purity Fluoropolymer Diaphragm Valves, MS-02-171, RevI, March 2021, Flow Data Flow Coefficients on page 5 of this reference catalog, taking the table of FineThread Flare End Connections as an example, the C of a 1-inch valve in a medium size 2ways valve body v The value is 3.6. In the large size 2ways valve body, the C v The value is 10.2, and the valve body of the 1 / 2-inch valve in the small size2ways has a C v The value is 0.8, and the C v The value is 2.6, which shows that the inner diameter ratio of the valve body With C v The value is positively correlated, and its inner diameter ratio The larger the valve chamber space, the larger the streamline curvature radius will be and the higher the C v value, but the inner diameter ratio The valve body size may be too large; conversely, the head loss coefficient ξ is related to the ratio of the inner diameter of the valve chamber d3 to the inner diameter of the center hole d0. Inversely related, the inner diameter ratio The larger the head loss coefficient ξ, the lower the inner diameter ratio The smaller the diameter, the higher the head loss coefficient ξ. There will be too large a head loss coefficient ξ.

[0109] Reference 5

[0110] 2020 GF Piping Systems–Industrial Piping Systems Catalog, handbediende-membraanafsluiters-type-514.pdf, page 3, Table K v 100 values ​​(flow characteristics) Type 514–517, DN50 actual inner diameter 57 mm C v The value is 116cmh, and the head loss coefficient ξ is 1.7.

[0111] Reference Document 6

[0112] 2022-CKD-Weir Diaphragm Valve SWD / MWD Series Catalog CC-1096T 8, page 1Weir Diaphragm Valve Pneumatic SWD Series Specifications Model SWD5※-50C v The value is 50, its diameter is 47.8mm, and the head loss coefficient ξ is 4.47.

[0113] Reference Document 7

[0114] 2021-Hezhengfeng Technology / bueno catalog, flow control, KH200, page 40; the flow channel structure is structure C4, KH200-19P, diameter 16mm, inner diameter ratio is 2.09, and its C v value is 4.5, and the head loss coefficient ξ is 5.18; KH200-25P, diameter 22mm, inner diameter ratio is 1.88, and its C v value is 9.1, and the head loss coefficient ξ is 6.04; KH200-40P, diameter 33.7mm, inner diameter ratio is 1.87, and its C v The value is 0.9, and the head loss coefficient ξ is 6.30.

[0115] Reference Case 1

[0116] 1898 US patent, US606867 (A)-valve, Fig.1, the reference case has a similar structure to structure C2 and also has the same flow channel weakness, the corner B is 90 degrees horizontal jet S 121 Flowing toward the axis of the outlet channel, the jet S 121 The angle D and angle E are both 0 degrees, but the radial width ratio is too small. Ratio to radial clearance The diffuser C streamline must make too many turns in the radial flow channel, causing the jet S 121 With slow flow S122 The flow interference in the valve chamber causes high head loss. These weaknesses cannot solve the problems 1 and 2. The radial clearance between the outer diameter of the valve plug and the inner diameter of the valve chamber is About 0.025 causes the valve chamber space above the valve plug to become a stagnation area, and the inner diameter ratio About 1.67 is not conducive to reducing the head loss. This reference case can be made by casting method but is not suitable for plastic injection molding or metal forging.

[0117] From the above discussion, this reference proposal cannot solve the requirements of Problem 1 and Problem 2, nor can it meet the requirements of Limitations 3 and 4. It is necessary to specify the casting method to meet Limitation 5. For example, the head loss coefficient ξ of structure C2 still cannot meet the innovation goal.

[0118] Reference Case 2

[0119] The 1927 US patent, US1647823A-Valve, Fig. 1, meets the requirements of restrictions 1 and 2, but cannot meet the requirements of restriction 3. The structure of this reference case is similar to structure C4, and the inner diameter ratio is slightly smaller than restriction 4. The head loss will be slightly increased by about 1.71. The inlet flow channel has a turning angle A of 90° and extends into the valve chamber to form an independent elbow. The radial clearance of the valve plug is About 0.24 will not produce stagnant space to cause particle condensation, the radial width ratio A smaller ratio of about 0.268 can only provide a smaller curvature radius for the streamline of diffusion C, and the annular space is connected to the bottom space of the valve chamber; an open stagnant area is easily generated in the space below the independent bend at the bottom of the valve chamber, which cannot meet the requirements of restriction three.

[0120] Question 1: The inlet flow channel is a curved pipe structure with a smooth cross-sectional area, its corner A is 90° and the curvature radius of the streamline is very good. The outlet pipe is a straight pipe with a smooth cross-sectional area, the corner B is 90° and the curvature radius of the streamline is small; the jet S 121 The streamlines of the diffuser C in the radial flow channel will be concentrated on the inner outlet side. The streamlines of the diffuser C are blocked by the inner diameter of the valve chamber and make a first downward turn D of 90° to enter the annular space, slowing down the flow S 122 After passing the corner D2, the streamline will flow down along the slope of the bottom of the annular groove to the inner outlet, and make a second turn of about 30° at the corner D2 to flow into the inner outlet. 121 When the jet flows through the far end point E3, it needs to make a secondary turn D1 of 90° to enter the inner outlet. The outlet flow channel is a horizontal straight pipe with a turn angle E of 0°, but the jet S 121 The secondary turning angle D1 will cause a recirculation zone to form in the upper edge space of the outlet flow channel; the slow flow S 122When the flow is downwardly inclined, a separation flow is generated when passing over the independent elbow and the bottom of the valve chamber is caused to become an open stagnant area.

[0121] Question 2: Due to the jet S 121 The streamline makes a secondary turn D of 90° and bends downward to enter the inner outlet, slowing down the flow S 122 There is an angle of about 30° with the center line of the outlet. Although the outlet flow channel is a straight pipe with an angle E of 0 degrees, the jet S 121 With slow flow S 122 A large angle between the two will cause flow interference at the inner outlet, and a recirculation zone and mixed diffusion will be generated in the outlet flow channel, causing more pressure loss.

[0122] From the above discussion, this reference case cannot meet the requirements of Problem 1 and Problem 2, and cannot meet the requirements of Limitation 3 and Limitation 4. For example, the head loss coefficient ξ of structure C4 still cannot meet the innovation goal.

[0123] Reference Case 3

[0124] The 1945 US patent, US2381544A Diaphragm Valve, Fig.1, meets the requirements of restrictions 2 and 4, but cannot meet the requirements of restriction 3. The structure of this reference case is similar to structure C4, which has a cylindrical valve chamber space and a diaphragm directly sealed without the valve plug. The diaphragm has good sealing performance and will not produce stagnant space to cause particle condensation. However, the diaphragm is directly pressurized, which will have life concerns and cannot meet restriction 1. It meets the inner diameter ratio of restriction 4. The inlet channel has a turning angle A of 90° and extends into the valve chamber to form an independent elbow. The radial width is about About 0.31 can provide a more appropriate turning of the streamline of the diffuser C, because the center of the diaphragm is conical and has an inner concave ring structure formed around it when fully opened; the distal end point E3 of the inner outlet is lower than the sealing surface of the valve seat, forming a smooth turning ∩-shaped guide flow channel in the valve chamber, so that the jet S 121 With slow flow S 122 The first turn D1 and the turn D2 can be smoothly made to enter the annular groove downward and flow interference will be generated in the annular groove; the jet S 121 When the jet flows through the far end point E3, it needs to make a secondary turn D1 of 90° to enter the inner outlet. The outlet flow channel is a horizontal straight pipe with a turn angle E of 0°, but the jet S 121 The secondary turning angle D1 will cause a recirculation zone to form in the upper edge space of the outlet flow channel.

[0125] Question 1: The inlet flow channel is a horizontal upward curved pipe with a smooth cross-sectional area. The structure of the outlet flow channel is also a horizontal straight pipe. The bottom of the annular groove is a curved surface structure. The corners B, diffusion C, and corners D are guided by cones and concave rings to guide the fluid into a ∩-shaped smooth turning, which greatly increases its curvature radius, so that the first corner D of the fluid forms a ∩-shaped smooth turning and flows smoothly downward into the annular groove. The jet S 121 With slow flow S 122 No flow interference will be formed in the valve chamber; and the slow flow S 122 Separate flow occurs over the separate elbow and creates an open stagnant area at the bottom of the valve seat outer diameter.

[0126] Problem 2: Jet S 121 Before entering the inner exit, it is necessary to make another turn at an angle of 90° D1 to slow down the flow S 122 At the inner outlet, a turn D of about 30° is made. Although the outlet flow channel is a horizontal straight pipe with a turn E of 0°, the jet S 121 With slow flow S 122 A large angle between the two will cause flow interference, and the mixing after entering the horizontal inner outlet will cause head loss.

[0127] From the above discussion, this reference case cannot meet the requirements of Problem 1 and Problem 2, nor can it meet the requirements of Limitation 1 and Limitation 3. For example, the head loss coefficient ξ of structure C4 still cannot meet the innovation goal.

[0128] Reference Case 4

[0129] In 1953, the US patent US2638307-diaphragm valve, Fig. 1, met the requirements of limitation 1, limitation 2 and limitation 4, but failed to meet the requirement of limitation 3. The structure of the reference case is similar to structure C4, which has a cylindrical valve chamber space and a diaphragm and a valve plug with a spherical curved surface. The diaphragm has good sealing performance, but the narrow space on the valve plug and the radial clearance are smaller than Too small will create stagnant space and cause particle condensation, which meets the inner diameter ratio of restriction 4. About 1.85, the inlet channel angle A is 90 degrees and is at right angles, the radial width ratio The ratio of about 0.25 is too small to provide a more appropriate turning of the streamline of the diffusion C. When fully open, the fluid will make a turn B of 45° along the spherical surface and flow out in a conical diffusion C. The annular groove has a downwardly inclined surface and surrounds the outer diameter of the valve seat and is connected to the bottom of the outer diameter of the valve seat and then connected to the inner outlet. The distal end point E3 of the inner outlet is higher than the sealing surface of the valve seat, and the upper edge of the outlet flow channel forms an oblique line segment at an angle of 45 degrees, and the lower edge point E4 of the inner outlet is horizontal with the lower edge point E6 of the valve outlet, so that the inner outlet has a very long major axis a y ; Jet S 121The main flow line is blocked by the inner diameter of the valve chamber, passes through multiple turning corners D1, and finally flows into the inner outlet at a 45° angle and enters the upper half space of the outlet flow channel; the slow flow S 122 After being blocked by the inner diameter of the valve chamber, the fluid will enter the annular groove 90 degrees downward through multiple turning angles D2; the 45° conical diffusion C will result in a jet S 121 With slow flow S 122 A flow interference occurs in the valve chamber.

[0130] The requirements of restrictions 1, 2 and 4 are met. If the injection molding method is used, a slider needs to be manufactured for the inner outlet, which will cause cost concerns.

[0131] Problem 1: The inlet flow channel is a right-angle elbow with a smooth cross-sectional area, but the right-angle corner A brings additional head loss. The outlet flow channel is a horizontal straight pipe, and the bevel of the annular groove has an angle β; the corner B is 45 degrees, which greatly increases its curvature radius. Because the proximal end point E4 of the inner outlet is horizontal with the proximal end point E6 of the valve outlet, the slow flow S 122 After leaving the oblique angle β, a second turn D2 with an angle of β is required to flow horizontally into the inner outlet, so that the slow flow S 122 When crossing the valve seat outer diameter, a separated flow will be generated at the bottom of the valve seat outer diameter and an open stagnant area will be caused, which will also increase the head loss.

[0132] Problem 2: Jet S 121 The flow along the annular groove is inclined downward, with a 45-degree angle between it and the center line of the outlet, and at the corner E, it must make another 45-degree turn to flow horizontally; slow flow S 122 It will also flow obliquely downward along the annular groove and make a turn of about 30 degrees D to enter the lower half space of the inner outlet, but a recirculation zone will be generated at the near end point E4; the jet S 121 With slow flow S 122 The relatively small angle between them will not cause serious flow interference at the inner outlet, but will cause more head loss in the outlet flow channel due to mixing at the corner E.

[0133] From the above discussion, this reference case cannot meet the requirements of Problem 1 and Problem 2, nor can it meet the limitation 3. The head loss coefficient ξ is improved compared with the structure C4, but it still cannot meet the innovation goal.

[0134] Reference Case 5

[0135] In 1991, the US patent, US5002086A-Plastic control valve, Fig.1, met the requirements of restrictions 1 and 2. Its horizontal outlet flow channel still had a reflow zone at the upper edge of the outlet flow channel of the inner outlet, which caused the particles to condense and did not meet the requirements of restriction 3. The excessively high inner diameter ratio would greatly increase the volume and did not meet the requirements of restriction 4. The structure of this reference case is similar to structure C4. The outlet flow channel and the inlet flow channel are both horizontal straight pipes, with a cylindrical valve chamber space and a diaphragm with a valve plug. The diaphragm has good sealing performance and the radial clearance ratio of the cylindrical valve plug is About 0.53 does not produce stagnant space to cause particle condensation, and does not meet the inner diameter ratio of restriction 4 About 2.56, too high inner diameter ratio There will be too much volume. The inlet flow channel angle A is 90 degrees and the right angle will increase the head loss. The radial width is The ratio is about 0.44, which is very large. When the diffusion C is expanded, the streamline can ensure a reasonable curvature radius and make a suitable turn. When the valve is opened, the fluid will make a turn B of 45 degrees along the bottom of the valve plug and flow out in a conical diffusion C. The bottom of the annular groove is a downward inclined surface, and the inclined surface surrounds the outer diameter of the valve seat and crosses the bottom of the outer diameter of the valve seat to enter the inner outlet. This innovation can reduce the problem of the bottom of the annular groove and the inclined surface being too short to generate a recirculation area at the bottom of the outer diameter of the valve seat and generate particle condensation. The jet S 121 The main flow line flows out from the diffuser C at a 45-degree cone angle and needs to make a larger turning angle D1 with an angle of ≥ 90° to enter the annular groove downward. It is difficult to make a smooth ∩-shaped turn directly to enter the annular groove; slow flow S 122 The fluid will form two horizontally rotating and rolling streams and flow in a circle along the inner diameter of the valve chamber. After passing through the corner D2 with an angle of ≥90°, it can enter the annular groove downward and flow along the bottom of the inclined surface with an angle of β; the jet S 121 With slow flow S 122 Flow interference occurs in the valve chamber, and the angle of the turning angle D is too large to limit the jet S 121 of traffic.

[0136] Question 1: The inlet flow channel is a right-angle elbow with a smooth cross-sectional area, but the right-angle corner A is 90 degrees, which brings additional head loss, and the corner B is 45 degrees, which makes the jet S 121 With slow flow S 122 The first turning angle D1 and the turning angle D2 are both ≥90° to flow downward; the jet S 121 When the jet flows through the far end point E3, it needs to make a secondary turn D1 of 90° to enter the inner outlet. The outlet flow channel is a horizontal straight pipe with a turn angle E of 0°, but the jet S 121 The secondary turning angle D1 will cause a recirculation zone to form in the upper edge space of the outlet flow channel; the slow flow S 122At the inner outlet, a second turn D2 of about 45° is made before entering the outlet flow channel; slow flow S 122 When passing over the valve seat outer diameter, it flows along the downwardly inclined bottom and passes over the bottom of the valve seat outer diameter to enter the inner outlet without generating a separated flow and without an open stagnant area.

[0137] Problem 2: Jet S 121 The flow along the annular groove is inclined downward and there is a 90-degree angle between the center line of the outlet. A secondary turn D1 must be made with an angle of 90°, slow flow S 122 It will also flow obliquely downward along the annular groove, with an angle of about 45 degrees between it and the center line of the outlet, slow flow S 122 Make a secondary turn D2 of about 45°, and the jet S 121 With slow flow S 122 If the angle between them is too large, flow interference will occur at the inner outlet, increasing the pressure loss.

[0138] From the above discussion, this reference case cannot meet the requirements of problem one and problem two, and does not meet the requirements of restrictions three and four. For example, the head loss coefficient ξ of structure C4 still cannot meet the innovation goal. A similar reference case with similar structure C4, the 2023 US patent, US11585460B2-Diaphragm valve structure, is also a similar structure and meets the requirements of restrictions one, two and four. Since the inclined bottom is also directly connected to the inner outlet, it can also reduce the horizontal outlet flow channel of the confluence area. The inner diameter ratio meets the requirements of restriction four. Some improvements have been made to the right-angle part of the inlet flow channel, but there is still not much effect, and there is still a problem of particle condensation that refluxes at the upper edge of the outlet flow channel of the inner outlet.

[0139] Reference Case 6

[0140] 1991 Chinese patent, CN2083665U-Anti Corrosion Stop Valve, p.5, meets the requirements of limitation 1 and limitation 2, and the too low inner diameter ratio does not meet the requirements of limitation 4. The reference case structure is a metal casting valve with an anti-corrosion lining, similar to structure C3 with a cylindrical valve chamber space and a valve plug and a diaphragm, the diaphragm has good sealing performance and is barrel-shaped and has a radial clearance ratio with the inner diameter of the valve chamber. About 0.092, which will produce stagnant space and cause particles to condense. The radial clearance of the cylindrical valve plug is It is about 0.13, which does not produce stagnant space to cause particle condensation, and does not meet the inner diameter ratio of restriction 4. About 1.47, too low inner diameter ratio There will be a large head loss. The inlet flow channel area is smooth and has a turning angle A of 90 degrees and a circular arc flow channel. The bottom of the valve plug has a conical surface so that the turning angle B is about 45 degrees. There will be a diffusion C of the conical streamline, and the jet S121 The main flow line flows out from the diffuser C at a 45-degree cone angle and it is difficult to flow along the outlet center line of the outlet flow channel at a 60-degree angle downward, so that the jet S 121 It will enter the upper half of the inner outlet space with a larger curvature radius and flow along the upper edge of the outlet flow channel, slow flow S 122 The long cylindrical valve chamber space in the valve chamber rotates and rolls to make a corner D to enter the inner outlet.

[0141] Problem 1: The inlet flow channel has a smooth cross-sectional area and is a circular curved pipeline. The outlet flow channel is a horizontal outlet with a smooth cross-sectional area from the valve chamber oblique downward bend pipe. From corner B, diffusion C to corner D, they are all limited to too small inner diameter ratios, resulting in increased head loss and jet S 121 With slow flow S 122 Both require the flow of the conical diffuser C and are confined to the narrow valve chamber, which will cause flow interference between the two.

[0142] Problem 2: Jet S 121 After the corner D, it enters the upper half space of the inner outlet and flows along the upper edge of the outlet flow channel, while the slow flow S 122 The long cylindrical valve chamber space in the valve chamber rotates and rolls to make a corner D and enter the inner outlet, so that the jet S 121 With slow flow S 122 Flow interference occurs in the upper space of the inner outlet, causing head loss.

[0143] From the above discussion, this reference case cannot meet the requirements of Problem 1, Problem 2 and Limitation 3, Limitation 4. It will have a higher head loss coefficient ξ than structure C3 and still cannot meet the innovation goal.

[0144] Reference Case 7

[0145] In 1991, the US patent US5083750A-Membrane valve, Fig.1, met the requirements of limitation 1 and limitation 2, but the too high inner diameter ratio did not meet the requirement of limitation 4. The valve chamber of the reference case structure with a round and flat space is sealed by a diaphragm with a valve plug, and the valve plug has a radial clearance ratio of About 3.57, no stagnant space will be generated to cause particle condensation, too large inner diameter ratio About 4.88 does not meet the limit four, too high inner diameter ratio The inlet flow channel and the outlet flow channel can be installed on the plane of the partition at the same time with low head loss. The inlet flow channel and the outlet flow channel are both smooth arc flow channels with angles A and E both of 90 degrees. The bottom of the valve plug has a conical surface so that the angle B is about 45 degrees and there will be a conical streamline diffusion C; the jet S 121 The jet S flows out from the diffuser C at 45 degrees and then turns downward through multiple turns to enter the outlet flow channel.121 The main flow line will make a ∩-shaped turn to enter the inner outlet, but the streamlines of the remaining fan-shaped expansion parts need to flow in the horizontal direction of the circumference to enter the inner outlet. In this way, too many turns will result in a large head loss; slow flow S 122 It will flow into the oblate valve chamber along the remaining circumferential angles at a 45-degree conical streamline, slowing down S 122 The fluid is divided into two streams and rolls down along the inner diameter surface of the valve chamber in a horizontal circle to enter the inner outlet. Too many turns will also result in a large head loss, and too large an inner diameter ratio Slow flow that causes rotation and tumbling 122 The flow rate is reduced, and the corner area between the inner wall of the valve chamber and the partition becomes an open retention area, which does not meet the requirements of restriction three.

[0146] Question 1: Since the streamlines have large turns at corners A and B, the jet S 121 With slow flow S 122 The horizontal circular flow in the valve chamber will produce flow interference, and the corner B, diffusion C and corner D will not be smooth.

[0147] Problem 2: Jet S 121 The main flow line of the outlet makes a 45-degree cone upward spray at the corner B, then makes a ∩-shaped turn downward to enter the inner outlet. From the corner B to the inner outlet, a 135-degree turning angle is required. Finally, at the inner outlet, the included angle with the center line of the outlet is 0 degrees, and it will flow with the slow flow S of the horizontal circular flow. 122 Flow interference occurs at the inner outlet.

[0148] From the above discussion, this reference has a large inner diameter ratio It does not meet the innovation goal, and the flow interference in Questions 1 and 2 obviously cannot meet the requirements.

[0149] Reference Case 8

[0150] In 2004, the US patent US6672561B2-Piston diaphragm with integral seal met the requirements of restrictions 1, 2 and 3. The excessively high inner diameter ratio did not meet the requirements of restriction 4. The structure of this reference case is derived from structure C4, but the valve chamber of this reference case has a bowl-shaped space, and its outlet flow channel is an inclined downward flow channel, which can solve the particle condensation problem of the original structure C4 on the wall. It is sealed by a diaphragm with a valve plug, and the excessively large inner diameter ratio About 3.4 does not meet restriction four. The bowl-shaped valve chamber has enough flow space and will not produce stagnant space to cause particle condensation. The sealing surface of the valve seat is located at the horizontal plane at the bottom of the valve chamber. The inlet flow channel is of equal diameter and flows horizontally from one side of the valve body and then makes a right angle A of 90 degrees to enter the conical center hole upward. The outlet flow channel is inclined downward from the valve chamber at about 45 degrees and then makes a horizontal straight pipe to flow out from the other side. The inner outlet of the outlet flow channel is a conical pipeline and the lower edge of its opening is located at the horizontal plane at the bottom of the valve chamber. The cross-section of the entire inner outlet is a vertical long ellipse. The equal diameter horizontal pipeline of the outlet flow channel is connected to the conical pipeline. When the valve is opened, the fluid makes a turn of about 90 degrees at the center hole B to enter the bowl-shaped radial flow channel. The jet S 121 The jet S diffuses along the inner surface of the bowl and flows toward the inner outlet. 121 At the inner entrance, a turn D of about 45 degrees is made to enter the conical flow channel, and the jet S 121 After entering the outlet channel, it turns at an angle of about 45 degrees and flows out from the horizontal straight pipe, with a slow flow S 122 In the remaining circumferential directions, it flows into the valve chamber space along the inner surface of the bowl, and then spirally rolls along the inner surface of the bowl to make a horizontal circular flow, and finally converges to make a turn D of about 45 degrees and flows obliquely downward into the inner outlet, slowing down S 122 After entering the outlet flow channel, it makes a turn E of about 45 degrees and flows out from a horizontal straight pipe.

[0151] Question 1: Since corner A is a right angle with more head loss, the conical slope of the center hole will assist the bend of corner B at about 80 degrees to reduce the head loss. The flow of diffuser C along the bowl-shaped inner surface of the valve chamber is a flow with a high curvature radius, which will help the jet S 121 With slow flow S 122 The turning angle D, most jets S 121 It will enter the lower semi-elliptical space of the inner outlet along the horizontal plane, and the slow flow S 122 The two streams are divided into two streams, which spirally tumble on the bowl-shaped inner surface of the valve chamber, and then make a turn D at a 45-degree angle and flow downward into the upper semi-elliptical space of the inner outlet.

[0152] Problem 2: Jet S 121 With slow flow S 122 After turning at corner D, the jet S 121 The outlet centerline is at an angle of 45 degrees, slow flow S 122 The direction is parallel to the center line of the outlet, and the jet S 121 With slow flow S 122 Flow interference will occur in the conical flow passage of the inner outlet, and the head loss cannot be significantly reduced.

[0153] Based on the above discussion, this reference proposal cannot meet the requirements of Question 1 and Question 2, nor can it meet the requirement of Restriction 4.

[0154] Reference Case 9

[0155] The 2012 US patent, US2012056120A1-Diaphragm Valve, does not meet the requirements of restriction 1, but meets the requirements of restrictions 2 and 3. Due to the structure being different from the stop valve, the flow channel of the sealing weir body of this reference is designed to be an elongated ellipse, with its major axis a Z The length is also close to 2a0 to maintain the inlet flow channel area and the outlet flow channel area unchanged, so it can still meet the requirements of restriction four. The patent content of this reference case regarding restriction five does not disclose the product forming method, but the manufacturer does have injection molded products, as shown in reference document five, which are also suitable for casting but not for forging; the structure of this reference case is a weir valve or a weir valve. The sealing weir body has an oblong arc sealing surface on the Z axis, which causes the diaphragm to only be able to perform linear compression sealing in the Z axis direction, and cannot provide the circular sealing line of the circular hole with uniform force and uniform deformation, resulting in a decrease in the quality of high-reliability sealing and failing to meet the requirements of restriction one. On both sides of the sealing weir body, there are arc surfaces connecting the inlet flow channel and the outlet flow channel, and the lower edges of the two flow channels are directly connected horizontally at the weir body. The inlet flow channel and the outlet The flow channels are connected to the sealing weir body by a horizontal slant, and the cross-sectional areas of the two flow channels are designed to be equal. The curvature radius of the streamlines when the fluid flows is very reasonable, and a smooth flow channel is also made on the weir body, so only the corners A and E need to be considered. When the diaphragm is opened, an inwardly concave arc flow channel is formed at the weir body to fully meet the requirements of corners B, diffusion C, and corner D. The streamline turning of this part is also very smooth, and there is a very low head loss on the overall flow channel. Since this reference case is different from the stop valve, the fluid does not flow in the space of the valve chamber, that is, the fluid flows in the flow channel and the flow channel formed by the diaphragm without having to worry about the requirement of restriction four. In addition, this Changan guest case has a very smooth flow channel and each cross-section of the flow channel has the same area, so the lowest head loss coefficient ξ can be obtained, which fully meets the requirements of problems one and two.

[0156] Question 1: The valve inlet is circular and gradually slopes upward at the weir body to become a flat ellipse that is elongated in the Z-axis direction and reduced in height in the Y-axis direction. The flat ellipse of the weir body gradually slopes downward while shrinking the length of the Z-axis to the circular shape of the valve outlet. At this time, each cross-section of the flow channel maintains the same area, and it is very smooth from corner A, corner B, diffusion C, corner D to corner E.

[0157] Problem 2: Jet S 121 With slow flow S 122 All in the same flow channel, the jet S 121 The inlet flow channel will expand in a fan shape and begin to contract after passing through the flat elliptical part of the weir body, making the jet S 121Flow coaxially with the center line of the outlet; slow flow S 122 The inlet flow channel and the jet S 121 Make the same fan-shaped expansion but its position is in the jet S 121 The outer side of the weir also begins to shrink at the flat elliptical part passing through the weir, making the slow flow S 122 The flow is close to coaxial with the center line of the outlet, so the jet S 121 With slow flow S 122 Both the pump and its mixture have low head loss.

[0158] From the above discussion, this reference case cannot meet the requirements of restriction 1, but meets the requirements of restriction 2, restriction 3, and restriction 4. Moreover, the Cv value of the actual inner diameter of DN50 of reference file 5 is 116cmh, and the head loss coefficient ξ is 1.67, which is difficult to achieve for stop valves with complex angles B, diffusion C, and angle D. For example, the head loss coefficient ξ of structure C3 is 3.4, which is much higher than this reference case. However, in other companies' similar cases with weir body seat sealing, such as reference file 6, the same weir body valve structure cannot meet the requirements of restriction 1 and its head loss The loss coefficient ξ is as high as 4.47, which is a huge difference compared with the head loss coefficient ξ of 1.7 in reference file 5. The reason is that the cross-sectional area of ​​the flow channel of reference file 6 is reduced at the weir body, and the lower edge line of the inlet flow channel and the lower edge line of the outlet flow channel are not smooth and have too many turns, resulting in the streamline turning of corners B, diffusion C, and corner D at the sealing weir body. It is completely incomparable with reference file 5, and its head loss coefficient ξ is also higher than the value of structure C3. It can be seen that an existing structure is not sufficient to ensure that its head loss coefficient ξ can easily meet the demand.

[0159] From the analysis of the structures C1, C2, C3, and C4 in the reference documents and the above nine references, it can be seen that limitations 1, 2, 3, 4, and 5 all have partial solutions, but none of the references has a complete solution. For problem 1, the content has been disclosed separately on how to maintain a smooth flow path. For example, structure C3 has a smooth flow path but cannot meet problem 2 of reducing the jet S. 121 The problem of too large an angle α1 with the center line of the outlet also produces a jet S 121 With slow flow S 122There is a flow interference problem at the inner outlet, and the requirement of restriction three cannot be met. That is, except for reference case 9, none of the reference cases has a flow passage that meets the requirement of integrity. Reference case 9 is limited by the inability to meet the requirement of restriction one and is not the subject of this innovation. The structure disclosed in reference document 6 shows that it is not easy to achieve smooth streamlines in corner B, diffusion C, and corner D. In other words, these public countermeasures are all existing technologies that can be separately or individually cited, but it is not easy to implement them in the valve body flow passage as a whole and achieve the goal of low head loss coefficient ξ. Another key to the solution to problem 2 is to reduce the jet S 121 With slow flow S 122 The problem of too large angle α3 between the rated flow limits has not been solved by the current structure C3. In addition, the streamline angle α3 of structure C2 is 0 degrees, but its structure cannot meet both problems one and two at the same time, that is, the overall solution that meets limitations one, two, three, and four at the same time and also meets problems one and two is the key to truly achieving the goal of the head loss coefficient ξ; the overall solutions described above all require an innovative valve body flow channel structure, hereinafter referred to as structure C5, in order to meet the needs of innovation at the same time. In addition, different materials and processes must be described in the embodiments in order to meet the process provision requirements of limitation five. Summary of the invention

[0160] The valve body flow channel structure of the present invention, hereinafter referred to as structure C5, targets the head loss coefficient ξ, 1.7≤ξ≤3.0, and the comparison benchmark is d0=52.5mm.

[0161] Structure C5 is a transformation that makes good use of the advantages of structure C4 to avoid its disadvantages and pursues the low head loss coefficient ξ of reference document 5. There are three innovative countermeasures for structure C5:

[0162] By improving the inlet flow channel, the curved arc flow channel can completely avoid the recirculation area.

[0163] Second, improve the outlet flow channel. The curved arc flow channel can completely avoid the recirculation area.

[0164] The third is to improve the jet S 121 With slow flow S 122 The curved arc flow channel can completely avoid the recirculation zone; let the jet S 121 The flow direction has a lower angle α1 with the center line of the outlet, and the jet S 121 With slow flow S 122 There is a smaller angle α3 between the streamlines to reduce the flow interference at the inner outlet. The characteristics of structure C5 will be further described below.

[0165] Please refer to Figure 1A and Figure 1B, the flow channel structure, coordinate points and inlet centerline S1, radial centerline S of structure C5 12 , schematic diagram of the exit center line S2 and corner A, corner B, diffusion C, corner D, and corner E.

[0166] Please refer to Figure 1C Figure 1 shows the placement angle θ and rotation angle 2θ of structure C5, including θ1, θ2, θ 21 ,θ 22 , 2θ1, 2θ2, 2θ 21 , 2θ 22 Schematic diagrams from various angles.

[0167] The present invention will be described with reference to a stop valve with an inner diameter of 52.5 mm.

[0168] An improved valve body flow channel structure of a globe valve, structure C5, the valve body flow channel structure includes a valve chamber, an annular groove, a valve seat, a valve plug, a sealing surface, a valve inlet, an inlet flow channel, a center hole, a valve outlet, an outlet flow channel, an inner outlet, etc. The following sealing mechanism takes the valve plug and its diaphragm as an example.

[0169] The inner diameter of the valve chamber is d3, the outer diameter of the valve plug is d2, the outer diameter of the valve seat is d1, the valve inlet diameter is d0, and the valve outlet diameter is d0.

[0170] The center point P1 of the center hole has a height of LH1, the center point P3 of the inner outlet has a height of LH2, the sealing surface of the valve seat has a height of LH3, and the center point P DP ; The valve inlet has a center point P2, and the valve outlet has a center point P4.

[0171] A horizontal line XL1 passes through the center point P1 of the center hole, and the horizontal line XL1 intersects with the circumference of the center hole at two intersection points, the distal end point E1 and the proximal end point E2. The distal end point E1 is located at the valve inlet side, and the proximal end point E2 is located at the valve outlet side.

[0172] A tube axis XL2 (X-axis) passes horizontally through the center point P2 and the center point P4. The height marking of the present invention is based on the tube axis XL2 connecting the valve outlet and the valve inlet. The coordinate zero point of the Y-axis will have positive values ​​(>0), zero values ​​(=0) and negative values ​​(<0) when indicating the position relative to the tube axis XL2.

[0173] A vertical line YL1 passes through the center point P1 and intersects the tube axis XL2 at point P 11 .

[0174] A vertical line YL2 passes through the center point P4, and the vertical line YL2 intersects the valve outlet circumference at two intersection points, the distal end point E5 and the proximal end point E6. The height of the distal end point E5 is The height of the proximal end point E6 is The proximal end point E6 is the lowest point of the outlet flow channel.

[0175] A vertical line YL3 passes through the center point P3 of the inner outlet and intersects the tube axis XL2 at point P 31 , and the vertical line YL3 intersects with the inner outlet circle at two intersection points, the distal end point E3 and the proximal end point E4, the height of the distal end point E3 is LH4 and the height of the proximal end point E4 is LH5.

[0176] A vertical line YL4 is established through the center point P2, and the vertical line YL4 intersects the valve inlet circumference at two intersection points, the distal end point E7 and the proximal end point E8. The height of the distal end point E7 is The height of the proximal point E8 is The proximal end point E8 is the lowest point of the inlet flow channel.

[0177] There is a horizontal distance L1 between the center point P1 and the center point P2. 11 P2=L1; there is a horizontal distance L2 between the center point P4 and the center point P1, P4P 11 =L2; there is a horizontal distance L between the center point P2 and the center point P4, P4P2=L=L1+L2.

[0178] There is a horizontal distance LL2 between the center point P4 and the center point P3.

[0179] The valve chamber is provided with the annular groove and the valve seat, and is provided with the valve plug, the valve shaft and the sealing surface, and the valve plug, the valve shaft and the sealing surface are concentric; the valve chamber is used to connect the inlet flow channel and the outlet flow channel; the inlet flow channel enters from the horizontal valve inlet and turns upward, and the center hole of the valve seat is provided at its outlet end; the inner outlet is provided on the inner diameter surface of the valve chamber to connect the outlet flow channel; the valve inlet and the valve outlet are respectively provided on both sides of the valve body; when the outlet flow channel is a straight pipe or a circular curved pipe in a downward inclined form, the inner outlet is a non-standard elliptical shape;

[0180] The annular groove is located at the inner diameter of the valve chamber 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 at the inlet flow channel side, and the lower side of the slope is located at the outlet flow channel side and connected to the proximal end point E4 of the inner outlet.

[0181] The valve seat is installed at the outlet end of the inlet flow channel and is provided with the sealing surface.

[0182] The valve plug is cylindrical and has a flat surface at the bottom. When the stop valve is closed, the valve plug is used to couple and seal with the sealing surface. When the valve is fully opened, the bottom surface of the valve plug and the sealing surface form a radial flow channel with an opening B1. Preferred embodiment, B1≈13.14mm.

[0183] The inlet flow channel includes the valve inlet, an inlet center line S1, the center hole, an upper edge line S 1a With the edge line S 1b The entrance center line S1 connects the center points P1 and P DP There is an angle γ1 with the center point P2 and with the vertical line YL1 at the center point P1; when the angle γ1≠0°, the center hole will be a non-standard elliptical hole with a major axis a in the X-axis direction. x , a x ≥d0,a x =E1E2, E1P1≥P1E2; when the angle γ1=0°, the center hole will be a circular hole with a diameter of d0; and has a short axis b in the Z-axis direction. z , b z = d0. The upper edge line S 1a Connecting the distal end point E1 and the distal end point E7, the lower edge line S 1b The proximal end point E2 and the proximal end point E8 are connected.

[0184] The radial flow channel includes a radial center line S 12 , the opening B1, when the valve plug is open, the bottom surface of the valve plug and the sealing surface form the radial flow channel. The opening B1, the radial flow channel is a radial flow channel surrounding the center hole, the height of the radial flow channel is LH6, LH6 = B1 + LH3. Radial centerline S 12 , connecting the center point P1 and the center point P3; it flows out from the center point P1 in a radial manner in different directions and finally connects to the center point P3.

[0185] The outlet flow channel includes the inner outlet, the valve outlet, an outlet center line S2, an upper edge line S 2a With the edge line S 2b The outlet center line S2 connects the center point P3 and the center point P4, and has an angle γ2 with the vertical line YL3 at the center point P3, 0°≤γ2<90°. The inner outlet is a non-standard elliptical hole with a major axis a in the Y-axis direction. y , a y ≥d0,a y =E3E4, E3P3≥P3E4, with a short axis b in the Z direction z , b z = d0; when the angle γ2 = 90°, the outlet flow channel is a horizontal straight pipe, a y = d0. The upper edge line S 2a Connecting the distal end point E3 and the distal end point E5, the lower edge line S 2bConnect the proximal end point E4 and the proximal end point E6. The distal end point E3 has a height difference H1 relative to the sealing surface, LH4-LH3=H1, when the distal end point E3 is higher than the sealing surface, H1≥0, otherwise H1≤0; the inner outlet center point P3 has a height difference H3 relative to the sealing surface, LH2-LH3=H3, when the P3 point is higher than the sealing surface, H3≥0, otherwise H3≤0.

[0186] A radial clearance B3 is located between the outer diameter d2 of the valve plug and the inner diameter d3 of the valve chamber, B3 = (d3-d2) / 2, An annular space B2 is between the outer diameter d1 of the valve seat and the inner diameter d3 of the valve chamber, B2 = (d3-d1) / 2, Inner diameter ratio The ratio of the inner diameter d3 of the valve chamber to the inlet diameter d0 of the valve is:

[0187] The following will be based on the inlet centerline S1, the radial centerline S 12 The three center lines including the outlet center line S2 are used to represent the streamlines, and the description of these turning angles is limited to the basis of the inferred geometric shapes. Further description will be obtained using complex 3D-CFD calculations.

[0188] The inlet center line S1 can be a single line segment or a combination of several line segments, and the types of line segments include: arc curve, vertical line segment, oblique line segment, horizontal line segment, wherein the vertical line segment is coaxial with the vertical line YL1, the horizontal line segment is coaxial with the pipe axis XL2, and the turning angle A is the turning angle of the inlet center line S1 from the valve inlet to the center hole.

[0189] The radial center line S 12 After the fluid flows out of the center hole, all streamlines will flow out in different directions in a radial manner and enter the radial flow channel. The turning angle B is from the inlet center line S1 to the radial center line S 12 All streamlines will diffuse along the radial flow channel C and will flow toward the inner outlet after making several turns limited by the inner diameter of the valve chamber. 12 The flow rate of the fluid in diffusion C slows down after turning corner B because the area of ​​the radial flow channel increases, but when it flows toward the inner outlet after several turns, it accelerates because the area decreases; the radial centerline S 12 Affected by the relative position between the radial flow channel and the inner outlet, it can be a straight line or an arc line, or a multiple-bend arc line.

[0190] The radial center line S 12 Since the fluid is driven by the pressure difference between the valve inlet and the valve outlet, the radial center line S of the diffuser C 12 Can be divided into jet S121 With slow flow S 122 The dense streamlines that are subjected to the high pressure gradient are the jets S 121 The low-density streamline with higher flow velocity and low pressure gradient is a slow flow. 122 Its flow velocity is slightly lower; the streamlines of the diffusion C flow will fan out in the circumferential direction and be affected by the angle B. The jet S 121 will fan out toward the inner outlet, and the slow flow S 122 The fan-shaped expansion will be performed at a circular angle other than the fan-shaped expansion angle of the jet; some jets S 121 will flow directly into the inner outlet, and the remaining jet S 121 With slow flow S 122 The valve will be divided into two streams in the valve chamber, tumbling along the inner diameter and entering the inner outlet. 12 , the jet S of the radial flow channel 121 With slow flow S 122 The fluid in the annular space B2 of the radial gap B3 will be induced to flow in two vortices, and the jet S 121 With slow flow S 122 The shear force of the flow will generate thrust for the two vortex flows and diffuse them and finally flow into the inner outlet. In most cases, the two vortex flows in the annular space B2 will not cause particle condensation problems. When the width of the radial gap B6 is too small or there is an inner concave space, there will be particle condensation problems. The radial centerline S 12 , jet S 121 With slow flow S 122 Before flowing into the inner outlet, they will make a turn D and a jet S 121 The corner is D1, the slow flow is S 122 is the turning angle D2, when the jet S 121 When passing through the annular space B2, the jet S 121 The α1 angle will begin to turn and will be further reduced when entering the inner exit, which also means that the angle of the turning angle D1 is reduced.

[0191] The outlet centerline S2 can be a single line segment or a combination of several line segments, and the line segment types include: arc curve, oblique line segment, horizontal line segment, etc., wherein the horizontal line segment is coaxial with the tube axis XL2. The outlet centerline S2, the turning angle D is the radial centerline S 12 The fluid turns at the outlet center line S2, and then flows out of the valve outlet after making a turn E in the inner outlet and the outlet flow channel.

[0192] The following will focus on the inner diameter ratio Under the conditions of; further explanation is given with different embodiments of the features of the present invention.

[0193] First embodiment

[0194] Please refer to Figures 1A to 1C , Figure 2A , Structure C5 is a schematic diagram of the flow channel structure and dimensions of the first embodiment. The inlet centerline S1 is composed of a horizontal line segment and a circular arc curve, and the outlet centerline S2 is composed of a horizontal line segment and a circular arc curve. The inlet flow channel starts from the circumference of the valve inlet and goes along the inlet centerline S1 to the circular center hole with a diameter of d0. A 3D inner diameter surface diagram of the inlet flow channel is made, and its cross section has an upper edge line S 1a With the lower edge line S 1b .

[0195] The technical features of the present invention include:

[0196] The inlet center line S1 has a straight line segment and a circular arc curve; a tangent point P is taken on the tube axis XL2 12 The arc curve has one end point as the center point P1 and another end point as the tangent point P 12 The arc curve is tangent to the tube axis XL2 at the tangent point P 12 , the arc curve has a horizontal distance L 11 =P 11 P 12 , one end of the straight line segment is the tangent point P 12 The other end point is the center point P2, P 12 Horizontal distance of P2 = L1-L 11 ; Through point P 12 Draw a vertical line YL6 and take a point P0 on the vertical line YL6 so that the line segment P0P 12 is the same length as line segment P0P1, while line segment P0P 12 The angle 2θ1 between the line segment P0P1 is equal to the rotation angle A, and the placement angle θ1 is equal to the line segment P1P 12 and obtain the angle γ1 between the arc curve and the vertical line YL1 at the center point P1 of the center hole, γ1 = 90°-2θ1.

[0197] When the angle γ1≠0°, the center hole is corrected from a non-standard long elliptical hole to a circular hole with a diameter of d0. The original major axis a x , a x =The length of E1E2 will be reduced to d0 by taking a far end point on the major axis. Replace the distal point E1 with a proximal point on the long axis Replace the proximal point E2, Long axis a x Length reduction ratio

[0198] The angle of the rotation angle A is 2θ1,55。 ≤2θ1≤105 。 .

[0199] Long axis a x Length reduction ratio

[0200] Partial jet S 121 will flow along the upper half space of the annular groove, while the slow flow S 122 It will flow along the slope in the lower half space of the annular groove, and the jet S 121 With slow flow S 122 The key to stratified flow is the upper edge line S of the outlet flow channel. 2a The angle of rotation E is 2θ 21 , 30°≤2θ 21 ≤90°, slow flow S 122 It will flow into the lower half of the annular groove, and the jet S 121 The distal end point E3 has a height LH4, the height difference between the distal end point E3 and the sealing surface is H1, the proximal end point E4 has a height LH5, and the proximal end point E4 is connected to the bottom of the inclined surface of the annular groove. Line segment E3E4 is the long axis a of the inner outlet in the Y-axis direction. y , a y =E3E4.

[0201] The outlet center line S2 has a straight line segment and an arc curve; a tangent point P is taken on the tube axis XL2 34 One end point of the arc curve is the center point P3 and the other end point is the tangent point P 34 The arc curve is tangent to the tube axis XL2 at the tangent point P 34 , the arc curve has a horizontal distance LL 21 =P 31 P 34 , one end of the straight line segment is the tangent point P 34 The other end point is the center point P4, P 34 Horizontal distance of P4 = LL2-LL 21 ; Through point P 34 Draw a vertical line YL5 and take a point P5 on the vertical line YL5 so that the line segment P5P 34 is the same length as line segment P5P3, while line segment P5P 34 The angle 2θ2 between the line segment P5P3 is equal to the rotation angle E, and the placement angle θ2 is equal to the line segment P3P 34 The horizontal angle between the arc curve and the vertical line YL3 is obtained at the center point P3, and γ2 = 90°-2θ2.

[0202] The outlet flow channel maintains a cross-sectional area of ​​equal diameter, and its upper edge line S 2a , lower edge line S 2b The three arc curves are parallel to each other and have a common center point P5. The inner outlet is a non-standard long ellipse. The major axis a of the non-standard long ellipse is y =E3E4, E3P3>P3E4, the minor axis b of the non-standard long ellipse z =d0.

[0203] The upper edge line S 2a It will intersect with the vertical line YL5 at a tangent point E 35 , tangent point E 35 The height of line segment P5E is d0 / 2. 35 The angle between the line segment P5E3 and the line segment P5E3 is 2θ 21 , and obtain the angle γ between the arc curve and the vertical line YL3 at the far end point E3 21 , γ 21 =90°-2θ 21 , when 2θ 21 When it is equal to 90 degrees, it means that the inner outlet flow channel has the longest major axis a y ; Through the upper edge line S 2a The height value LH4 of the far end point E3 can be obtained. 21 .

[0204] When the height difference ratio is H1 / d0, H1 / d0≤0.5, the height of the far end point E3 has no significant effect on reducing the head loss, while the major axis ratio a y The larger / d0 is, the lower the head loss can be; when 2θ 21 When it is equal to 90 degrees, it means that the inner outlet has the longest major axis a y , same LL 21 The longer it is, the longer the major axis a y The longer it is, the larger the volume of the valve body will be.

[0205] Due to the jet S 121 The radial flow channel flows horizontally, and the valve opening B1 has a height LH6, LH6≈LH3+B1, which can correspond to the major axis a y There is a virtual pair of points Its height is similar to that of LH6. The height difference with the valve seat sealing surface is And you can get a placement angle Equal to line segment The horizontal angle of the line segment The new long axis Line segment The angle with the horizontal line is the installation angle in Because part of the jet S 121 will directly enter the inner outlet from the radial flow channel, and the angle of placement Used to describe the jet S that flows directly into the inner outlet 121 The turning angle D is more appropriate because the jet S 121 When passing through the annular space, the streamline begins to bend so as to flow smoothly into the inner outlet. The above description is for the jet S that directly enters the inner outlet. 121 The α1 angle can be understood more correctly and the actual α1 angle can be lowered.

[0206] The lower edge line S 2b It will intersect with the vertical line YL5 at a tangent point E 46 , tangent point E 46 The height is Line segment P5E 46 The angle between the line segment P5E4 and the line segment P5E4 is 2θ 22 , and obtain the lower edge line S at the proximal end point E4 2b Angle γ with vertical line YL3 22 , γ 22 =90°-2θ 22 , through the lower edge line S 2b The height value LH5 of the near end point E4 can be obtained. 22 .

[0207] Outlet flow channel upper edge line S 2a The angle of rotation E is 2θ 21 , 30°≤2θ 21 ≤90°; there is a height difference H1 between the far end point E3 and the valve seat, The proximal end point E4 is connected to the bottom of the inclined surface and the height LH5 of the proximal end point E4 is -0.4≤LH5 / d0≤0.4; the inclined angle β of the inclined surface of the annular groove is approximately equal to the included angle θ 22 , 8°≤β≤20°.

[0208] When necessary, in order to further enhance the strength of the valve seat, a vertical rib is added to the outer diameter surface of the valve seat. The vertical rib is located on the inner outlet side, and its lower part is connected to the bottom of the annular groove. The two side surfaces of the vertical rib are two vertical arc surfaces, and one side edge of the two arc surfaces on both sides is tangent to the outer diameter surface of the valve seat to form a wide bottom side, and the other side edges of the two arc surfaces on both sides intersect to form an end with a small arc angle. The vertical rib can also guide the streamlines from the two flows in the annular groove to the inner outlet.

[0209] Preferred embodiment A, taking 2θ 21 The range of the following parameters when equal to 90 degrees:

[0210] When the horizontal length LL of the outlet center line S2 21 , 2.0 ≥ LL 21 / d0≥0.5, the major axis a y Compared with the diameter d0,

[0211] θ2 and θ 22 The angle range is as follows: the turning angle E of the outlet flow channel is 2θ2,30 。 ≤2θ2≤74°, the angle 2θ of the turning angle E of the lower edge line S2b of the outlet flow channel 22 , 14°≤2θ 22 ≤54°.

[0212] Preferred embodiment B, taking 2θ 21 The range of the following parameters when it is equal to 30 degrees:

[0213] When the horizontal length LL of the outlet center line S2 21 , 2.0 ≥ LL 21 / d0≥0.5, the major axis a y Compared with the diameter d0,

[0214] θ2 and θ 22 The angle range is as follows: the turning angle E of the outlet flow channel is 2θ2, 20 。 ≤2θ2≤28°, the angle 2θ of the turning angle E of the lower edge line S2b of the outlet flow channel 22 , 15 。 ≤2θ 22 ≤26°.

[0215] Second embodiment

[0216] Please refer to Figures 1A to 1C , Figure 2B , Structure C5 is a schematic diagram of the flow channel structure and dimensions of the second embodiment, the inlet center line S1 is composed of a horizontal line segment and a circular arc curve, and the outlet center line S2 is composed of a horizontal line segment and an oblique line segment.

[0217] The technical features of the present invention include:

[0218] According to the first embodiment, the outlet flow channel is constructed by the embodiment and the inner outlet is maintained as a non-standard ellipse, but the outlet center line S2 and the upper edge line S 2a , the lower edge line S 2b Change to a combination of straight line segments; line segment P3P 34 Connect the center point P3 and the tangent point P 34 , line segment E3E 35 Connect the far end point E3 and the tangent point E 35, line segment E4E 46 Connect the proximal end point E4 and the tangent point E 46 ; From the circumference of the non-standard ellipse of the inner outlet as the starting point, along the outlet center line S2 to the circular valve outlet, make a 3D inner diameter surface diagram of the outlet flow channel, and its section has an upper edge line S 2a With the lower edge line S 2b .

[0219] Through point P 34 Draw a vertical line YL5 and take a point P5 on the vertical line YL5 so that the line segment P5P 34 is the same length as line segment P5P3, while line segment P5P 34 The angle 2θ2 between the line segment P5P3 is equal to the line segment P3P 34 The rotation angle E, the placement angle θ2 is equal to the line segment P3P 34 Horizontal angle.

[0220] The line segment P3P 34 The installation angle is θ2 and the rotation angle D of the center point P3 is θ2,

[0221] The line segment E3E 35 The installation angle θ 21 And the rotation angle D of the far end point E3 is θ 21 ,

[0222] The line segment E4E 46 The installation angle θ 22 And the angle D of the near end point E4 is θ 22 ,

[0223] The outlet center line S2 is at the tangent point P 34 Make a turn at angle E, angle E = θ2.

[0224] The upper edge line S 2a At the tangent point E 35 Make a turn at angle E, angle E = θ 21 .

[0225] The lower edge line S 2b At the tangent point E 46 Make a turn at angle E, angle E = θ 22 .

[0226] The rotation angle D of the far end point E3 = θ 21 , 14°≤θ 21 ≤45°.

[0227] Tangent point E 35 The rotation angle E = θ 21 , 14°≤θ21 ≤45°.

[0228] The rotation angle D of the near end point E4 = θ 22 , 7°≤θ 22 ≤20°.

[0229] Tangent point E 46 The rotation angle E = θ 22 , 7°≤θ 22 ≤20°.

[0230] Third embodiment

[0231] Please refer to Figures 1A to 1C , Figure 2C , Structure C5 is a schematic diagram of the flow channel structure and dimensions of the third embodiment, the inlet center line S1 is composed of a horizontal line segment and a circular arc curve, and the outlet center line S2 is composed of a horizontal line segment and an oblique line segment.

[0232] The technical features of the present invention include:

[0233] According to the first embodiment and the second embodiment, the outlet flow channel is constructed by the embodiment and the inner outlet is maintained as a non-standard ellipse, and the shape of the inner outlet is further modified from the original non-standard ellipse to a rectangle, and the non-standard ellipse is inscribed in the rectangle, and the two have the same major axis a y With short axis b z and have the same distal end point E3 and proximal end point E4, the four right angles of the rectangle are modified into four small rounded corners; the outlet center line S2 of the outlet flow channel, the upper edge line S 2a , the lower edge line S 2b Change to a combination of straight line segments; line segment P3P 34 Connect the center point P3 and the tangent point P 34 , line segment E3E 35 Connect the far end point E3 and the tangent point E 35 , line segment E4E 46 Connect the proximal end point E4 and the tangent point E 46 ; From the circumference of the inner rectangular outlet as the starting point along the outlet center line S2 to the circular valve outlet, a 3D inner diameter surface diagram of the outlet flow channel is made, and its cross section has an upper edge line S 2a With the lower edge line S 2b .

[0234] Through point P 34 Draw a vertical line YL5 and take a point P5 on the vertical line YL5 so that the line segment P5P 34 is the same length as line segment P5P3, while line segment P5P 34 The angle 2θ2 between the line segment P5P3 is equal to the line segment P3P 34The rotation angle E, the placement angle θ2 is equal to the line segment P3P 34 Horizontal angle.

[0235] The line segment P3P 34 The installation angle is θ2 and the rotation angle D of the center point P3 is θ2,

[0236] The line segment E3E 35 The installation angle θ 21 And the rotation angle D of the far end point E3 is θ 21 ,

[0237] The line segment E4E 46 The installation angle θ 22 And the angle D of the near end point E4 is θ 22 ,

[0238] The outlet center line S2 is at the tangent point P 34 Make a turn at angle E, angle E = θ2.

[0239] The upper edge line S 2a At the tangent point E 35 Make a turn at angle E, angle E = θ 21 .

[0240] The lower edge line S 2b At the tangent point E 46 Make a turn at angle E, angle E = θ 22 .

[0241] The rotation angle D of the far end point E3 = θ 21 , 14°≤θ 21 ≤45°.

[0242] Tangent point E 35 The rotation angle E = θ 21 , 14°≤θ 21 ≤45°.

[0243] The rotation angle D of the near end point E4 = θ 22 , 7°≤θ 22 ≤20°.

[0244] Tangent point E 46 The rotation angle E = θ 22 , 7°≤θ 22 ≤20°.

[0245] Fourth embodiment

[0246] Please refer to Figures 1A to 1C , Figure 2D, Structure C5 is a schematic diagram of the flow channel structure and dimensions of the fourth embodiment, the inlet center line S1 is composed of a horizontal line segment and a circular arc curve, and the outlet center line S2 is composed of a horizontal line segment and a circular arc curve.

[0247] The technical features of the present invention include:

[0248] According to the first embodiment, the outlet flow channel is constructed with the embodiment and the inner outlet is maintained as a non-standard ellipse. When the distal end point E3 is higher than the sealing surface of the valve seat and the height of the distal end point E3 needs to be adjusted, a circular arc S3 can be made tangent to the upper edge line S 2a and intersect at the new far end point Remote Point There is a height difference with the valve seat The line segment The new long axis A tangent surface SS is made along the arc S3 and the inner diameter surface of the outlet flow channel. The angle between the arc S3 and the vertical line YL3 A larger angle, Make part of the jet S 121 When directly entering the inner outlet, the flow can flow along the curved surface SS and reduce the angle of the turning angle D1; this item is for the upper edge line S of the outlet flow channel 2a The purpose of the modification is to obtain a suitable height of the valve chamber while still maintaining the high flow performance of the flow channel.

[0249] Remote Point Angle of corner D

[0250] New major axis of the ellipse

[0251] Fifth embodiment

[0252] Please refer to Figures 1A to 1C , Figure 2E FIG. 3 is a schematic diagram of the flow channel structure and dimensions of the fifth embodiment of structure C5, wherein the inlet center line S1 is composed of a horizontal line segment and a circular arc curve, and the outlet center line S2 is composed of a horizontal line segment and a circular arc curve.

[0253] The technical features of the present invention include:

[0254] Please refer to the first embodiment, and use this embodiment to construct the inlet flow channel and the outlet flow channel. The inner diameter d3 of the valve chamber and the outer diameter d1 of the valve seat are eccentrically designed, so that the structure of the valve chamber is a hollow circular eccentric structure. The structure of the valve chamber is divided into a valve plug chamber with a diameter of 1.8d0 and an annular chamber with a diameter of 2.2d0. The center deviation between the valve plug chamber and the annular chamber is 0.2d0, and the height of the top of the annular chamber is LH7; the valve plug chamber and the valve seat are concentric and a vertical line YL1 passes through them. The valve plug chamber is used to accommodate the valve plug. 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 inner outlet side of the annular chamber is 1.3d0; the annular chamber accommodates the annular space and the annular groove, and the width B2 of the annular groove varies with the eccentric design and has a maximum width on the inner outlet side. There is a height difference H5 between the top of the annular chamber and the sealing surface of the valve seat, H5 = LH7-LH3, 0.6 ≥ H5 / d0 ≥ 0.25; due to the major axis a of the inner outlet y Greater than the center hole diameter d0, 2.2 ≥ a y / d0≥1.3; at this time, such a value can be obtained in drawing and calculation, but in practice, it must be modified according to the fifth embodiment to meet the requirements of the physical flow channel.

[0255] Since the height LH4 of the distal end point E3 may also be higher than the height LH7, LH4>LH7, in this case, the distal end point E3 needs to be at the long axis a y Find a new remote point And by the remote point Make an arc S3 tangent to the upper edge line S 2a , and ensure that the remote endpoint Height difference from the valve seat The line segment The new long axis A tangent surface SS is made along the arc S3 and is tangent to the inner diameter surface of the outlet flow channel. The angle between the arc S3 and the vertical line YL3 A larger angle, Remote Point Angle of corner D New major axis of the ellipse (The concave arc S3 and the tangent curved surface SS are formed in the same manner as in the fourth embodiment)

[0256] Sixth embodiment

[0257] According to the first embodiment, please refer to Figures 1A to 1C picture, Figure 2F, Structure C5 is a schematic diagram of the flow channel structure and dimensions of the sixth embodiment, the inlet center line S1 is composed of a horizontal line segment and a circular arc curve, and the outlet center line S2 is composed of a horizontal line segment and a circular arc curve.

[0258] The technical features of the present invention include:

[0259] According to the first embodiment, the inlet flow channel is constructed by the embodiment, and the outlet flow channel is constructed by the embodiment. The sealing surface of the valve seat is located outside the center hole. A conical tube coaxial with the vertical line YL1 is installed on the center hole and the conical tube has a center point P DP The height of the sealing surface of the valve seat is LH3, the height of the center hole is LH1, and the height h of the conical tube has a cone angle φ, LH3 = LH1 + h; the function of the conical tube is to provide a diffusion effect for the fluid and its inlet streamline S1, so that it can turn angle B more smoothly to enter the radial flow channel. This function can further reduce the head loss. Secondly, the conical tube increases the structural strength of the valve seat and improves the reliability of the seal.

[0260] The height of the conical tube h,

[0261] The cone angle φ of the conical tube is 15°≤φ≤60°.

[0262] The requirements for satisfying the restriction conditions in the above six embodiments are described in detail as follows:

[0263] Limitation 1: The valve seat provides a highly reliable seal. The angle 2θ1 of the angle A of the first to sixth embodiments of the structure C5 is 55°≤2θ1≤105°, which can provide a reliable valve seat strength. The height h of the conical tube of the sixth embodiment is The strength of the valve seat can be further improved. When necessary, the vertical ribs added to the outer diameter surface of the valve seat can further improve the strength of the valve seat to increase the reliability of the sealing performance.

[0264] Restriction 2: The inlet and outlet are in the same straight line, and the center point P2 of the valve inlet and the center point P4 of the valve outlet of the first embodiment to the sixth embodiment of the structure C5 pass through the pipe axis XL2.

[0265] Limitation three: The valve body cannot have cleanliness problems. The inlet flow channel and the outlet flow channel of the first embodiment, the second embodiment, the third embodiment, the fourth embodiment, the fifth embodiment, and the sixth embodiment of structure C5 are all smooth bends or inclined tube structures, and the valve chamber does not have a closed retention area, an open retention area, or a recirculation area, and there will be no problems such as particle condensation and liquid residue. The position of the inner outlet covers the radial flow channel plus the position of the distal end point E3 of the inner outlet, and the height of the proximal end point E4 is LH5, -0.4≤LH5 / d0<0.4, which can reduce the height of the oblique downward flow of the fluid so that the fluid flowing into the annular groove will generate a rotating flow in the outlet flow channel after entering the inner outlet, completely eliminating the recirculation area and there will be no problems such as particle condensation and liquid residue.

[0266] Limitation 4: The inner diameter ratio of the valve body is 1.75≤d3 / d0≤2.5. The inner diameter ratio of the best embodiment of structure C5 is 2.0, and there will be no problem of excessive volume. The valve chamber of the fifth embodiment adopts an eccentric design, and the inner diameter ratio of the annular chamber is 2.2 and the inner diameter ratio of the valve plug chamber is 1.8, and there will be no problem of excessive volume.

[0267] Limitation 5: The structure of the innovative flow channel of the valve body must meet various manufacturing methods and material selection. Embodiment 1, Embodiment 2, Embodiment 3, Embodiment 4, Embodiment 5, and Embodiment 6 of Structure C5 can all be manufactured using the metal casting method; Embodiment 1 can only be manufactured using the injection molding method if both the outlet centerline and the inlet centerline are single arcs, Embodiment 4 is also suitable for injection molding, Embodiment 5 is also suitable for injection molding as required, and Embodiment 6 is also suitable for injection molding.

[0268] Solutions have been proposed for the above six embodiments to solve the problems, and the solutions are described as follows:

[0269] The technical features of structure C5 are that the inlet streamline and the outlet streamline are both based on curved arc flow channels, the inlet centerline is an arc curve, the outlet centerline is an arc curve or a downward slanting straight line, and the height of the distal end point E3 is LH4 higher than the valve seat, and the height of the proximal end point E4 is LH5. Jet S 121 It will enter the upper half of the annular groove, slowing down the flow S 122 can flow into the lower half of the annular groove, and the jet S 121 With slow flow S 122 The stratified flow in the annular groove can maintain the maximum curvature radius between the inlet streamline, the radial streamline, and the outlet streamline, while avoiding the flow interference in the valve chamber and the flow interference in the inner outlet; such technical features make the streamline turning of the corner B, the diffusion C and the corner D smoother, while maintaining the minimum head loss coefficient ξ, 1.7≤ξ≤3.0, C v≥73.5.

[0270] Question 1: When the height difference ratio of the far point E3 is H1 / d0, H1 / d0 ≥ 0.5, the far point E3 and the corresponding point The space between the two is not an effective flow space and will also cause additional head loss. The larger the space, the new major axis The shorter it will be, the smaller the actual flow area of ​​the inner outlet will be.

[0271] Problem 1: New long axis or major axis ratio The larger the jet S 121 With slow flow S 122 The better the stratified flow in the annular groove, the less flow interference there is and the smaller the head loss is.

[0272] Question 1: Antipodal Point of Placement Corner The installation angle θ is less than or equal to the line segment E3E5 21 , placement angle Represents the jet S 121 Closer to the actual turning angle D, and the jet S 121 Will flow into the corresponding point of the inner exit The flow channel space between the center point P3, when the height difference is too large than H1 / d0, the new major axis or major axis ratio Reduce the jet flow S 121 A reduction in the radius of curvature will result in additional head loss.

[0273] Question 1: The second and third embodiments use straight-line flow passages to achieve the same effect. The fourth embodiment is a correction method when the position of the distal end point E3 is too high. The fifth embodiment uses an eccentric design for the valve chamber to 121 The streamline obtains a better curvature radius. The sixth embodiment adds the conical tube above the central hole to increase the diffusion function and reduce the jet S 121 The above embodiments can achieve the same effect regardless of the angle of the corner B.

[0274] Question 1: The jet flow S can be maintained from the inlet flow channel to the outlet flow channel 121 One of the technical features of the first embodiment of the structure C5, the preferred embodiment A, the upper edge line S of the outlet flow channel 2a The angle of rotation E is 2θ 21 , 2θ 21 =90°, the height of the distal end point E3 is LH4, LH4>LH3, the major axis ratio a y / d0,1.3≤ay / d0 ≤ 2.2, the area of this inner outlet can completely cover this radial flow channel and the upper half area of this inner outlet is larger than the lower half area. When the jet flow S 121 makes a fan-shaped expansion in this radial flow channel and then crosses this annular groove, it can flow obliquely downward to the upper half opening of this inner outlet, so that the streamline of the jet flow S 121 can maintain a larger radius of curvature when entering this inner outlet.

[0275] Problem 1: The streamline of the jet flow S can be maintained smoothly from this inlet flow channel to this outlet flow channel 121 with good radius of curvature; one of the technical features of the first embodiment of Structure C5, preferred embodiment B, the angle 2θ of the turning angle E of the upper edge line S of the outlet flow channel 2a is 21 2θ 21 = 30°, the height of the distal point E3 is LH4, LH4 < LH3, the major axis ratio a y / d0, 1.06 ≤ a y / d0 ≤ 1.12, the jet flow S 121 makes a first 90-degree turning angle D1 downward from the diffusion C, and then makes a secondary turning angle D1 with an angle of 60° at the distal point E3. The angle 2θ of the turning angle E of the lower edge line S of the outlet flow channel 2b is 22 14° ≤ 2θ 22 ≤ 26°, when the slow flow S 122 flows on this inclined surface of this annular groove, the angle when making a secondary turning angle D2 and flowing into this proximal point E4 is greatly reduced, so that the streamline of the jet flow S 121 can avoid the streamline of the slow flow S 122 and can maintain the stratified flow in this annular groove and reduce the flow interference at this inner outlet.

[0276] Problem 1: The height of this proximal point E4 is LH5, -0.4 ≤ LH5 / d0 < 0.4, and the turning angle D at this proximal point E4 is close to the inclined surface angle of this annular groove. When the slow flow S 122 makes a fan-shaped expansion in this radial flow channel, it will not interfere with the jet flow S 121 and enables more slow flow S 122 to be guided by this inclined surface of this annular groove to make more fluid flow to the lower half opening of this inner outlet.

[0277] Problem 1: The streamline of the jet flow S can be maintained smoothly from this inlet flow channel to this outlet flow channel 121 with good radius of curvature; the inlet flow channel of Structure C5 is a smooth flow channel and the angle 2θ1 of the turning angle A is 55° ≤ 2θ1 ≤ 105°, which can keep the inlet streamline smooth and make the turning angle B smoother when the fluid enters this radial flow channel after passing through the turning angle B and diffuse in this valve chamber.

[0278] Question 1: Example 5 The horizontal distance between the center point P1 of the valve seat on the inner outlet side and the inner diameter of the annular chamber is 1.3d0, which allows the streamline to have a larger turning space when entering the inner outlet.

[0279] Question 1: Example 6 The height h of the conical hole has a cone angle φ which has a diffusion function, which can provide the fluid with an opportunity to diffuse and increase the turning curvature radius when flowing out of the center hole, thereby reducing the angle of the turning angle B and reducing the head loss coefficient ξ.

[0280] Question 1: Example 1 and Example 2 illustrate that the turning angle of the outlet flow channel is 2θ2; the flow channel of Example 1 is a smoothly curved flow channel, and its turning angle D is 2θ2, which will cause some loss when the fluid enters the inner outlet, but its turning angle E is also 2θ2 and will not cause additional losses and has a low head loss coefficient ξ; the turning angle D of Example 2 is θ2 to reduce the loss of the jet at entry, and the outlet flow channel of Example 2 has an obtuse turn, and the angle θ2 of its turning angle E will bring a slightly higher head loss coefficient ξ, while the overall outlet flow channel can still maintain a low head loss coefficient ξ.

[0281] Question 1: The center hole is reduced from a non-standard long elliptical hole to a circular hole with a diameter of d0 and a major axis a x The length reduction ratio, The actual cross-sectional area of ​​the inlet flow channel at the center hole can be maintained without excessive reduction, which would lead to an increase in the lift loss coefficient ξ. There is enough space to maintain a reasonable distribution of streamlines in the flow channel, and a better turning angle B can be maintained when the fluid flows out of the center hole.

[0282] Problem 2: Reduce the jet S 121 The angle between the direction and the outlet centerline S2, the jet S 121 The flow will diffuse C to make the streamlines fan-shaped. The fan-shaped streamlines are distributed on the inner outlet side. The jet S 121 It will flow into the annular groove and then flow obliquely downward toward the inner outlet. The jet S 121 The oblique downward flow causes the angle α1 with the outlet centerline S2 to be greatly reduced, rather than the original high angle or 90 degrees at the far end point E3, α1 = (90-γ2).

[0283] Problem 2: Reduce the jet S 121 The angle between the direction and the axis XL2 of the outlet flow channel, in the preferred embodiment A of the first embodiment, the height LH4 of the distal end point E3 of the inner outlet is higher than the height LH3 of the sealing surface of the valve seat, LH4>LH3, and the major axis a y Ratio to diameter d0, 1.3≤a y / d0≤2.2, so that the jet S 121When diffusing C can flow obliquely downward with sufficient space when crossing the annular groove in the radial flow channel, the included angle α1 with the outlet center line S2 can be reduced to enter the upper half area of the inner outlet, thereby significantly reducing the head loss coefficient ξ.

[0284] Problem 2: Reduce the jet S 121 The included angle between the direction and the axis line XL2 of the outlet flow channel. In the preferred embodiment B of the first embodiment, the height LH4 of the distal point E3 of the inner outlet is lower than the height LH3 of the sealing surface of the valve seat, LH4 < LH3, major axis a y Compared with the diameter d0, 1.06 ≤ a y / d0 ≤ 1.12, so that the jet S 121 Makes a first 90-degree turn D1 downward when diffusing C crosses the annular groove, and will make a second turn D1 in advance when passing through the distal point E3, and its angle is γ 21 , 0° ≤ γ 21 ≤ 60°, thereby reducing the included angle α1 between the jet S 121 And the outlet center line S2, thereby reducing the head loss coefficient ξ.

[0285] Problem 2: Reduce the slow flow S 122 The included angle α2 between the streamline of and the outlet center line S2 of the inner outlet. The streamline of the slow flow S 122 Will cross the valve seat into the annular groove in the circumferential direction outside the fan-shaped expansion of the jet S 121 . In the first embodiment, the height of the near point E4 is LH5, And the near point E4 is connected to the bottom of the annular groove with an inclined bottom, and the included angle β of the inclined surface is relatively close to the angle difference of the turn D of the near point E4. When the slow flow S 122 Makes an oblique downward turn along the annular groove at a 3D solid angle and enters the inner outlet, the included angle α2 will also be reduced, and the streamline of the slow flow S 122 Obtains a larger curvature radius.

[0286] Problem 2: Can maintain a small included angle α3 between the streamlines of the jet S 121 And the slow flow S 122 . In the jet S of the first embodiment 121 After the fan-shaped expansion and then crossing the annular groove, most of the streamlines of the jet S 121 Flow to the upper half area of the inner outlet; while the slow flow S 122 Makes a fan-shaped expansion in the circumferential direction outside the fan-shaped expansion of the jet S and flows into the annular groove. Most of the streamlines of the slow flow S 121 Flow along the inclined surface of the annular groove and enter the lower half area of the inner outlet; while the jet S 122 And the slow flow S 121 And the slow flow S 122There is no intense interference before entering the inner exit, that is, the jet S 121 With slow flow S 122 The small angle α3 between the streamlines is maintained at a relatively small state and no flow interference phenomenon occurs at the inner outlet; however, the jet S 121 With slow flow S 122 After entering the inner outlet, the flow passage rotates relative to each other, and such a rotating flow can greatly reduce the backflow in the outlet flow passage and the generation of particle condensation.

[0287] The above discussion of structure C5 is that the distal end point E3 of the inner outlet is higher than the height difference H1 of the sealing mask, and the height of the proximal end point E4 is LH5, -0.4≤LH5 / d0<0.4, so that the inner outlet E4E 46 The line segment has an angle of placement θ 22 , 7°≤θ 22 ≤20°, slow flow S 122 The corner D2 entering the inner outlet can be greatly reduced; that is, structure C5 can achieve the innovative goal, the head loss coefficient ξ, ξ≤3.0, and the comparison benchmark is d0=52.5mm shall prevail. BRIEF DESCRIPTION OF THE DRAWINGS

[0288] Figure 1A Schematic diagram of the flow channel structure and coordinate points of structure C5.

[0289] Figure 1B for Figure 1A IB-IB cross-sectional view.

[0290] Figure 1C are the placement angle θ and rotation angle 2θ of structure C5, θ1, θ2, θ 21 ,θ 22 , 2θ1, 2θ2, 2θ 21 , 2θ 22 And streamline S1, streamline S 12 , schematic diagram of streamline S2 and corner A, corner B, diffusion C, corner D, and corner E.

[0291] Figure 2A It is a schematic diagram of the flow channel structure of the first embodiment of structure C5.

[0292] Figure 2B It is a schematic diagram related to the flow channel of the second embodiment of structure C5.

[0293] Figure 2C It is a schematic diagram of the flow channel structure of the third embodiment of structure C5.

[0294] Figure 2DIt is a schematic diagram of the flow channel structure of the fourth embodiment of structure C5.

[0295] Figure 2E It is a schematic diagram of the flow channel structure of the fifth embodiment of structure C5.

[0296] Figure 2F It is a schematic diagram of the flow channel structure of the sixth embodiment of structure C5.

[0297] Figure 3A This is the cross-sectional structure and streamline distribution diagram of the existing structure C4.

[0298] Figure 3B It is a top view of the streamline fan-shaped expansion of the flow chamber of the existing structure C4.

[0299] Figure 3C A 45-degree view of the flow channel of the existing structure C4.

[0300] Figure 4A This is an improvement of the existing structure C4 - a cross-sectional structure and streamline distribution diagram.

[0301] Figure 4B The fan-shaped top view of the valve chamber streamline is an improvement of the existing structure C4.

[0302] Figure 4C A 45-degree view of the flow channel which is an improvement of the existing structure C4.

[0303] Figure 5A The cross-sectional structure and streamline distribution diagram are the second improvement of the existing structure C4.

[0304] Figure 5B This is a fan-shaped top view of the valve chamber streamlines, which is an improvement of the existing structure C4.

[0305] Figure 5C A 45-degree view of the flow channel of the second improvement of the existing structure C4.

[0306] Fig. 6A The cross-sectional structure and streamline distribution diagram of the preferred embodiment A of the first embodiment of the innovative structure C5.

[0307] Figure 6B This is a fan-shaped top view of the valve chamber streamline of the preferred embodiment A of the first embodiment of the innovative structure C5.

[0308] Figure 6C A 45-degree view of the flow channel of preferred embodiment A of the first embodiment of the innovative structure C5.

[0309] Fig.6D In the preferred embodiment A of the first embodiment of the innovative structure C5, vertical ribs are further added to the outer diameter surface of the valve seat to improve the structural strength and guide the streamline flow to the inner outlet.

[0310] Fig. 7A It is the cross-sectional structure and streamline distribution diagram of the second embodiment of the innovative structure C5.

[0311] Figure 7B This is a top view of the valve chamber streamline fan-shaped expansion of the second embodiment of the innovative structure C5.

[0312] Figure 7C A 45-degree view of the flow channel of the second embodiment of the innovative structure C5.

[0313] Fig. 8A It is the cross-sectional structure and streamline distribution diagram of the third embodiment of the innovative structure C5.

[0314] Figure 8B This is a top view of the valve chamber streamline fan-shaped expansion of the third embodiment of the innovative structure C5.

[0315] Figure 8C A 45-degree view of the flow channel of the third embodiment of the innovative structure C5.

[0316] Fig. 9A It is the cross-sectional structure and streamline distribution diagram of the fourth embodiment of the innovative structure C5.

[0317] Fig. 9B This is a top view of the valve chamber streamline fan-shaped expansion of the fourth embodiment of the innovative structure C5.

[0318] Fig. 9C A 45-degree view of the flow channel of the fourth embodiment of the innovative structure C5.

[0319] Fig. 10A It is the cross-sectional structure and streamline distribution diagram of the fifth embodiment of the innovative structure C5.

[0320] Fig. 10B This is a top view of the valve chamber streamline fan-shaped expansion of the fifth embodiment of the innovative structure C5.

[0321] Fig. 10C A 45-degree view of the flow channel of the fifth embodiment of the innovative structure C5.

[0322] Fig.11A It is the cross-sectional structure and streamline distribution diagram of the sixth embodiment of the innovative structure C5.

[0323] Fig. 11B This is a top view of the valve chamber streamline fan-shaped expansion of the sixth embodiment of the innovative structure C5.

[0324] Fig. 11C A 45-degree view of the flow channel of the sixth embodiment of the innovative structure C5.

[0325] Fig. 12AThe cross-sectional structure and streamline distribution diagram of the preferred embodiment B of the first embodiment of the innovative structure C5.

[0326] Fig. 12B This is a fan-shaped top view of the valve chamber streamline of the preferred embodiment B of the first embodiment of the innovative structure C5.

[0327] Fig. 12C A 45-degree view of the flow channel of the preferred embodiment B of the first embodiment of the innovative structure C5.

[0328] Fig.13A The coordinate axes, coordinate points, and streamlines S1 and S2 are for the existing structure C3 flow channel. 12 , Streamline S 121 , Streamline S 122 , schematic diagram of streamline S2.

[0329] Fig. 13B This is a schematic diagram of the existing structure C3 flow channel and its installation angle, corner A, corner B, diffusion C, corner D, and corner E.

[0330] Fig.14A The coordinate axes, coordinate points, and streamlines S1 and S2 are for the existing structure C4 flow channel. 12 , Streamline S 121 , Streamline S 122 , schematic diagram of streamline S2.

[0331] Fig. 14B This is a schematic diagram of the corner A, corner B, diffusion C, corner D, and corner E of the existing structure C4 flow channel.

[0332] Explanation of reference numerals: 5-valve chamber; 51-valve seat; 510-sealing surface; 511-sealing ring; 512-vertical rib; 5121-arc surface; 5122-arc surface; 5123-end of small arc angle; 52-conical tube; 53-annular groove; 531-inclined surface; 54-valve plug; 542-inner concave surface; 55-valve plug chamber; 56-annular chamber; 6-inlet flow channel; 63-center hole; 60-right angle; 7-radial flow channel; 8-outlet flow channel; 82-inner outlet; S-streamline; S1-inlet centerline; S 1a - Upper edge of inlet flow channel; S 1b - Lower edge of inlet channel; S 12 - radial centerline; S 121 - jet; S 122 - slow flow; S2- outlet center line; S 2a - Upper edge of outlet channel; S 2b - outlet flow channel lower edge line; S3-circular arc; SS-tangent surface; A-angle A; B-angle B; C-diffusion C; D-angle D; D1-jet S 121 At the corner D1; D2-slow flow S122 Angle D2 at angle D; E - Angle 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 vertical line YL6; P1 - Center point of center hole; P2 - Center point of valve inlet; P3 - Center point of inner outlet; P4 - Center point of valve outlet; P5 - Point on vertical line YL5; P DP - Center point of the sealing surface; P 11 - The intersection of the vertical line YL1 and the tube axis XL2; 12 - The tangent point between the inlet centerline S1 and the tube axis XL2; P 31 - The intersection of the vertical line YL3 and the tube axis XL2; 34 - the tangent point between the outlet center line S2 and the tube axis XL2; XL1-horizontal line; XL2-tube axis; YL1-vertical line through the center point P1; YL2-vertical line through the center point P4; YL3-vertical line through the center point P3; YL4-vertical line through the center point P2; YL5-vertical line through the intersection point P 12 The vertical line; YL6- passes through the intersection point P 34 The vertical line of E1-the distal end of the central hole; E1 * - When γ1≠0°, the center hole is corrected to be reduced from a non-standard long elliptical hole to the distal end of a circular hole; E2-the proximal end of the center hole; E2 * - When γ1≠0°, the corrected central hole is reduced from a non-standard long elliptical hole to the proximal end of a circular hole; E3-the distal end of the inner outlet; E3 * - Valve opening B1 on major axis a y Antipodal point; E3 ** - Make the distal end point of the inner exit of the concave arc S3; E 35 -Upper edge line S 2a Tangent point with vertical line YL5; E4-proximal point of inner exit; E 46 -Lower edge line S 2b Tangent point with vertical line YL5; E5- distal end point of valve outlet; E6- proximal end point of valve outlet; E7- distal end point of valve inlet; E8- proximal end point of valve inlet; LH1- height of center point P1; LH2- height of center point P3; LH3- height of sealing surface; LH4- height of distal end point E3; LH5- height of proximal end point E4; LH6- height of radial flow channel; LH7- height of top of annular chamber; H1- height difference of distal end point E3 relative to sealing surface; H1 * - Antipodal point E3 * Height difference relative to the sealing surface; H1 ** - Remote point E3 **Height difference relative to the sealing surface; H3-height difference of outlet center point P3 relative to the sealing surface; H5-height difference between the top of the annular chamber and the valve seat sealing surface; 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 arc curve of the entrance center line S1; L2- horizontal distance between the center point P1 and the center point P4; LL2- horizontal distance between the center point P3 and the center point P4; LL 21 - horizontal distance of the arc curve of the outlet center line S2; B1- valve opening; B2- annular space; B3- radial clearance; γ1- angle between the inlet center line S1 and the vertical line YL1; γ2- angle between the outlet center line S2 and the vertical line YL3; γ 21 -Upper edge line S 2a Angle with vertical line YL3; γ 21 ** - the angle between the concave arc S3 and the vertical line YL3; γ 22 -Lower edge line S 2b Angle with vertical line YL3; 2θ1-angle of turning angle A; θ1-placement angle of entrance center line S1; 2θ2-angle of turning angle E; 2θ 21 -Upper edge line S 2a Angle; 2θ 22 -Lower edge line S 2b Angle; θ2-the installation angle of the outlet centerline S2; θ 21 -Upper edge line S 2a The installation angle of θ 21 * - Antipodal point E3 * The obtained installation angle; θ 21 ** - Remote point E3 ** The obtained installation angle; θ 22 -Lower edge line S 2b The placement angle; β-angle of the inclined surface 531; a x - long axis of the central hole (not shown); a y -Inner outlet long axis; b z - inner outlet short axis; b z - short axis of the center hole (not shown); a y * - Antipodal point E3 * The long axis of the inner outlet is obtained; a y ** - Remote point E3 ** The obtained inner outlet major axis; h-the height of the conical tube; φ-cone angle; N-reflux area. DETAILED DESCRIPTION

[0333] The flow channel structural features of the innovative structure C5 of the present invention (such as Fig. 6A ): the smoothly curved inlet flow channel 6, the valve chamber 5, the horizontal radial radial flow channel 7, the annular groove 53 with a slope 531 at the bottom, and the smoothly curved outlet flow channel 8; the radial flow channel 7 comprises an inner concave surface 542 at the bottom of the valve plug 54 and a sealing surface 510 of the valve seat 51 and has a flow channel height B1; the distal end point E3 of the inner outlet 82 of the outlet flow channel 8 is higher than the valve seat 51 and the proximal end point E4 is lower than the valve seat 51; the inner diameter ratio d3 of the valve chamber 5 to the inner diameter d0 of the valve inlet is d3 / d0, 1.75≤d3 / d0≤2.5.

[0334] The innovative structure C5 of the present invention can achieve the following effects: the smoothly curved inlet flow channel 6 has a corner A (the inlet streamline S1) without a recirculation zone N, and the corner B of the center hole 63 contains a jet S 121 With slow flow S 122 With reasonable distribution in the circumferential direction, the fluid will spray through the radial flow channel 7. 121 The diffuser C will fan out (the radial streamline S 12 ) and contains a jet S when flowing into the annular groove 53 121 With slow flow S 122 The laminar flow will not interfere with the flow inside the valve chamber 5, and the corner D of the fluid entering the inner outlet 82 contains the jet S 121 The turning angle D1 and the slow flow S 122 The corner D2 will not interfere with the flow of the inner outlet 82, wherein the preferred embodiment A, wherein the inner outlet 82 has a longer major axis a y ( Fig. 6A ), Can provide jet S 121 With slow flow S 122 There is enough space to flow into the inner outlet 82, the outlet flow channel 8 is smoothly curved, has a corner E (the outlet streamline S2) and no internal recirculation area N is generated; the major axis a of the inner outlet 82 y The height of the valve seat 51 is completely covered, so that the jet S 121 With slow flow S 122 The flow can be layered in the space of the annular groove 53; in the preferred embodiment B, the long axis a of the inner outlet 82 y ( Fig. 12A ), Can provide jet S 121 When passing through the far end point E3, a secondary turn D1 is made in advance, so that the jet S 121 With slow flow S 122 The flow can be layered in the space of the annular groove 53; the head loss coefficient ξ of the structure C5 is based on the inner diameter of 52.5mm, C v≥73.5, 1.7≤ξ≤3.0.

[0335] The following will be based on d0 = 52.5mm, d3 / d0 = 2, B1 = 0.25d0 = 13.14mm, L1 = L 12 =90mm, and the 3D computational fluid dynamics (CFD) software of four flow channel structures was used to analyze the flow field to obtain C v The estimated values ​​are used to illustrate the characteristics of the innovative structure of the present invention. The following schematic diagram of flow field analysis calculation depicts the streamlines of the self-flow field analysis software to illustrate the content in a concise manner. Each embodiment depicts eight streamlines to illustrate the streamline distribution.

[0336] Case A, the results of the flow field analysis calculation of the existing structure C4, please refer to Figure 3A .

[0337] Case B, the flow field analysis calculation results of the improvement 1 of the existing structure C4. The improvement 1 here is a partial improvement of the innovative flow channel of the present invention. Please refer to Figure 4A .

[0338] Case C, the results of flow field analysis and calculation of the existing structure C4 Improvement 2. Here, Improvement 2 is another partial improvement of the innovative flow channel of the present invention. Please refer to Figure 5A .

[0339] Case D, the results of the flow field analysis and calculation of the innovative structure C5, is a complete explanation of the innovative flow channel of the present invention, please refer to Fig. 6A , the innovative structure C5 of the present invention is also the first embodiment of the present invention.

[0340] And continue to discuss the flow channel analysis of the innovative structure C5. Case E, the second embodiment, please refer to Fig. 7A Case F, third embodiment, please refer to Fig. 8A . Case G, Figure 4 embodiment, please refer to Fig. 9A . Case H, Figure 5 embodiment, please refer to Fig. 10A Case I, sixth embodiment, please refer to Fig.11A .

[0341] The following are the structural parameters used in each case: the major axis a of the central hole 63 x ( Figure 1A The height LH1 of the sealing surface 510 is LH3 and is installed on the periphery of the center hole 63 and has a sealing ring 511. The angle γ1 ( Figure 1C ); the radial flow channel opening B1, the radial flow channel height LH6; the height of the center point P3 is LH2, the height of the distal end point E3 is LH4, and the height of the proximal end point E4 is LH5; the placement angle θ of the E3E5 line segment 21, the placement angle of the P3P4 line segment θ2, the placement angle of the E4E6 line segment θ 22 , the inner outlet major axis a y , on the major axis a y The antipodal point on Its line segment Long axis Angle of placement of line segment ( Figure 1B , Figure 1C ).

[0342] Case A, flow path analysis of existing structure C4

[0343] Please refer to Figure 3A Figure, the cross-sectional structure and streamline distribution of the existing structure C4. Please refer to Figure 3B , the streamline fan-shaped upper view of the valve chamber 5 of the existing structure C4. Please refer to Figure 3C , the radial center line S of the existing structure C4 12 A 45 degree view of the corner D of the inner outlet 82. (See also Figures 1A to 1C ).

[0344] C v Value, C V ≈61.89<73.5,ξ≈4.23>3.0.

[0345] The inlet flow channel 6 is a horizontal straight pipe and flows upward at a right angle 60 to the center hole 63 of the valve seat 51; LH3 = LH1 = 36 mm, γ1 = 0°, a x =d0.

[0346] 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 the inclined surface 531 is at the same height as the proximal end point E4.

[0347] The radial flow channel 7 is a horizontally radiating annular flow channel with a valve opening B1.

[0348] The outlet flow channel 8 is a horizontal straight pipe. The distal end point E3 of the inner outlet 82 is lower than the sealing surface 510 of the valve seat 51. <LH3;LH6=49.14mm,LL2=LL 21 =78.75mm, LH4=26.25mm, H1=-9.75mm, LH2=0mm, LH5=-26.25mm, a y =52.5mm, θ 21 =0°, θ2=0°,θ 22 =0°.

[0349] The corner A and the inlet center line S1. The inlet center line S1 in the inlet flow channel 6 is significantly affected by the 60-degree right-angle turn, and there are several recirculation zones N as shown in the figure. Among them, on the upper edge line S 1a There is a large recirculation zone N in the area near the central hole 63. This recirculation zone N will cause the streamline S to be unreasonably deflected to the lower edge line S 1b side, resulting in a reduction in the effective area of the inlet flow channel 6.

[0350] Corner B. When the fluid on the lower edge line S 1b flows out of the central hole 63, a part of the streamline will cross the recirculation zone N near the central hole 63 in the inlet flow channel 6 and spray out towards the distal point E1 side and flow into the radial flow channel 7 to become a slow flow S 122 , the angle of corner B is less than 90 degrees. Another part of the streamline S will spray upwards along the inner wall of the lower edge line S 1b and flow into the radial flow channel 7 to become a jet flow S 121 . The angle of corner B is close to 90 degrees. The recirculation zone N in the figure occupies the flow channel area, resulting in a reduction in the flow rate of the inlet flow channel 6 and being unable to flow into the radial flow channel 7 at a lower angle of corner B.

[0351] Diffusion C. The annular space B2 of the radial gap B3 generates obvious two vortex flows but does not cause particle condensation problems.

[0352] Diffusion C, radial center line S 12 and fan-shaped expansion. The height LH4 of the distal point E3 is lower than the height LH3 of the sealing surface 510 of the valve seat 51, LH4 < LH3. The jet flow S 121 is blocked by the inner diameter of the valve chamber 5 and cannot quickly flow into the inner outlet 82. The streamline S of the jet flow S 121 in the fan-shaped expansion angle of the radial flow channel 7 will exceed 180 degrees, and the fan-shaped expansion of the slow flow S 122 will be at the remaining circumferential angles. Please refer to Figure 3B .

[0353] Corner D, including the corner D1 of the jet flow S 121 and the corner D2 of the slow flow S 122 . The jet flow S 121 and the slow flow S 122 both need to make a 90-degree downward turn to flow into the annular groove 53. This is the first corner D.

[0354] Corner D, the jet flow S 121 and the slow flow S 122 flow interference in the valve chamber 5. The jet flow S 121 and the slow flow S 121 both need to make a 90-degree downward turn for the first corner D of the streamline S to enter the annular groove 53. Among them, part of the jet flow S121 The streamline S will directly enter the inner outlet 82 with the shortest distance and the slow flow S 122 The flow distance will be longer, and a 90-degree downward turn D will disrupt the jet S. 121 With slow flow S 122 The space in the annular groove 53 has a laminar flow, and the downward turning angle D of 90 degrees significantly increases the flow interference inside the valve chamber 5 .

[0355] Corner D, jet S 121 With slow flow S 122 At the flow interference at the inner outlet 82, the jet S 121 The main streamline S is blocked by the inner diameter of the valve chamber 5 and then enters the annular groove 53 downward. After passing the distal end E3, it makes a second turn D1 in the horizontal outlet flow channel 8 and its turning angle is also close to 90 degrees, α1≈90°. 121 A smaller radius of curvature R is required C The flow cannot directly enter the upper half space of the inner outlet 82 and pass through the lower half space of the inner outlet 82, and such a curvature radius R C Will make the jet S 121 The streamline S needs to cross the tube axis XL2 and flow into the lower half space of the inner outlet 82, and the upper edge line S in the outlet flow channel 8 2a The inner diameter surface creates a recirculation zone N, an area where particle condensation may occur.

[0356] Corner D, slow flow S 122 The streamline S will flow along the inclined surface 531 at the bottom of the annular groove 53, α2≈β, and make a secondary turn D2 before the proximal end point E4, where the angle changes from the inclined angle β to the horizontal, and enter the lower half space of the inner outlet 82. At this time, the slow flow S 122 With jet S 121 When entering the lower half of the inner outlet space, flow interference will occur directly, α3≈90°-β.

[0357] The outlet flow channel 8 is a horizontal straight pipe with an angle E of 0 degrees, but the jet S 121 With slow flow S 122 There is severe interference and a recirculation zone N is generated when entering the inner outlet 82 , so the fluid still needs to diffuse inside the outlet flow channel 8 , which will still cause additional head loss.

[0358] For discussion of the flow path of the existing structure C4, please refer to Figure 3AThe right angle 60 of the corner A is a significant head loss and leads to a reduction in the flow channel area. The flow interference of the recirculation zone N on the central hole 63 will cause the angle of the corner B of the streamline S to be close to 90 degrees, which is also a head loss. The outlet flow channel 8 is a horizontal straight pipe, resulting in the distal end point E3 being lower than the sealing surface 510 of the valve seat 51, so that when the streamline S of the radial flow channel 7 is radially expanded, the jet S 121 The streamline will be blocked by the inner diameter of the valve chamber 5 and must flow downward 90 degrees into the annular groove 53. The first turning angle D1 and the turning angle D2 partially flow directly to the jet S of the inner outlet 82. 121 In fact, it makes a ∩-shaped rotation, which is also a head loss, and the jet S 121 When entering the inner outlet 82, the jet flow will make a second turn D1 close to a 90-degree angle, which will cause more head loss. 121 With slow flow S 122 The inner outlet 82 causes serious interference and head loss, resulting in the C of the flow channel of structure C4. V , C V ≈61.89<73.5, ξ≈4.23>3.0 values ​​cannot meet the high flow demand.

[0359] Case B, flow channel analysis of existing structure C4 (improvement 1)

[0360] Please refer to Figure 4A , the improved cross-sectional structure and streamline distribution diagram of the existing structure C4. Please refer to Figure 4B , the improvement of the existing structure C4 is a fan-shaped upper view of the valve chamber 5 streamline. Please refer to Figure 4C , the radial streamline S of the existing structure C4 is improved 12 A 45 degree view of the inner outlet 82 at the corner D. (See also Figures 1A to 1C ).

[0361] C v Value, C V ≈69.88<73.5,ξ≈3.32>3.0.

[0362] The inlet flow channel 6 is a circular curved pipe, flowing upward at an angle A to flow out of the center hole of the valve seat 51; LH3 = LH1 = 59.34 mm, γ1 = 23.2°, d0 / a x ≈0.911.

[0363] 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 the inclined surface 531 is at the same height as the proximal end point E4.

[0364] The radial flow channel 7 is a horizontally radiating annular flow channel with a valve opening B1.

[0365] The outlet flow channel 8 is a horizontal straight pipe, and the distal end 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, θ 22 = 0°, θ 21 = 0°, θ2 = 0°, θ 22 = 0°.

[0366] The included angle γ1 between the rotation angle A and the inlet center line S1, and the inlet center line S1 in the figure has no recirculation zone N in the inlet flow channel 6 and the streamline S is smoothly distributed as shown. The included angle γ1 between the rotation angle A and the center hole 63 of the inlet flow channel 6, γ1 ≠ 0°. When the included angle is non-zero, the effective cross-sectional area of the flow channel will also decrease, but there will be no recirculation zone N and streamline bending, and the effective cross-sectional area is still much higher than Figure 3A .

[0367] Rotation angle B. When the fluid flows out of the center hole 63, the streamline S will make a turn of the rotation angle B. Since the streamline S is smoothly distributed in the figure, on the upper edge line S 1a the radius of curvature R c is small, the flow velocity is fast, and the streamline S is relatively dense. As Figure 4A shown, many streamlines S will turn from the upper edge line S 1a side and turn to the near-end point E2 side at the center hole 63 and enter the radial flow channel 7 to become the jet flow S 121 , and another part of the streamline S will turn to the distal end point E1 and flow into the radial flow channel 7 to become the slow flow S 122 . Such a flow will slightly reduce and smooth the angle of the rotation angle B. Although the flow channel area will decrease due to the included angle γ1, the smooth flow channel will only cause some head losses.

[0368] Diffusion C, radial streamline S 12 and fan-shaped expansion. The height LH4 of the distal end point E3 is lower than the height LH3 of the sealing surface 510 of the valve seat 51. LH4 < LH3. The jet flow S 121 is blocked by the inner diameter of the valve chamber 5 and cannot quickly flow into the inner outlet 82. The streamline S of the jet flow S 121 in the fan-shaped expansion angle of the radial flow channel 7 will not exceed 180 degrees. The fan-shaped expansion of the slow flow S 122 will occur at the remaining circumferential angles; obvious two-vortex flows will be generated in the annular space B2 of the radial gap B3, but no particle condensation problem will occur.

[0369] At corners D and E, the outlet flow channel 8 in this case is the same as the outlet flow channel 8 in case A. There is flow interference in the valve chamber 5 and flow interference in the inner outlet 82 and a recirculation area N is generated.

[0370] For discussion on flow path of the existing structure C4 improvement, please refer to Figure 4A , the arc angle of the corner A can greatly reduce the local head loss, which may reduce the flow channel area but is not affected by the recirculation area N. The angle of the corner B will be reduced, which is another way to reduce the local head loss. The outlet flow channel 8 is a horizontal straight pipe, which causes the far end point E3 to be lower than the sealing surface 510 of the valve seat 5, so that when the streamline of the radial flow channel 7 is expanded 360 degrees, the jet S 121 With slow flow S 122 The streamline will be blocked by the inner diameter of the valve chamber 5 and must make a 90-degree turn downward to flow into the annular groove 53. This situation can reduce some flow interference in the valve chamber 5, but it cannot effectively reduce the first turning angle D1 and the turning angle D2, which is also a head loss, and the jet S 121 When entering the inner outlet 82, the jet flow will make a second turn D1 close to a 90-degree angle, which will cause more head loss. 121 With slow flow S 122 The inner outlet 82 generates severe flow interference and causes head loss, resulting in the structure C4 improving the C of the flow channel. V , C V ≈69.88<73.5, ξ≈3.32>3.0, which is higher than the C of the original structure C4 in case A. V The value is slightly improved by 12.91%, but it is still limited by the outlet flow channel and cannot meet the high flow demand.

[0371] Case C, flow path analysis of existing structure C4 (improvement 2)

[0372] Please refer to Figure 5A , the cross-sectional structure and streamline distribution diagram of the second improvement of the existing structure C4. Please refer to Figure 5B , the valve chamber 5 streamline fan-shaped expansion top view of the second improvement of the existing structure C4. Please refer to Figure 5C , the radial streamline S of the second improvement of the existing structure C4 12 A 45 degree view of the inner outlet 82 at the corner D. (See also Figures 1A to 1C ).

[0373] C v Value, C V ≈64.09<73.5, ξ≈3.94>3.0.

[0374] The inlet flow channel 6 is a horizontal straight pipe and flows upward at a right angle 60 to the center hole of the valve seat 51; LH3 = LH1 = 59.34 mm, γ1 = 0°, a x =d0.

[0375] 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 the inclined surface 531 is at the same height as the proximal end point E4.

[0376] The radial flow channel 7 is a horizontally radiating annular flow channel with a valve opening B1.

[0377] The outlet flow channel 8 is an arc elbow, and the height LH4 of the distal end point E3 of the inner outlet 82 is higher than the sealing surface 510 of the valve seat 51, LH4>LH3; LH6=72.48mm, H1≈19.41mm, LH2=20.05mm, LL2=LL 21 =52.5mm, LH4=78.75mm, LH2=20.05mm, LH5=-12.18mm, a y =90.93mm, θ 21 =45°, θ2=22.46°,θ 22 =15.0°.

[0378] Angle A, inlet centerline S1, angle B, the inlet flow channel 6 in this case is the same as the inlet flow channel 6 in case A. The recirculation area N of the inlet flow channel 6 close to the center hole 63 occupies the flow channel area, so that the flow rate of the inlet flow channel 6 is reduced and cannot flow into the radial flow channel 7 at a lower angle of angle B.

[0379] Diffusion C, radial centerline S 12 The distal end point E3 is higher than the sealing surface 510 of the valve seat 51, LH4>LH3, and the geometric shape of the inner outlet 82 is a non-standard ellipse, with the major axis a y Compared with the diameter d0, a y / d0=1.732, and the height of the proximal end point E4 is LH5, LH5=-12.18mm, and the jet S is affected by the reflow zone N near the center hole 63. 121 The streamline S is obviously affected by the recirculation zone N as in case A, but the jet S of the diffuser C in this case 121 The streamline S can flow directly into the inner outlet 82 and the angle after fanning out will not exceed 180 degrees, slowing down the flow S 122 The fan-shaped expansion will occur at the remaining circumferential angles; the annular space B2 of the radial gap B3 produces obvious two vortex flows but does not cause particle condensation problems.

[0380] Corner D, including jet S121 The turning angle D1 and the slow flow S 122 The distal end point E3 is higher than the sealing surface 510 of the valve seat 51, so that the jet S 121 With slow flow S 122 The angle of the turning angle D of the annular groove 53 is greatly reduced. The first turning angle D, where H1≈19.41mm and B1≈13.14mm, means that the radial flow channel 7 is included between the center point P3 and the distal end point E3. The angle of the turning angle D of the center point P3 is 2θ2=44.91°, and the antipodal point The line segment The new long axis LH6=72.465mm, Represents the majority of jets S 121 Antipodal point The space between the inner outlet 82 and the center point P3 flows into the jet S 121 When entering the inner outlet 82, the angle of the turning angle D is 44.91°<turning angle D<82.7°. A too high H1 means that the turning angle D will cause additional head loss.

[0381] Corner D, jet S 121 With slow flow S 122 The flow interference in the valve chamber 5, the jet S 121 With slow flow S 121 The first turning angle D of the streamline S can enter the annular groove 53 as long as it turns downward less than 90 degrees, and part of the jet S 121 The streamline S will enter the inner outlet 82 with a smaller turning angle and the shortest distance, while the remaining jet S 121 The flow distance will be the second longest and a larger downward turn D is required. 122 The flow distance will be the longest and a larger angle D needs to be made downward, so that the jet S 121 With slow flow S 122 The stratified flow in the space of the annular groove 53; the jet S 121 will flow along the upper half space of the annular groove 53, and the slow flow S 122 The jet flow will flow along the lower half space of the annular groove 53 and along the inclined surface 531 , and the flow interference between the jet flow and the slow flow in the valve chamber is significantly reduced.

[0382] Corner D, jet S 121 With slow flow S 122 At the flow interference at the inner outlet 82, the jet S 121It will still flow along the upper half of the annular groove 53 to make a second turn D1 and more easily enter the upper half of the inner outlet 82. The height of the proximal end point E4 of the inner outlet 82 is LH5, LH5 = -12.18mm, so that the angle β of the inclined surface 531 at the bottom of the annular groove 53 becomes smaller, slowing down the flow S 122 The jet S flows along the lower half of the annular groove 53 and along the inclined surface 531 to make a second turn D2 and can flow more easily into the lower half of the inner outlet 82. 121 The second turning angle D1 and the angle α1 with the outlet center line S2, α1≈22.455°~39.285°, the jet S 121 A larger radius of curvature R will be obtained C can flow into the outlet channel 8, and the curvature radius R C Only a few jets S 121 The streamline needs to cross the tube axis XL2 and flow into the lower half of the inner outlet 82. The flow interference between the jet and the slow flow at the inner outlet is significantly reduced, and the upper edge line S of the inner part of the outlet flow channel 8 is 2a The inner diameter surface will not produce a recirculation zone N, and there will be no problem of particle condensation.

[0383] Corner D, slow flow S 122 The streamline will flow along the inclined surface 531 at the bottom of the annular groove 53, α2≈β, and make a secondary turn D2 before the near end point E4, and its angle changes from the oblique angle β to E4E 46 The installation angle θ 22 , and enters the lower half of the inner outlet 82; due to the jet S 121 The flow with a larger curvature radius smoothly enters the upper half of the inner outlet 82, while the slow flow also smoothly enters the lower half of the inner outlet 82. 121 With slow flow S 122 There will only be slight flow interference between them, α3≈α1-α2.

[0384] The outlet flow channel 8 is a circular curved pipe with a turning angle E of 2θ2, but a smooth curved pipe will not produce a high head loss. Although the jet S 121 With slow flow S 122 Even if there is a slight interference between the outlet flow channel 8, there will be no excessive head loss, no reflow zone N will be generated, and there will be no particle agglomeration problem.

[0385] The outlet flow channel is a circular bend pipe with a turning angle E of 2θ2, but a smooth bend will not produce high head loss. Although the jet S 121 With slow flow S 122 Even if there is a slight interference between the two, it will not increase the head loss of the outlet flow channel too much, and there will be no recirculation area N, and there will be no particle agglomeration problem.

[0386] For discussion of flow path in Improvement 2 of Structure C4, please refer to Figure 5A The right angle 60 of the corner A is a significant head loss and leads to a reduction in the flow channel area. The flow interference of the recirculation zone N on the central hole 63 will cause the angle of the corner B of the streamline S to be close to 90 degrees, which is also a head loss. The result is similar to Figure 3A The flow interference in the valve chamber is significantly reduced except for the recirculation area N of the flow channel. The outlet flow channel 8 is a smooth arc elbow structure, with the distal end E3 higher than the valve seat 51 and the major axis a y is larger than the diameter d0 of the central hole 63, so that when the streamline of the radial flow channel 7 is expanded 360 degrees, the jet S 121 The streamline only needs to make a first downward turn D1 at a small angle to enter the upper half of the annular groove 53. The flow interference between the jet and the slow flow at the inner outlet is significantly reduced, which is also a slight head loss. However, due to the difficulty of the inlet flow channel, the original flow diversion function of the streamline of the jet and the slow flow is not fully utilized. The improvement of the second flow channel C4 V , C V ≈64.09<73.5, ξ≈3.94>3.0, the result of this improvement 2 still does not reach the innovation goal, and is better than the C of the original structure C4. V The value is slightly improved by 3.55%, but it is one C better than the original structure C4. V The value is slightly smaller, and the improvement effect is not as good as the original structure C4.

[0387] Case D, flow channel analysis of innovative structure C5 (preferred embodiment A of the embodiment of FIG. 1 )

[0388] Please refer to Fig. 6A , the cross-sectional structure and streamline distribution diagram of the first embodiment of the innovative structure C5. Please refer to Figure 6B , the valve chamber 5 of the first embodiment of the innovative structure C5 is fanned out in a streamlined upper view. Please refer to Figure 6C , the radial center line S of the first embodiment of the innovative structure C5 12 A 45 degree view of the inner outlet 82 at the corner D. (See also Figures 1A to 1C , Figure 2A ).

[0389] This innovation combines the partial innovations of Case B and Case C into a complete innovative flow channel.

[0390] C v Value, C V ≈82.89>73.5, ξ≈2.36≤3.0.

[0391] The inlet flow channel 6 is a circular curved pipe, and flows upward at an angle A to flow out of the center hole 63 of the valve seat 51; LH3 = LH1 = 59.34 mm, γ1≈23.2°, d0 / a x ≈0.911.

[0392] 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 the inclined surface 531 is at the same height as the proximal end point E4.

[0393] The radial flow channel 7 is a horizontally radiating annular flow channel with a valve opening B1.

[0394] The outlet flow channel 8 is an arc-shaped curved pipe. The height LH4 of the distal end point E3 of the inner outlet 82 is higher than the sealing surface 510 of the valve seat 51, LH4>LH3; LH6=72.48mm, LL2=LL 21 =68.25mm, LH4=94.5mm, H1=35.16mm, LH2=29.14mm, LH5=-5.12mm, a y =99.61, θ 21 =45°, θ2=25.273°,θ 22 =17.21°.

[0395] Angle A, inlet centerline S1, angle B, the inlet flow channel 6 of this case is similar to the inlet flow channel 6 of case B, the inlet flow channel 6 is an arc curved flow channel, and flows upward at the center hole 63 of the valve seat 51 at the angle A, γ1 = 23.2°, d0 / a x ≈0.911, and flows into the radial flow channel 7 at a lower turning angle B, the effective cross-sectional area of ​​the flow channel will also decrease, but there will be no reflow zone N and streamline bending, and the effective cross-sectional area is still much higher than Figure 3A .

[0396] Diffusion C, radial streamline S 12 The distal end point E3 is higher than the sealing surface 510 of the valve seat 51, LH4>LH3, and the geometric shape of the inner outlet 82 is a non-standard ellipse, with the major axis a y Compared with the diameter d0, a y / d0=1.8974, and the height of the near end point E4 is LH5, LH5=-5.12mm, the jet S of the diffuser C 121 The streamline S can flow directly into the inner outlet 82 and the angle after fanning out will not exceed 180 degrees, slowing down the flow S 122 The fan-shaped expansion will occur at the remaining circumferential angles; the annular space B2 of the radial gap B3 produces obvious two vortex flows but does not cause particle condensation problems.

[0397] Corner D, including jet S 121 The turning angle D1 and the slow flow S 122 The distal end point E3 is higher than the sealing surface 510 of the valve seat 51, so that the jet S 121 With slow flow S 122 The angle of the corner D of the downward turn into the annular groove 53 is greatly reduced, the first corner D; the angle of the corner D of the center point P3 is 2θ2=50.55°, the line segment The new long axis LH6=72.465mm, This means that most fluids will flow from the antipodal point The space between the inner outlet 82 and the center point P3 flows into the space between the inner outlet 82; the angle of the angle D when the fluid enters the inner outlet 82 is 50.55°<angle D<68.2°. A too high H1 means that the angle D will have additional head loss. The height of the proximal end point E4 of the inner outlet 82 is LH5, LH5=-5.12mm, so that the angle β of the inclined surface 531 at the bottom of the annular groove 53 becomes smaller; the partial jet S 121 The streamline of the jet S will enter the inner outlet 82 with a smaller turning angle and the shortest distance, while the remaining jet S 121 The flow distance will be the second longest and a larger downward turn D is required. 122 The flow distance will be the longest and a larger angle D needs to be made downward, so that the jet S 121 With slow flow S 122 The stratified flow in the space of the annular groove 53 can slow down the flow S 122 The streamline S will flow along the inclined surface 531 at the bottom of the annular groove 53, α2≈β, and make a secondary turn D2 before the near end point E4, and its angle changes from the oblique angle β to E4E 46 The installation angle θ 22 , and enters the lower half space of the inner outlet 82; the jet S 121 will flow along the upper half space of the annular groove 53, and the slow flow S 122 will flow along the lower half space of the annular groove 53 along the inclined surface 531, so that the jet S 121 With slow flow S 122 A slight flow interference occurs in the valve chamber 5; the jet S 121 The angle D1 of the jet S is α1 with the center line S2 of the outlet, α1≈50.55°~68.2°. 121 A larger radius of curvature R will be obtained C can flow into the outlet channel 8, and the curvature radius R C Only a few jets S 121The streamline needs to cross the tube axis XL2 and flow into the lower half space of the inner outlet 82, and the upper edge line S inside the outlet flow channel 8 2a The inner diameter surface will not produce a recirculation zone N, and there will be no problem of particle condensation; the jet S 121 With slow flow S 122 A slight flow interference occurs at the inner outlet 82 .

[0398] The outlet flow channel 8 in this case is similar to the outlet flow channel in case C. The outlet flow channel 8 is a circular arc bend with an angle E of 2θ2. However, a smooth bend will not produce a high head loss. Although the jet S 121 With slow flow S 122 Even if there is a slight interference between the outlet flow channel 8, there will be no excessive head loss, no reflow zone N will be generated, and there will be no particle agglomeration problem.

[0399] Discussion on the flow channel of the first embodiment of the innovative structure C5, the arc angle of the corner A can greatly reduce the local head loss, which may reduce the flow channel area but is not disturbed by the recirculation area N. The angle of the corner B will be reduced, which is another way to reduce the local head loss. The outlet flow channel 8 is a smooth arc elbow structure, the far end point E3 is higher than the sealing surface 510 of the valve seat 51, and the major axis a y is larger than the diameter d0 of the central hole 63, so that when the streamline of the radial flow channel 7 is expanded 360 degrees, the jet S 121 The streamline only needs to make a first downward turn D1 at a small angle to enter the upper half of the annular groove 53, which is also a slight head loss, and the jet S 121 When entering the inner outlet 82, it has to make a second small angle turn D1, which also causes a slight head loss. Finally, the jet S 121 With slow flow S 122 There is a smaller angle α3 at the inner outlet 82, and the jet S 121 With slow flow S 122 The mutually rotating flows in the outlet flow channel 8 can eliminate the backflow with a rotation angle E of 2θ2, and finally the C of the flow channel with the innovative structure C5 is obtained. V Value, C V ≈82.89>73.5, ξ≈2.36≤3.0, compared with the original structure C4, improved by one, improved by two V The values ​​have been greatly improved, from 11% to 54%, fully meeting the high flow demand. Fig.6DWhen necessary, in order to further enhance the strength of the valve seat 51, a vertical rib 512 is added to the outer diameter surface of the valve seat 51. The vertical rib 512 is located on the side of the inner outlet 82, and its lower part is connected to the bottom of the annular groove 53. The two side surfaces of the vertical rib 512 are two vertical arc surfaces 5121 and 5122, and one side of the two arc surfaces 5121 and 5122 on both sides is tangent to the outer diameter surface of the valve seat 51 to form a wide bottom side, and the other side of the two arc surfaces 5121 and 5122 on both sides intersects to form an end 5123 with a small arc angle. The vertical rib 512 can also guide the streamlines S from the two flows in the annular groove 53 to the inner outlet 82.

[0400] Case E, flow channel analysis of innovative structure C5 (second embodiment)

[0401] Please refer to Fig. 7A , the cross-sectional structure and streamline distribution diagram of the second embodiment of the innovative structure C5. Please refer to Figure 7B , the valve chamber 5 of the second embodiment of the innovative structure C5 is expanded in a streamlined fan-shaped top view. Please refer to Figure 7C , the radial streamline S of the second embodiment of the innovative structure C5 12 A 45 degree view of the inner outlet 82 at the corner D. (See also Figures 1A to 1C , Figure 2B ).

[0402] C v Value, C V ≈81.32>73.5,ξ≈2.45≤3.0.

[0403] The flow channel structure of the second embodiment is established with reference to the first embodiment, wherein the outlet flow channel 8 has the same non-standard elliptical inner outlet 82, and its upper edge line S 2a It is replaced by the straight line segment E3E5, and the lower edge line S 2b It is replaced by straight line segment E4E6.

[0404] The inlet flow channel 6 is a circular arc elbow, and flows out of the center hole 63 of the valve seat 51 upward at an angle A; LH3 = LH1 = 59.34 mm, γ1≈23.2°.

[0405] 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 the inclined surface 531 is at the same height as the proximal end point E4.

[0406] The radial flow channel 7 is a horizontally radiating annular flow channel with a valve opening B1.

[0407] The outlet flow channel 8 is an inclined tube. The height LH4 of the distal end point E3 of the inner outlet 82 is higher than the sealing surface 510 of the valve seat 51, LH4>LH3; LH6=72.48mm, LL2=LL21 =68.25mm, LH4=94.5mm, H1=35.16mm, LH2=29.14mm, LH5=-5.12mm, a y =99.61, θ 21 =45°, θ2=25.27°,θ 22 =17.21°.

[0408] Corner A, entrance centerline S1 and corner B are similar to Fig. 6A Streamline S and corners A and B.

[0409] Diffusion C, radial centerline S 12 Expanding like a fan, similar to Figure 6B The streamline S fan-shaped.

[0410] Angle D, angle D is θ2, 25.27°<angle D<34.11°, similar to Fig. 6A The angle D of the streamline S, including the jet S 121 The turning angle D1 and the slow flow S 122 Corner D2, jet S 121 With slow flow S 122 There is only slight flow interference in the valve chamber 5, and the jet S 121 With slow flow S 122 Only slight flow interference occurs at the inner outlet 82 .

[0411] Corner E, please refer to Fig. 7A The outlet flow channel 8 is a downward sloping straight section pipe with a turning angle E of θ2 and an elbow angle. However, the relatively smooth turning of the elbow angle will not produce a high head loss, and there will be no recirculation area N and no particle agglomeration problem.

[0412] Discussion on the flow channel of the second embodiment of the innovative structure C5, the turning angle D is θ2 so that the jet S 121 With slow flow S 122 can enter the upper and lower halves of the annular groove 53 at a relatively low angle, and the jet S 121 With slow flow S 122 The mutually rotating flows in the outlet flow channel 8 can eliminate the backflow in the elbow angle region where the angle E is θ2, and finally the C of the flow channel of the innovative structure C5 is obtained. V Value, C V ≈81.32>73.5, ξ≈2.45≤3.0, compared with the original structure C4, improved by one, improved by two V The values ​​have been greatly improved, from 11% to 54%, fully meeting the high flow demand.

[0413] Case F, flow channel analysis of innovative structure C5 (Figure 3 embodiment)

[0414] Please refer to Fig. 8A , the cross-sectional structure and streamline distribution diagram of the third embodiment of the innovative structure C5. Please refer to Figure 8B , the valve chamber 5 of the third embodiment of the innovative structure C5 is fanned out in a streamlined upper view. Please refer to Figure 8C , the radial streamline S of the third embodiment of the innovative structure C5 12 A 45 degree view of the inner outlet 82 at the corner D. (See also Figures 1A to 1C , Figure 2C ).

[0415] d0=52.5mm,its C v Value, C V ≈84.6>73.5,ξ≈2.26≤3.0.

[0416] The flow channel structure of the third embodiment is established with reference to the first embodiment, wherein the outlet flow channel 8 has the same non-standard elliptical inner outlet 82, and its upper edge line S 2a It is replaced by the straight line segment E3E5, and the lower edge line S 2b The straight line segments E4 and E6 are used to replace the inner outlet 82, and the shape of the inner outlet 82 is changed to the rectangle inscribed by the non-standard long ellipse, and the two have the same major axis a. y With short axis b z And have the same distal end point E3 and the proximal end point E4, and the four right angles of the rectangle are modified into four small rounded corners, and the area of ​​the rectangle is larger than the area of ​​the non-standard ellipse, which is more conducive to the jet S 121 With slow flow S 122 In particular, the space in the lower half of the inner outlet 82 can be connected to the annular groove 53 more smoothly.

[0417] The inlet flow channel 6 is a circular arc bend pipe, and flows upward at the center hole 63 of the valve seat 51 at an angle A; LH3 = LH1 = 59.34 mm, γ1≈23.2.0°, d0 / a x ≈0.911.

[0418] 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 the inclined surface 531 is at the same height as the proximal end point E4.

[0419] The radial flow channel 7 is a horizontally radiating annular flow channel with a valve opening B1.

[0420] The outlet flow channel 8 is a rectangular inclined tube in cross section. The distal end point E3 of the inner outlet 82 is higher than the sealing surface 510 of the valve seat 51 by a height LH4. <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, θ 21 =45°, θ2=25.273°,θ 22 =17.21°.

[0421] Corner A, entrance centerline S1 and corner B are similar to Fig. 6A Streamline S and corners A and B.

[0422] Diffusion C, radial centerline S 12 Expanding like a fan, similar to Figure 6B The streamline S fan-shaped.

[0423] Corner D, similar to Fig. 6A The angle D of the streamline S is θ2, 25.27°<angle D<34.11° including the jet S 121 The turning angle D1 and the slow flow S 122 Corner D2, jet S 121 With slow flow S 122 There is only slight flow interference in the valve chamber 5, and the jet S 121 With slow flow S 122 Only slight flow interference occurs at the inner outlet 82 .

[0424] Corner E, please refer to Fig. 8A The outlet flow channel 8 is a downward sloping straight section pipe with a turning angle E of θ2 and an elbow angle. However, the relatively smooth turning of the elbow angle will not produce a high head loss, and there will be no recirculation area N and no particle agglomeration problem.

[0425] The discussion of the flow channel of the third embodiment of the innovative structure C5 is similar to the result of the second embodiment, but the inner outlet 82 is rectangular, which provides more streamline space than the original elliptical shape, so that the outlet flow channel 8 smoothly tapers from the inner outlet 82 to the valve outlet to obtain a higher C V value, and the jet S 121 With slow flow S 122 The mutually rotating flows in the outlet flow channel 82 can eliminate the backflow in the elbow angle region where the angle E is θ2, and finally the C of the flow channel of the innovative structure C5 is obtained. v , C v ≈84.6>73.5, ξ=2.26≤3.0, compared with the original structure C4, improved one, improved two C v The values ​​have been greatly improved, from 11% to 54%, fully meeting the high flow demand.

[0426] Case G, flow channel analysis of innovative structure C5 (fourth embodiment)

[0427] Please refer to Fig. 9A , the cross-sectional structure and streamline distribution diagram of the fourth embodiment of the innovative structure C5. Please refer to Fig. 9B , the valve chamber 5 of the fourth embodiment of the innovative structure C5 is fanned out in a streamlined upper view. Please refer to Fig. 9C , the radial streamline S of the fourth embodiment of the innovative structure C5 12 A 45 degree view of the inner outlet 82 at the corner D. (See also Figures 1A to 1C , Figure 2D ).

[0428] C v Value, C v ≈80.89>73.5,ξ≈2.48≤3.0.

[0429] The flow channel structure of the fourth embodiment is established with reference to the first embodiment.

[0430] The inlet flow channel 6 is a circular curved pipe, and flows upward at an angle A to flow out of the center hole 63 of the valve seat 51; LH3 = LH1 = 59.34 mm, γ1≈23.2°, d0 / a x ≈0.911.

[0431] 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 the inclined surface 531 is at the same height as the proximal end point E4.

[0432] The radial flow channel 7 is a horizontally radiating annular flow channel with a valve opening B1.

[0433] The outlet flow channel 8 is an arc-shaped curved pipe. The height LH4 of the distal end point E3 of the inner outlet 82 is higher than the sealing surface 510 of the valve seat 51, LH4>LH3; LH6=72.48mm, LL2=LL 21 =52.5mm, LH4=78.75mm, H1=19.41mm, LH2=20.05mm, LH5=-12.18mm, a y =90.93, θ 21 =45°, θ2=22.46°,θ 22 =15°.

[0434] At the upper edge line S of the outlet flow channel 8 21 Make a tangent arc S3 and intersect the vertical line YL3 at the new far end point Here, the arc S3 is a concave curve, that is, y Make a new remote point on And by the remote point Make an arc S3 tangent to the upper edge line S 2a , distal point The height difference with the valve seat 51 HL6=72.48mm, and the line segment The new long axis A tangent surface SS is made along the arc S3 and the inner diameter surface of the outlet flow channel 8, so that the angle between the arc S3 and the vertical line YL3 is A larger angle, Remote Point Angle of corner D New major axis of the ellipse

[0435] This item is for the upper edge line S of the outlet flow channel 2a The purpose of the modification is to obtain a suitable height of the valve chamber 5 and to eliminate the high turning angle D of the original diffusion C of the distal end point E3 while still maintaining the high flow performance of the flow channel.

[0436] Corner A, entrance centerline S1 and corner B are similar to Fig. 6A Streamline S and corners A and B.

[0437] Diffusion C, radial streamline S 12 Expanding like a fan, similar to Figure 6B The streamline S fan-shaped.

[0438] Corner D, including jet S 121 With slow flow S 122 , distal point Angle of corner D 25.27°<rotation angle D<34.11°, making the jet S 121 With slow flow S 122 The angle of the corner D where the fluid turns downward and flows into the annular groove 53 is greatly reduced, the first corner D.

[0439] Corner D, similar to Fig. 6A The streamline angle D, including the jet S 121 The turning angle D1 and the slow flow S 122 Corner D2, jet S 121 With slow flow S 122 There is only slight flow interference in the valve chamber 5, and the jet S 121 With slow flow S 122 Only slight flow interference occurs at the inner outlet 82 .

[0440] Corner E, please refer to Fig. 9AThe outlet channel 8 is a circular arc elbow with a turning angle E of 2θ. 22 , but smooth bends will not produce high head losses, although the jet S 121 With slow flow S 122 Even if there is slight flow interference between the two, it will not increase the head loss of the outlet flow channel 8 too much, and there will be no recirculation zone N, and there will be no particle agglomeration problem; the jet S 121 With slow flow S 122 The interference in the valve chamber 5, the jet S 121 With slow flow S 122 The streamlines will not cause obvious interference inside the valve chamber 5.

[0441] Discussion of the flow path of the fourth embodiment of the innovative structure C5, part of the jet flow S 121 When the streamline flows directly into the inner outlet 82, it will benefit from the angle of the arc S3 and the tangent surface SS and its turning angle D. 25.27°<angle D<34.11°, the final jet S 121 With slow flow S 122 There is a smaller angle α3 at the inner outlet 82, and the jet S 121 With slow flow S 122 The mutually rotating flows in the outlet flow channel 8 can eliminate the backflow with the turning angle E of 2θ2, and finally the C of the flow channel of the innovative structure C5 is obtained. v , C v ≈80.89>73.5, ξ=2.48≤3.0, compared with the original structure C4, improved by one, improved by two v The values ​​are greatly improved, 11% to 54%, which fully meets the high flow demand. When the arc S3 of this embodiment is other arc curves, C v Significant improvement in value.

[0442] Case H, flow channel analysis of innovative structure C5 (fifth embodiment)

[0443] Please refer to Fig. 10A , the cross-sectional structure and streamline distribution diagram of the fifth embodiment of the innovative structure C5. Please refer to Fig. 10B , the valve chamber 5 of the fifth embodiment of the innovative structure C5 is fanned out in a streamlined upper view. Please refer to Fig. 10C , the radial streamline S of the fifth embodiment of the innovative structure C5 12 A 45 degree view of the inner outlet 82 at the corner D. (See also Figures 1A to 1C , Figure 2E ).

[0444] The flow channel structure of the fifth embodiment is established with reference to the first embodiment.

[0445] d0=52.5mm,its Cv Value, C v ≈83.23>73.5, ξ≈2.34≤3.0.

[0446] The inlet flow channel 6 is a circular curved pipe, and flows upward at an angle A to flow out of the center hole 63 of the valve seat 51; LH3 = LH1 = 59.34 mm, γ1≈23.2°, d0 / a x ≈0.911.

[0447] 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 the inclined surface 531 is at the same height as the proximal end point E4.

[0448] The radial flow channel 7 is a horizontally radiating annular flow channel with a valve opening B1.

[0449] 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 center deviation of the valve plug chamber 55 and the annular chamber 56 is 0.2d0, and the height of the top inside the annular chamber 56 is LH7; the valve plug chamber 55 is concentric with the valve seat 51 and a vertical line YL1 passes through it. The valve plug chamber 55 is used to accommodate the valve plug 54, wherein 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 0.9d0, and 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 1.3d0; the annular chamber 56 accommodates the annular space B2 and the annular groove 53, and the width B2 of the annular groove 53 will vary with the eccentric design and has a maximum width on the inner outlet side.

[0450] The outlet flow channel 8 is an arc bent pipe, and the height LH4 of the distal end point E3 of the inner outlet 82 is higher than the sealing surface 510 of the valve seat 51, LH4>LH3; LH6=72.48mm, LH7=81.61mm, LL2=LL 21 =52.5mm, LH4=78.75mm, H1=19.41mm, LH2=20.05mm, LH5=-12.18mm, a y =90.93, θ 21 =45°, θ2=22.46°,θ 22 =15°.

[0451] When the distal end point E3 of the inner outlet 82 is located higher than the top of the annular chamber 56, LH4>LH7; the distal end point will be higher than the top of the annular chamber 56 and from the far end Make an arc S3 tangent to the upper edge line S 2a , and ensure that the remote endpoint The height difference between the sealing surface 510 of the valve seat 51 and the sealing surface 510 is The line segment The new long axis A tangent surface SS is made along the arc S3 and is tangent to the inner diameter surface of the outlet flow channel 8. The angle between the arc S3 and the vertical line YL3 A larger angle, Remote Point Angle of corner D New major axis of the ellipse (See the fourth embodiment)

[0452] Corner A, entrance centerline S1 and corner B are similar to Fig. 6A Streamline S and corners A and B.

[0453] Diffusion C, radial streamline S 12 Expanding like a fan, similar to Figure 6B 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, that is, the width B2 of the annular groove 53 has the maximum width on the inner outlet 82 side, the jet S 121 There will be more streamlines S that can flow directly into the inner outlet 82 and the angle will be smaller after the fan-shaped expansion and will not exceed 180 degrees, slowing down the flow S 122 The fan-out will be at the remaining circumferential angles.

[0454] Corner D, similar to Figure 6C The streamline angle D, including the jet S 121 The turning angle D1 and the slow flow S 122 Angle D2; Since the horizontal distance between P1 and P3 is 1.3d0, the jet S 121 With slow flow S 122 The diffusion C can be extended to a greater distance and the streamline S can be increased to a greater radius of curvature R. C , so that the jet S 121 With slow flow S 122 There is only slight flow interference in the valve chamber 5, and the jet S 121 With slow flow S 122 Only slight flow interference occurs at this inner outlet.

[0455] The outlet flow channel 8 is a downwardly inclined bend pipe with a turning angle E of 2θ2, but it is relatively smooth and will not produce high head loss. Although the jet S 121 With slow flow S 122Even if there is a slight interference between the outlet flow channel 8, there will be no excessive head loss, no reflow zone N will be generated, and there will be no particle agglomeration problem.

[0456] For a discussion of the flow path of the fifth embodiment of the innovative structure C5, please refer to Fig. 10A , the arc angle of corner A can greatly reduce the local head loss, which may reduce the flow area but not interfered by the recirculation zone N. The angle of corner B will be reduced, which is another way to reduce the local head loss; since the horizontal distance of P1P3 is 1.3d0, the jet S 121 With slow flow S 122 The diffusion C can be extended to a greater distance and the streamline S can be increased to a greater radius of curvature R. C The outlet flow channel 8 is a smooth arc elbow structure, the distal end E3 is higher than the sealing surface 510 of the valve seat 51 and the major axis a y is larger than the diameter d0 of the central hole 63, so that when the streamline S of the radial flow channel 7 is expanded 360 degrees, the jet S 121 The streamline only needs to make a first downward turn D1 at a small angle to enter the upper half of the annular groove 53, which is also a slight head loss, and the jet S 121 When entering the inner outlet 82, it has to make a second small angle turn D1, which also causes a slight head loss. Finally, the jet S 121 With slow flow S 122 There is a smaller angle α3 between the inner outlet 82, and finally the C of the flow channel of the innovative structure C5 is obtained. V , C V ≈83.23>73.5, ξ≈2.34≤3.0, compared with the original structure C4, improved by one, improved by two V The values ​​have been greatly improved, from 11% to 54%, fully meeting the high flow demand.

[0457] Case I, flow channel analysis of innovative structure C5 (sixth embodiment)

[0458] Please refer to Fig.11A , the cross-sectional structure and streamline distribution diagram of the sixth embodiment of the innovative structure C5. Please refer to Fig. 11B , the valve chamber 5 of the sixth embodiment of the innovative structure C5 is fanned out in a streamlined upper view. Please refer to Fig. 11C , the radial streamline S of the sixth embodiment of the innovative structure C5 12 A 45 degree view of the inner outlet 82 at the corner D. (See also Figures 1A to 1C , Figure 2F ).

[0459] The flow channel structure of the sixth embodiment is established with reference to the first embodiment.

[0460] C vValue, C V ≈97.98>73.5,ξ≈1.69≤3.0.

[0461] The inlet flow channel 6 is a circular arc bend pipe, and flows upward at the center hole 63 of the valve seat 51 at an angle A. The sealing surface 510 of the valve seat 51 is located above the center hole 63, and a conical pipe 52 coaxial with the vertical line YL1 is installed to connect the center hole 63. The height h of the conical pipe 52 has a cone angle φ, and its center point P DP , the height of the sealing surface 510 of the valve seat 51 is LH3, LH3 = LH1 + h1; LH1 = 86.88 mm, h = 5 mm, φ = 60°, LH3 = 91.88 mm, γ1 ≈ 2.02°, d0 / a x ≈0.999.

[0462] 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 the inclined surface 531 is at the same height as the proximal end point E4.

[0463] The radial flow channel 7 is a horizontally radiating annular flow channel with a valve opening B1.

[0464] The outlet flow channel 8 is an arc-shaped curved pipe. The height LH4 of the distal end point E3 of the inner outlet 82 is higher than the sealing surface 510 of the valve seat 51, LH4>LH3; LH6=105.02mm, LL2=LL 21 =78.75mm, LH4=105mm, H1=13.12mm, LH2=35.55mm, LH5=0.0mm, a y =105, θ 21 =45°, θ2=26.83°,θ 22 =18.43°.

[0465] Corner A, entrance centerline S1 and corner B are similar to Fig. 6A The function of the conical tube 52 is to provide a diffusion effect on the fluid and its inlet center line S1, so that it can turn angle B more smoothly to enter the radial flow channel 7. This function can further reduce the head loss. Secondly, the conical tube 52 increases the structural strength of the valve seat 51 and improves the reliability of the seal.

[0466] Diffusion C, radial centerline S 12 Expanding like a fan, similar to Figure 6B The streamline S fan-shaped; the conical tube 52 provides the diffusion effect of the inlet centerline S1, so that the jet S 121There are more streamlines S that can flow directly into the inner outlet 82 and the angle after fanning out will not exceed 180 degrees, slowing down the flow S 122 The fan-out will be at the remaining circumferential angles.

[0467] Corner D, including jet S 121 The turning angle D1 and the slow flow S 122 The distal end point E3 is higher than the sealing surface 510 of the valve seat 51, and the diffusion effect of the conical tube 52 makes the jet S 121 With slow flow S 122 The angle of the corner D where the fluid turns downward and flows into the annular groove 53 is greatly reduced, the first corner D.

[0468] Corner D, similar to Fig. 6A The streamline angle D, including the jet S 121 The turning angle D1 and the slow flow S 122 Angle D2; Due to the diffusion effect of the conical tube 52, the jet S 121 With slow flow S 122 There is only a slight flow interference in the valve chamber 5, and the jet S 121 With slow flow S 122 Only slight flow interference occurs at the inner outlet 82 .

[0469] The outlet flow channel 8 is a downwardly inclined bend pipe with a turning angle E of 2θ2, but it is relatively smooth and will not produce high head loss. Although the jet S 121 With slow flow S 122 Even if there is a slight interference between the outlet flow channel 8, there will not be too much head loss, no reflow zone N will be generated, and there will be no particle agglomeration problem.

[0470] For a discussion of the flow path of the sixth embodiment of the innovative structure C5, please refer to Fig.11A , the diffusion angle B of the conical tube 52 will be reduced, and the jet S 121 More fluid flows directly into the inner outlet 82 and the turning angle of the first turning angle D1 is reduced to enter the upper half of the annular groove 53, and the jet S 121 When entering the inner exit 82, it needs to make a second small-angle turn D1, and finally the jet S 121 With slow flow S 122 There is a smaller angle α3 at the inner outlet 82, and the jet S 121 With slow flow S 122 The mutually rotating flows in the outlet flow channel 8 can eliminate the backflow with a rotation angle E of 2θ2, and finally the C of the flow channel with the innovative structure C5 is obtained. V , C V≈97.98>73.5, ξ=1.69≤3.0, compared with the original structure C4, improved by one, improved by two V The values ​​have been greatly improved, from 11% to 54%, fully meeting the high flow demand.

[0471] Table 1, reference data table (unit: mm, %, °, d0 = 52.5, d3 = 105)

[0472]

[0473] Table 2, reference data table (unit: mm, %, °)

[0474]

[0475] Discussion of flow field analysis results: For the following discussion, please refer to the data in Tables 1 and 2.

[0476] 1. Please compare Case A Figure 3A Case B Figure 4A Case C Figure 5A The inlet channel 6 and the outlet channel 8 of the existing structure both have a 90-degree right angle geometric structure. V The value of C can be found that the right-angle structure of the inlet flow channel 6 has the greatest impact on the flow field, because when the inlet flow channel 6 is changed to an arc, C V It is worth improving, from 61.89 to 69.88, and the second improvement is to change the outlet flow channel 6 to an arc to obtain C V The value is 64.09. It is obvious that the recirculation area N generated by the right-angled inlet flow channel 6 is the most important improvement point, followed by the flow interference of the inner outlet 82. Figure 3A It is the flow interference in the valve chamber 5.

[0477] 2. Please compare Figure 3B , Figure 4B , Figure 5B The top view of the valve chamber 5 of the existing structure, improvement 1, and improvement 2 shows that due to the influence that the valve seat 51 is higher than the inner outlet 82, the fluid will be blocked by the inner diameter of the valve chamber 5 when flowing out of the center hole 63 and expand in a fan shape, wherein the jet S 121 The expansion angle will exceed 180 degrees.

[0478] 3. Please compare with Case B Figure 4A Case C Figure 5A Case D Fig. 6A , the C of the three V The values ​​are 69.88, 64.09, and 82.89, respectively, indicating that only the inlet flow channel 6 and the outlet flow channel 8 of the first embodiment are arc elbows. VThe value can only be higher than 73.5, indicating that the flow interference in the valve chamber 5 and the flow interference in the inner outlet 82 of the first embodiment are greatly reduced, but the area of ​​the inlet flow channel 6 of the first embodiment is reduced, d0 / a x ≈0.911, which also causes its C V The value cannot be increased further.

[0479] 4. Please compare Case D Fig. 6A Case E Fig. 7A In the second embodiment, the outlet channel 8 of the first embodiment is changed into an inclined tube structure, but the inner outlet 82 is still maintained to have the same size of non-standard ellipse. V The value is 81.32, with the elbow structure of the turning angle E, indicating that the inclined tube structure can be a jet S 121 The benefit of greatly reducing the first corner D is that the reflux in the elbow area brings additional losses. Although there will be no particle agglomeration problem in the reflux area of ​​the elbow, the overall C V The value decreased by 1.57.

[0480] 5. Please compare Case D Fig. 6A Case E Fig. 7A Case F Fig. 8A In the third embodiment, the outlet channel 8 of the second embodiment is changed into an inclined tube structure, but the inner outlet 82 has the same major axis a y With short axis b z The size of the rectangle is C V The value is 84.6. As the area of ​​the rectangular inner outlet 82 increases, more jet S 121 can flow more smoothly into the inner outlet 82, and the overall C V The value is improved by 3.28 compared with the second embodiment.

[0481] 6. Please compare Case D Fig. 6A Case G Fig. 9A In the fourth embodiment, the length LL of the outlet flow channel 8 is 21 Shortened, LL of the first embodiment 21 =68.25mm, LL of the fourth embodiment 21 =52.25mm, make corrections at the inner outlet 82, the correction method is to make corrections on the major axis a y Select Far Point And make the concave arc S3 and the concave surface SS, The advantage of reducing the head loss at the turning angle D is that the overall C of the fourth embodiment V The value is 80.89, which is 2.0 lower than that of the first embodiment. 21 The length of a is shortened y The value is also shortened, although The length can be maintained at 84.66mm, but the too low LH5 = -12.18mm is still not conducive to the flow of fluid, and finally offsets The advantages brought by the V Characteristics of the value.

[0482] 7. Please compare Case G Fig. 9A Case H Fig. 10A In the fifth embodiment, the valve chamber 5 of the fourth embodiment is made into an eccentric structure and the inner outlet 82 is not modified. Since 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 1.3d0, the width B2 of the annular groove 53 will change with the eccentric design and have a maximum width on the inner outlet 82 side. Among them, the eccentric structure is a jet S 121 It brings more diffusion space so that the corner D of the diffuser C has a smoother angle. The overall C of the fifth embodiment V The value is 83.23, which is 2.34 higher than that of the fourth embodiment.

[0483] 8. Please compare Case D Fig. 6A Case I Fig.11A In the sixth embodiment, the length LL of the outlet flow channel 8 of the first embodiment is 21 By extending and raising the height of the valve seat 51, the LL of the sixth embodiment 21 =78.75mm, LH3=91.88mm, LH1=86.88mm, d0 / a X =0.999, wherein 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 better diffusion effect of the fluid when making a turn B, and is the jet S 121 The corner D of the diffuser C has a smoother angle, and the overall C of the sixth embodiment V The value is 97.98, which is 15.09 higher than that of the first embodiment.

[0484] 9. Refer to Table 2. Case D1 and Case D2 are made according to the structure of Case D. The pipe diameter d0 is 52.5mm, but the inner diameter d3 of the valve chamber is more compact, which is 94.5mm. The inner diameter ratio is 1.8 to 84mm is 1.6, and its C V The values ​​are 81.37 and 68.26 respectively, and the head loss coefficient ξ is 2.43 and 3.48 respectively. It can be seen that a too small inner diameter d3 of the valve chamber will greatly reduce the width of the annular groove 53 and force the jet S 121 When the flow flows into the annular groove 53, the angle of the corner D increases, thereby increasing the head loss and increasing the flow interference in the valve chamber 5 and the flow interference in the inner outlet 82. Only the effect equivalent to that of case B can be achieved. The inner diameter ratio of case D2 is 1.6 is obviously too small.

[0485] 10. Please refer to Table 2. For case D3, the pipe diameter d0 (valve inlet diameter / valve outlet diameter / center hole diameter) is 22.2 mm, the valve chamber inner diameter d3 is 41.74 mm, and the inner diameter ratio The case where the head loss coefficient ξ is 1.88 and 2.29, the flow field analysis results of this case show that the minimum pipe diameter d0 is 22.2mm, but as long as the inner diameter is 1.88 is not too low and still can get a good C V The value is 15.06 and the head loss coefficient ξ is 2.29.

[0486] 11. The credibility of flow field analysis data is as follows:

[0487]

[0488] Among them, the data in reference file seven are the measured values ​​of the flow coefficient of the structure C4 product, KH200-19P; KH200-25P; KH200-40P; because the model of the flow field analysis software cannot truly reflect the flow of the valve body, although its analysis value will be slightly higher than the measured value, the reference value of its analysis result is still unquestionable.

[0489] 12. Compared with reference document 7, case D4 has a pipe diameter d0 of 33.7 mm and a valve chamber inner diameter d3 of 66.34 mm. is 2.0, and the flow coefficient C is obtained by flow field analysis V The value is 37.5, the head loss coefficient ξ is 1.95, and the prototype flow channel of case D4 is made by rapid prototyping (3D printing), and the obtained pipe diameter d0 is 33.1mm. The actual measured flow coefficient C V The value is 31.8, and the head loss coefficient ξ is 2.53; the measured value of case D4 is significantly and greatly improved over the measured value of structure C4 with the same caliber, and the ratio of the head loss coefficient ξ is 2.53:6.30, (6.3-2.53) / 6.3=0.598, which is a relative improvement of 59.8%; the comparison of the above data is sufficient to illustrate the advancement of the innovative flow channel C5 structure of the present invention.

[0490] 13. With respect to reference document 7, case D5 is a preferred embodiment B of the first embodiment. For detailed description of the flow channel and flow field, please see Fig. 12A , Fig. 12B , Fig. 12C In case D5, the pipe diameter d0 is 33.7 mm, the valve chamber diameter d3 is 63 mm, and the inner diameter ratio is 1.87, the jet S 21When the flow passes through the far end point E3, the angle of the second turn D1 is reduced to 60°. The flow coefficient C is obtained by flow field analysis. V The value is 33.79, and the head loss coefficient ξ is 2.41, which shows that the angle of the second turning corner D1 can effectively reduce the flow interference of the inner outlet.

[0491] 14. The extended application of the present invention, Case F and Case I are both extended from Case D to obtain a better flow coefficient value C V Of course, you can also add the rectangular inner outlet 82 of case I to case F to obtain a better flow coefficient value C V , but it will be limited by the casting forming method, that is, the contents of Case D, Case E, Case F, Case G, Case H, Case I in Table 1 and Case D1, Case D2, Case D3, Case D4, and Case D5 in Table 2. The local features of the innovative flow channel structure can be transformed in size and added in structural features to obtain a better flow coefficient value C V , and these structural and dimensional variations are all within the scope of the present invention.

Claims

1. An improved valve body flow channel of a stop valve, a valve body flow channel with a low head loss coefficient ξ that meets the ESG requirements, the structure of the valve body flow channel includes a valve chamber, an annular groove, a valve seat, a valve plug, a sealing surface, a valve inlet, an inlet flow channel, a center hole, a valve outlet, an outlet flow channel, and an inner outlet; The inner diameter of the valve chamber is d3, the outer diameter of the valve plug is d2, the outer diameter of the valve seat is d1, the inlet diameter of the valve is d0, the outlet diameter of the valve is d0, and the center hole diameter is d0; The sealing surface of the valve seat is located outside the center hole, the center point P1 of the center hole has a height of LH1, the center point P3 of the inner outlet has a height of LH2, the sealing surface of the valve seat has a height of LH3 and is provided with a sealing convex ring; the valve inlet has a center point P2, and the valve outlet has a center point P4; A horizontal line XL1 passes through the center point P1 of the center hole, and the horizontal line XL1 intersects with the circumference of the center hole at two intersection points, a distal end point E1 and a proximal end point E2, wherein the distal end point E1 is located at the inlet side of the valve, and the proximal end point E2 is located at the outlet side of the valve; A pipe axis XL2 passes horizontally through the center point P2 and the center point P4. The height markings are all based on the pipe axis XL2 connecting the valve outlet and the valve inlet. The Y-axis coordinate zero point has positive, zero and negative values ​​when indicating the position relative to the pipe axis XL2. A vertical line YL1 passes through the center point P1 and intersects the tube axis XL2 at point P 11 ; A vertical line YL2 passes through the center point P4, and the vertical line YL2 intersects the valve outlet circumference at two intersection points, the distal end point E5 and the proximal end point E6, and the proximal end point E6 is the lowest point of the outlet flow channel; A vertical line YL3 passes through the center point P3 of the inner outlet and intersects the tube axis XL2 at point P 31 , and the vertical line YL3 intersects the inner outlet circumference at two intersection points, the distal end point E3 and the proximal end point E4, the height of the distal end point E3 is LH4 and the height of the proximal end point E4 is LH5; A vertical line YL4 is established through the center point P2, and the vertical line YL4 intersects the valve inlet circumference at two intersection points, the distal end point E7 and the proximal end point E8, and the proximal end point E8 is the lowest point of the inlet flow channel; There is a horizontal distance L1 between the center point P1 and the center point P2, P11P2 = L1; there is a horizontal distance L2 between the center point P4 and the center point P1, P4P 11 =L2; there is a horizontal distance L between the center point P2 and the center point P4, P4P2=L=L1+L2; There is a horizontal distance LL2 between the center point P4 and the center point P3. The valve chamber is provided with the annular groove and the valve seat, and is provided with the valve plug, valve shaft and sealing surface, and the valve plug, valve shaft and sealing surface are concentric; the valve chamber is used to connect the inlet flow channel and the outlet flow channel; the inlet flow channel enters from the horizontal valve inlet and turns upward, and the center hole of the valve seat is provided at its outlet end; the inner outlet is provided on the inner diameter surface of the valve chamber to connect the outlet flow channel; the valve inlet and the valve outlet are respectively provided on both sides of the valve body; when the outlet flow channel is a straight pipe or a circular curved pipe in a downward inclined form, the inner outlet is a non-standard elliptical shape; The annular groove is located at the inner diameter of the valve chamber and surrounds the outer diameter of the valve seat. The bottom of the annular groove is a slope with an angle β. The high side of the slope is located at the inlet flow channel side, and the low side of the slope is located at the outlet flow channel side and connected to the proximal end point E4 of the inner outlet. The valve seat is installed at the outlet end of the inlet flow channel and is provided with the sealing surface; The valve plug is cylindrical and has a flat surface at the bottom. When the stop valve is closed, the valve plug is used to couple and seal with the sealing surface. When the valve is fully opened, the bottom surface of the valve plug and the sealing surface form a radial flow channel with an opening B1. The inlet flow channel includes the valve inlet, an inlet center line S1, the center hole, an upper edge line S 1a With the edge line S 1b The entrance center line S1 connects the center points P1 and P DP There is an angle γ1 with the center point P2 and with the vertical line YL1 at the center point P1; when the angle γ1≠0°, the center hole will be a non-standard elliptical hole with a major axis a in the X-axis direction. x , a x ≥d0,a x =E1E2, E1P1≥P1E2; when the angle γ1=0°, the center hole will be a circular hole with a diameter of d0; and has a short axis b in the Z-axis direction. z , b z = d0; the upper edge line S 1a Connecting the distal end point E1 and the distal end point E7, the lower edge line S 1b Connecting the proximal end point E2 and the proximal end point E8; The radial flow channel includes a radial center line S 12 , the opening B1, when the valve plug is opened, the bottom surface of the valve plug and the sealing surface form the radial flow channel, the opening B1, the radial flow channel surrounds the radial flow channel of the center hole, the height of the radial flow channel LH6, LH6 = B1 + LH3; radial center line S 12 , connecting the center point P1 and the center point P3; radiating out from the center point P1 in different directions and finally connecting to the center point P3; The outlet flow channel includes the inner outlet, the valve outlet, an outlet center line S2, an upper edge line S 2a With the edge line S 2b The outlet center line S2 connects the center point P3 and the center point P4, and has an angle γ2 between the center point P3 and the vertical line YL3, 0°≤γ2<90°, and when the inner outlet is a non-standard elliptical hole, it has a major axis a in the Y-axis direction y , a y ≥d0,a y =E3E4, E3P3≥P3E4, with a short axis b in the Z direction z , b z = d0; when the angle γ2 = 90°, the outlet flow channel is a horizontal straight pipe, a y = d0; the upper edge line S 2a Connecting the distal end point E3 and the distal end point E5, the lower edge line S 2b Connect the proximal end point E4 and the proximal end point E6; the distal end point E3 has a height difference H1 relative to the sealing surface, LH4-LH3=H1, when the distal end point E3 is higher than the sealing surface, H1≥0, otherwise H1≤0; the inner outlet center point P3 has a height difference H3 relative to the sealing surface, LH2-LH3=H3, when the P3 point is higher than the sealing surface, H3≥0, otherwise H3≤0; A radial gap B3 is located between the outer diameter d2 of the valve plug and the inner diameter d3 of the valve chamber. An annular space B2 is between the outer diameter d1 of the valve seat and the inner diameter d3 of the valve chamber, B2 = (d3-d1) / 2, Inner diameter ratio The ratio of the inner diameter d3 of the valve chamber to the inlet diameter d0 of the valve is: The following will be based on the inlet centerline S1, the radial centerline S 12 The three center lines including the outlet center line S2 are used to represent the streamlines, while the description of the turning angles is based on the geometric shapes that can be inferred. The description will be obtained using complex 3D-CFD calculations; The entrance center line S1 is a single line segment or a combination of several line segments, and the line segment types include: arc curve, vertical line segment, oblique line segment, horizontal line segment, wherein, The vertical line segment is coaxial with the vertical line YL1, the horizontal line segment is coaxial with the tube axis XL2, and the turning angle A is the turning angle of the inlet center line S1 from the valve inlet to the center hole; The radial center line S 12 After the fluid flows out of the center hole, all streamlines flow out in different directions in a radial manner and enter the radial flow channel. The turning angle B is from the inlet center line S1 to the radial center line S 12 The turning angle between the two, all streamlines pass through the horizontal radial flow diffusion C and make several turns to flow toward the inner outlet; the radial center line S 12 The flow rate of the fluid in diffusion C slows down after turning B because the area of ​​the radial flow channel increases, but it accelerates when flowing toward the inner outlet after several turns because the area decreases; the radial center line S 12 Affected by the relative position between the sealing surface and the inner outlet, it is a straight line, an arc, or an arc with multiple bends; The radial center line S 12 Since the fluid is driven by the pressure difference between the valve inlet and the valve outlet, the radial center line S of the diffuser C 12 Jet S 121 With slow flow S 122 The high-density streamline that is subjected to the high pressure gradient is the jet S 121 The low-density streamline with higher flow velocity and low pressure gradient is a slow flow. 122 Its flow velocity is slightly lower; the streamlines of the diffusion C flow fan out in the circumferential direction and are affected by the angle B. The jet S 121 Fan out toward the inner outlet, and the slow flow S 122 The fan-shaped expansion is performed at a circumferential angle outside the jet fan-shaped expansion angle; the radial center line S 12 , jet S 121 With slow flow S 122 Before flowing into the inner outlet, they make a turn D and a jet S 121 The corner is D1, the slow flow is S 122 is the corner D2; The outlet center line S2 is a single line segment or a combination of several line segments, and the line segment types include: arc curve, oblique line segment, horizontal line segment, etc., wherein the horizontal line segment is coaxial with the tube axis XL2; the outlet center line S2, the turning angle D is the radial center line S 12 The fluid makes a turn E between the inner outlet and the outlet flow channel and then flows out of the valve outlet; Features: The inlet flow channel starts from the circumference of the valve inlet and goes along the inlet center line S1 to the circular center hole with a diameter of d0. A 3D inner diameter surface diagram of the inlet flow channel is made, and its section has an upper edge line S 1a With the lower edge line S 1b ; The inlet center line S1 has a straight line segment and a circular arc curve; a tangent point P is taken on the tube axis LX2 12 The arc curve has one end point as the center point P1 and another end point as the tangent point P 12 , tangent point P 12 is the tangent point between the arc curve and the tube axis XL2, and the arc curve has a horizontal distance L 11 =P 11 P 12 , one end of the straight line segment is the tangent point P 12 The other end point is the center point P2, P 12 Horizontal distance of P2 = L1-L 11 ; Through point P 12 Draw a vertical line YL6 and take a circle center point P0 on the vertical line YL6 so that the line segment P0P 12 is the same length as line segment P0P1, while line segment P0P 12 The angle 2θ1 between the line segment P0P1 is equal to the rotation angle A, and the placement angle θ1 is equal to the line segment P1P 12 and obtaining an angle γ1 between the arc curve and the vertical line YL1 at the center point P1 of the center hole, γ1 = 90°-2θ1; When the angle γ1≠0°, the center hole is corrected from a non-standard long elliptical hole to a circular hole with a diameter d0. The original major axis a x , a x = The length of E1E2 is reduced to d0 by taking a far end point on the major axis. Replace the distal point E1 with a proximal point on the long axis Replace the proximal point E2, Long axis a x Length reduction ratio Long axis a x Length reduction ratio The distal end E3 has a height LH4, the height difference between the distal end E3 and the sealing surface is H1, and the proximal end E4 has a height LH5; the line segment E3E4 is the long axis a of the inner outlet in the Y-axis direction. y , a y =E3E4; The outlet center line S2 has a straight line segment and an arc curve; a tangent point P is taken on the tube axis XL2 34 One end point of the arc curve is the center point P3 and the other end point is a tangent point P 34 , tangent point P 34 The arc curve is tangent to the tube axis XL2, and the arc curve has a horizontal distance LL 21 =P 31 P 34 , one end of the straight line segment is the tangent point P 34 The other end point is the center point P4, P 34 Horizontal distance of P4 = LL2-LL 21 ; Through point P 34 Draw a vertical line YL5 and take a circle center point P5 on the vertical line YL5 so that the line segment P5P 34 is the same length as line segment P5P3, while line segment P5P 34 The angle 2θ2 between the line segment P5P3 is equal to the rotation angle E, and the placement angle θ2 is equal to the line segment P3P 34 The horizontal angle between the arc curve and the vertical line YL3 is obtained at the center point P3, and γ2 = 90°-2θ2; When the outlet center line S2 is composed of a straight line segment and an arc curve, the outlet flow channel maintains a cross-sectional area of ​​equal diameter, and its upper edge line S 2a , lower edge line S 2b The three arc curves are parallel to each other and have a common center point P5. The inner outlet is a non-standard long ellipse. The major axis a of the non-standard long ellipse is y =E3E4, E3P3>P3E4, the minor axis b of the non-standard long ellipse z =d0; The upper edge line S 2a It will intersect with the vertical line YL5 at a tangent point E 35 , tangent point E 35 The height of line segment P5E is d0 / 2. 35 The angle between the line segment P5E3 and the line segment P5E3 is 2θ 21 , and obtain the angle γ between the arc curve and the vertical line YL3 at the far end point E3 21 , γ 21 =90°-2θ 21 , through the upper edge line S 2a The height value LH4 of the far end point E3 will be obtained; The lower edge line S 2b It will intersect with the vertical line YL5 at a tangent point E 46 , tangent point E 46 The height is The angle between line segment P5E46 and line segment P5E4 is 2θ 22 , and obtain the lower edge line S at the proximal end point E4 2b Angle γ with vertical line YL3 22 , γ 22 =90°-2θ 22 ; Through the lower edge line S 2b The height value LH5 of the near end point E4 will be obtained; Jet S 121 With slow flow S 122 The annular groove can finally achieve stratified flow to reduce the flow interference in the valve chamber and the flow interference of the inner outlet. The upper edge line S of the outlet flow channel 2a The angle of rotation E is 2θ 21 , 30°≤2θ 21 ≤90°.

2. The valve body flow channel improvement of the stop valve according to claim 1, characterized in that: The center point of the center hole has a height LH1 relative to the tube axis XL2, and its rotation angle A is an angle 2θ1, 55°≤2θ1≤105°.

3. The valve body flow channel improvement of the stop valve according to claim 1, characterized in that: Jet S 121 When the diffuser C flows to the annular groove, it makes the first turn D1, and when it passes the far end point E3, it makes the second turn D1, and the angle is γ 21 , 0°≤γ 21 ≤60°.

4. The valve body flow channel improvement of the stop valve according to claim 1, characterized in that: The height LH5 of the proximal end point E4 is connected to the bottom of the inclined surface of the annular groove.

5. The valve body flow channel improvement of the stop valve according to claim 1, characterized in that: Outlet channel lower edge line S 2b The angle of rotation E is 2θ 22 , 14°≤2θ 22 ≤54°.

6. The valve body flow channel improvement of the stop valve according to claim 1, characterized in that: When the height difference ratio is H1 / d0, H1 / d0≤0.5, the height of the far end point E3 has no significant effect on reducing the head loss, while the major axis ratio a y / The larger the d0, the lower the head loss, but it also brings the problem of too large a valve body; due to the jet S 121 The radial flow channel is horizontally discharged, and the height LH6 of the radial flow channel corresponding to the major axis a is found. y There is a pair of points LH6≈LH3+B1, antipodal point The height difference with the valve seat is And the jet S 121 At the antipodal point The center point P3 flows into the inner outlet, where the antipodal point Placement angle Equal to line segment The horizontal angle of With a smaller placement angle To describe the jet S 121 It can be clearly seen that the lower the angle α1, the lower the head loss.

7. The valve body flow channel improvement of the stop valve according to claim 1, characterized in that: The bevel angle β of the inclined surface of the annular groove is approximately equal to the included angle θ. 22 , 8°≤β≤20°.

8. The valve body flow channel improvement of the stop valve according to claim 1, characterized in that: The radial flow channel is formed by an inner concave surface of the bottom of the valve plug and a sealing surface of the valve seat and has a flow channel height B1.

9. The improved valve body flow channel of the stop valve according to claim 1, characterized in that: The outlet flow channel maintains the inner outlet as a non-standard ellipse, and the outlet center line S2, the upper edge line S 2a , the lower edge line S 2b Change to a combination of straight line segments; line segment P3P 34 Connect the center point P3 and the tangent point P 34 , line segment E3E 35 Connect the far end point E3 and the tangent point E 35 , line segment E4E 46 Connect the proximal end point E4 and the tangent point E 46 ; From the circumference of the non-standard ellipse of the inner outlet as the starting point, along the outlet center line S2 to the circular valve outlet, make a 3D inner diameter surface diagram of the outlet flow channel, and its section has an upper edge line S 2a With the lower edge line S 2b ; Through point P 34 Draw a vertical line YL5 and take a point P5 on the vertical line YL5 so that the line segment P5P 34 is the same length as line segment P5P3, while line segment P5P 34 The angle 2θ2 between the line segment P5P3 is equal to the line segment P3P 34 The rotation angle E, the placement angle θ2 is equal to the line segment P3P 34 Horizontal angle.

10. The valve body flow channel improvement of the stop valve according to claim 1, characterized in that: The shape of the inner outlet is modified from the non-standard ellipse to a rectangle, the non-standard ellipse is inscribed in the rectangle, and the two have the same major axis a y With short axis b z and have the same distal end point E3 and proximal end point E4, the four right angles of the rectangle are modified into four small rounded corners; the outlet center line S2 of the outlet flow channel, the upper edge line S 2a , the lower edge line S 2b Change to a combination of straight line segments; line segment P3P 34 Connect the center point P3 and the tangent point P 34 , line segment E3E 35 Connect the far end point E3 and the tangent point E 35 , line segment E4E 46 Connect the proximal end point E4 and the tangent point E 46 ; From the circumference of the inner rectangular outlet as the starting point along the outlet center line S2 to the circular valve outlet, a 3D inner diameter surface diagram of the outlet flow channel is made, and its cross section has an upper edge line S 2a With the lower edge line S 2b ; Through point P 34 Draw a vertical line YL5 and take a point P5 on the vertical line YL5 so that the line segment P5P 34 is the same length as line segment P5P3, while line segment P5P 34 The angle 2θ2 between the line segment P5P3 is equal to the line segment P3P 34 The rotation angle E, the placement angle θ2 is equal to the line segment P3P 34 Horizontal angle.

11. The valve body flow channel improvement of the stop valve according to claim 9 or claim 10, characterized in that: The line segment P3P 34 The installation angle is θ2 and the rotation angle D of the center point P3 is θ2, The line segment E3E 35 The installation angle θ 21 And the rotation angle D of the far end point E3 is θ 21 , The line segment E4E 46 The installation angle θ 22 And the angle D of the near end point E4 is θ 22 , The outlet center line S2 is at the tangent point P 34 Make a turn at angle E, angle E = θ2; The upper edge line S 2a At the tangent point E 35 Make a turn at angle E, angle E = θ 21 ; The lower edge line S 2b At the tangent point E 46 Make a turn at angle E, angle E = θ 22 ; The rotation angle D of the far end point E3 = θ 21 , 14°≤θ 21 ≤45°; Tangent point E 35 The rotation angle E = θ 21 , 14°≤θ 21 ≤45°; The rotation angle D of the near end point E4 = θ 22 , 7°≤θ 22 ≤20°; Tangent point E 46 The rotation angle E = θ 22 , 7°≤θ 22 ≤20°.

12. The valve body flow channel improvement of the stop valve according to claim 1, characterized in that: When the height H1 of the far end point E3 of the ellipse needs to be adjusted, the upper edge line S 21 Make a tangent arc S3 and intersect the vertical line YL3 at the new far end point At the remote point The angle of arc S3 A large angle, A tangent surface SS is made along the arc S3 to the upper edge of the inner diameter of the outlet flow channel, so that part of the jet S 121 When entering the inner outlet directly, the flow flows along the tangent surface SS and reduces the angle of the turning angle D1.

13. The valve body flow channel improvement of the stop valve according to claim 13, characterized in that: Remote Point There is a height difference with the valve seat New major axis of the ellipse 14. The valve body flow channel improvement of the stop valve according to claim 1, characterized in that: The inlet flow channel and the outlet flow channel maintain the inner outlet as a non-standard ellipse. The inner diameter d3 of the valve chamber and the outer diameter d1 of the valve seat are eccentrically designed, so that the structure of the valve chamber is a hollow circular eccentric structure. The structure of the valve chamber is divided into a valve plug chamber with a diameter of 1.8d0 and an annular chamber with a diameter of 2.2d0. The center deviation between the valve plug chamber and the annular chamber is 0.2d0, and the height of the top of the annular chamber is LH7; the valve plug chamber and the valve seat are concentric and a vertical line YL1 passes through the valve. The plug chamber is used to accommodate the valve plug, wherein 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 inner outlet side of the annular chamber is 1.3d0; the annular chamber accommodates the annular space and the annular groove, and the width B2 of the annular groove varies with the eccentric design and has a maximum width on the inner outlet side. The top of the inner part of the annular chamber has a height difference H5 with the valve seat sealing surface, H5 = LH7-LH3, 15. The valve body flow channel improvement of the stop valve according to claim 14, characterized in that: When the height LH4 of the distal end point E3 is higher than the height LH7, H1>H5, LH4>LH7, then the distal end point E3 needs to be on the long axis a y Find a new remote point And by the remote point Make an arc S3 tangent to the upper edge line S 2a , and ensure that the remote endpoint Height difference with the valve seat sealing surface The line segment The new long axis A tangent surface SS is made along the arc S3 and is tangent to the inner diameter surface of the outlet flow channel. The angle between the arc S3 and the vertical line YL3 A large angle, Remote Point Angle of corner D New major axis of the ellipse 16. The valve body flow channel improvement of the stop valve according to claim 1, characterized in that: The sealing surface of the valve seat is located outside the center hole. A conical tube coaxial with the vertical line YL1 is installed on the center hole and has a center point P DP The height of the sealing surface of the valve seat is LH3, the height of the center hole is LH1, the height h of the conical tube has a cone angle φ, LH3 = LH1 + h; the function of the conical tube is to provide a diffusion effect for the fluid and its inlet streamline S1, and to be able to smoothly turn at an angle B to enter the radial flow channel to reduce the head loss, and the conical tube increases the structural strength of the valve seat and improves the reliability of the seal.

17. The valve body flow channel improvement of the stop valve according to claim 16, characterized in that: The height of the conical tube h, The cone angle φ of the conical tube is 15°≤φ≤60°.

18. The valve body flow channel improvement of the stop valve according to claim 1, characterized in that: In order to enhance the strength of the valve seat, a vertical rib is added to the outer diameter surface of the valve seat. The vertical rib is located on the inner outlet side, and its lower part is connected to the bottom of the annular groove. The two side surfaces of the vertical rib are two vertical arc surfaces, and one side edge of the two arc surfaces on both sides is tangent to the outer diameter surface of the valve seat to form a wide bottom side, and the other side edges of the two arc surfaces on both sides intersect to form an end with a small arc angle. The vertical rib is used to guide the streamlines of the two flows in the annular groove to the inner outlet.

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