High performance valve with composite throttling structure

Abstract

A high-performance valve with a composite throttling structure includes a valve body, a valve seat, and a valve core. The valve core has a flow channel in its center and a groove on its surface. The key feature is that both the outer and inner surfaces of the valve core are provided with throttling units. This invention enables a unique valve structure that achieves extremely low flow resistance at large openings and extremely high flow resistance at small openings. It achieves excellent flow control characteristics and resistance to erosion and cavitation across the entire opening range. This high-performance multi-stage throttling valve with strong particle control extends the valve's controllable range and performance to a wider extent.

Description

Technical Field

[0001] This invention belongs to the field of fluid control equipment, and particularly relates to throttling structure valves. Background Technology

[0002] Ball valves are used for fluid regulation and control. Hard-seal V-type ball valves, with their V-shaped ball core and hard alloy-faced metal seat, possess strong shearing force, making them particularly suitable for media containing fibers and small solid particles. When a ball valve is fully open, the passage is equivalent to a straight pipe section, minimizing fluid resistance. Furthermore, the seat and ball are not exposed to the flowing medium, thus ball valves in the fully open state experience virtually no wear or erosion. However, at smaller openings, or when there is leakage between the valve core and seat, the valve core directly faces a significant fluid pressure differential, resulting in poor erosion resistance.

[0003] Currently, valves employing spherical double-groove throttling (such as patent number: US4881718A, etc.) Figure 1 and Figure 2 Its advantages include good linearity of flow control at small openings, enabling smooth control of extremely small flow rates, high stability, strong particle throughput, and strong resistance to erosion due to the flow guide groove guiding the fluid through the throttling orifice. It breaks away from the traditional 90-degree full-stroke design of angle-stroke valves, increasing the stroke and using a longer throttling channel structure, resulting in more stable adjustment performance at small openings. The full stroke can reach 90-150 degrees, or even higher. The double-groove design (one in front and one behind) enables multi-stage throttling. However, its disadvantages include poor resistance to erosion at large openings, an insufficiently smooth transition between the grooved flow channel and the straight flow channel with sharp corners, and a tendency for abrupt changes in the flow curve and flow field, leading to poor control performance. This limits the valve's maximum usable opening and adjustment ratio, making it difficult to meet the requirements for fine control of large flow rates and resistance to erosion at large openings.

[0004] Currently, valves employing double V-shaped orifice throttling (such as patent number: US5524863A, etc.) Figure 3 and Figure 4 Its advantages lie in its large flow cross-section, low flow resistance, and strong flow capacity at large openings. When fully open, it can match the pipe diameter, allowing for strong particle passage. It also allows for complete pipe diameter passage, facilitating the passage of pigging equipment. The double-layer V-shaped throttling (one before and one after) enables multi-stage throttling. However, its disadvantages include difficulty in designing a smoother Cv curve and achieving smaller flow control at small openings. Furthermore, at small openings, the angle between the fluid flow direction and the throttling surface is relatively large (90 degrees), making the throttling orifice susceptible to particle erosion and reducing its erosion resistance; particles can easily become stuck in the orifice. When the opening exceeds 80%, the flow rapidly transitions to a circular state upon reaching the throttling orifice, causing a decrease in regulating performance. The patented design limits the opening range to 0-90 degrees.

[0005] Existing technologies have limitations in the slots opened on the valve core. They all use a single method and it is difficult to simultaneously achieve good flow control linearity at small openings, customizable Cv curves, high stability, strong particle throughput, and strong erosion resistance, as well as large flow cross-section, low flow resistance, and strong flow capacity at large openings.

[0006] In addition, optimizing the anti-erosion performance of ball valves throughout their entire stroke and providing a valve core structure with excellent overall performance across the entire opening stroke are technical challenges that urgently need to be addressed in this field. Summary of the Invention

[0007] The purpose of this invention is to provide a high-performance valve with a composite throttling structure, which can realize three-dimensional variable multi-stage throttling and solve the technical problem of insufficient linearity of flow control at small openings.

[0008] To achieve the above objectives, the specific technical solution of the present invention is as follows: A high-performance valve with a composite throttling structure includes a valve body, a valve seat, and a valve core. The valve core has a flow channel in the middle and a slot on its surface. A front valve seat and a rear valve seat are provided at both ends of the valve core. The valve core is characterized in that both its outer and inner surfaces are provided with throttling units, and the front and rear valve seats are fixed to the valve body by a front fixing ring and a rear fixing ring, respectively. The front valve seat, valve core, and rear valve seat constitute a complete throttling structure.

[0009] Furthermore, the throttling unit is disposed at both ends of the flow channel of the valve core; The throttling unit includes a first throttling unit disposed on the outer surface of the valve core near the front valve seat and a second throttling unit disposed on the inner surface of the flow channel, and a fourth throttling unit disposed on the outer surface of the valve core near the rear valve seat and a fifth throttling unit disposed on the inner surface of the flow channel. As the valve core rotates within the valve body, the angle between the flow channel and the central axis of the pipeline where the valve is located forms a third throttling unit.

[0010] Furthermore, the first and second throttling units, as well as the fourth and fifth throttling units, are connected by transition zones, so that the throttling units extend continuously and gradually from the outer surface of the valve core to the inner surface of the valve core's flow channel, and then, through the third throttling unit, extend continuously and gradually from the inner surface of the valve core's flow channel to the outer surface of the valve core.

[0011] Furthermore, the throttling units are centrally symmetrically distributed at both ends of the valve core.

[0012] Furthermore, the size of the throttling surface of the throttling unit changes continuously with the change of the valve core opening. The throttling surface gradually increases in the first half of the valve core opening and gradually decreases in the first and second halves of the valve core opening.

[0013] Furthermore, the first throttling unit, the second throttling unit, the fourth throttling unit, and the fifth throttling unit are grooves, and the opening size and depth of the grooves gradually increase towards the end of the flow channel, while the opening size and depth of the grooves gradually decrease towards the center of the inner surface of the flow channel and towards the outer surface of the valve core away from the end of the flow channel.

[0014] Furthermore, the valve core is spherical, cylindrical, frustum-shaped, or conical.

[0015] Furthermore, the groove is a V-shaped groove, a U-shaped groove, or a T-shaped groove, and a guide groove is provided at the bottom of the groove.

[0016] In practical applications of valves, under the same differential pressure, the ratio of the maximum flow rate (Qmax) to the minimum flow rate (Qmin) that a valve can stably control is called the turnability ratio, usually denoted by R (R=Qmax / Qmin). The turnability ratio of a valve directly reflects the range of its regulating capacity, and it is determined by the valve's original structural design. It is an important parameter for measuring valve performance; the larger the ratio, the wider the flow rate regulation range and the better the performance.

[0017] Under normal circumstances, the ideal adjustable ratio is usually 30:1. However, the adjustable ratio of special valves such as V-type ball valves and eccentric rotary valves designed for low flow conditions can be higher. However, single-stage throttling, large pressure difference before and after the throttling orifice, high medium flow velocity, and high pressure recovery coefficient (when the flow velocity increases, the pressure decreases, the flow velocity decreases, the pressure recovers, cavitation occurs when the pressure drops below the saturated vapor pressure of the medium, and flashing occurs when the pressure recovers above the saturated vapor pressure), makes them prone to cavitation and flashing, and their erosion resistance is poor.

[0018] The new type of valve features multi-stage throttling, which allows for higher flow resistance compared to traditional V-type ball valves (single-seat throttling), thus enabling a higher turn-up ratio. Multi-stage throttling gradually consumes the energy of the medium within a longer throttling channel, resulting in a low pressure recovery coefficient and strong resistance to differential pressure. It is suitable for applications requiring high differential pressure throttling and a high turn-up ratio.

[0019] The technical solution of the present invention has the following advantages: A special valve structure enables extremely low flow resistance at large openings and extremely high flow resistance at small openings. It achieves excellent flow control characteristics and resistance to erosion, cavitation, and particulate matter throughout the full opening range. This high-performance, multi-stage throttling valve extends the controllable range and performance of the valve to a wider extent.

[0020] The valve's adjustable ratio (R) has been increased from 30-100:1 in the traditional single structure to 500-1000:1. Combined with the current advancements in valve positioning technology, in many situations where fluid parameters are uncertain and a wide adjustable ratio is required for precise control, the customized characteristic curve can better adapt to the needs and meet the requirements for erosion resistance, anti-clogging, and high pressure differential. In practical applications, it can match more field operating conditions.

[0021] The Cv curve can be customized according to the operating conditions, and the curve change rate of throttling can be reasonably allocated. It can achieve superlogarithmic characteristics, with very slow flow change at small openings for high-precision control and very fast flow change at large openings for high-speed response. Attached Figure Description

[0022] Figure 1 A cross-sectional structural diagram of patent US4881718A; Figure 2 A structural schematic diagram of patent US4881718A; Figure 3 A schematic diagram of the structure of patent US5524863A; Figure 4 A cross-sectional structural diagram of patent US5524863A; Figure 5 This is a schematic diagram of the valve core in the fully closed state of the present invention; Figure 6 This is a schematic diagram of the valve core in its small opening state according to the present invention; Figure 7 This is a schematic diagram of the valve core's opening state structure according to the present invention; Figure 8 This is a schematic diagram of the valve core in its large opening state according to the present invention; Figure 9 This is a schematic diagram of the valve core in the fully open state of the present invention; Figure 10 This is a schematic cross-sectional view of the valve core of the present invention; Figure 11 This is a three-dimensional structural diagram of the valve core of the present invention from the B-view perspective; Figure 12 The Cv curves of the valve are shown for three different slot sizes in the valve core. Detailed Implementation

[0023] To better understand the purpose, structure, and function of this invention, the invention will be described in further detail below with reference to the accompanying drawings.

[0024] Example 1

[0025] like Figure 5 , Figure 10 , Figure 11As shown, the high-performance valve with a composite throttling structure of the present invention includes a valve body 1, a valve seat, and a valve core 4. A flow channel 15 is provided in the middle of the valve core 4, and slots are provided on the surface of the valve core 4 at the front and rear ends of the flow channel 15. A front valve seat 3 and a rear valve seat 5 are provided at both ends of the valve core 4. Throttling units are provided on both the outer and inner surfaces of the valve core 4. The front valve seat 3 and the rear valve seat 5 are fixed to the valve body 1 by a front fixing ring 2 and a rear fixing ring 6, respectively. The front valve seat 3, the valve core 4, and the rear valve seat 5 constitute a complete throttling structure.

[0026] Specifically, the throttling units are located at both ends of the flow channel 15 of the valve core 4, including a first throttling unit 12 located on the outer surface of the valve core 4 near the front valve seat 3 and a second throttling unit 14 located on the inner surface of the flow channel 15, as well as a fourth throttling unit 16 located on the outer surface of the valve core 4 near the rear valve seat 5 and a fifth throttling unit 18 located on the inner surface of the flow channel 15.

[0027] As the valve core 4 rotates within the valve body 1, the angle between the flow channel 15 and the central axis of the pipeline where the valve is located forms a third throttling unit. That is, the flow channel 15 deforms to form a third throttling unit. The third throttling unit is the channel (flow channel 15) within the valve core 4. As the opening changes, the angle between the flow channel 15 and the fluid direction changes, further resulting in changes in the flow resistance of the fluid passing through the valve.

[0028] To further optimize the flow control linearity of the valve at small openings, a transition interval 13 is provided between the first throttling unit 12 and the second throttling unit 14, and a transition interval 17 is provided between the fourth throttling unit 16 and the fifth throttling unit 18. This allows the throttling units to extend continuously and gradually from the outer surface of the valve core 4 to the inner surface of the flow channel 15 of the valve core 4, and after passing through the third throttling unit, to extend continuously and gradually from the inner surface of the flow channel 15 of the valve core 4 back to the outer surface of the valve core 4.

[0029] When the valve opening is between transition zone 13 and transition zone 17, the spherical groove of valve core 4 works together with the first throttling unit 12 and the second throttling unit 14. Through its unique geometric shape connection design, it ensures that the flow characteristic curve is smooth and continuous without inflection points or sudden changes. In this application, transition zone 13 and transition zone 17 play a role in smoothing the transition of valve opening.

[0030] Simultaneously, transition zones 13 and 17 also achieve fluid reversal, allowing the throttling unit to extend continuously and gradually from the outer surface of the valve core 4 to the inner surface of the flow channel 15 of the valve core 4. The third throttling unit causes the fluid to reverse again by changing the angle between the flow channel 15 and the pipe axis. The fourth throttling unit 16 to the fifth throttling unit 18 achieve fluid reversal once more, allowing the throttling unit to extend continuously and gradually from the inner surface of the flow channel 15 of the valve core 4 to the outer surface of the valve core 4.

[0031] It can be seen that the first throttling unit 12, the transition zone 13, the second throttling unit 14, the fourth throttling unit 16, the transition zone 17, and the fifth throttling unit 18 are centrally symmetrically distributed at both ends of the valve core 4.

[0032] Example 2

[0033] In this embodiment, the first throttling unit 12, the second throttling unit 14, the fourth throttling unit 16 and the fifth throttling unit 18 are grooves, and the opening size and depth of the grooves gradually increase towards the end of the flow channel 15, while the opening size and depth of the grooves gradually decrease towards the center of the inner surface of the flow channel 15 and the outer surface of the valve core 4 away from the end of the flow channel 15.

[0034] The size of the throttling surface that ultimately forms the throttling unit changes continuously with the opening degree of valve core 4, and the increase in the throttling unit is a continuous transition with the increase in opening degree. The throttling surface gradually increases in the first half of the valve core 4 opening, and gradually decreases in the first and last half of the valve core 4 opening.

[0035] By controlling the depth and width of the groove, the continuity and consistency of the Cv curve can be controlled, further realizing three-dimensional variable multi-stage throttling.

[0036] Example 3

[0037] In this embodiment, the valve core 4 is spherical. The valve core is not limited to spherical, but also includes cylindrical, cylindrical with a larger top and smaller bottom, cylindrical with a smaller top and larger bottom, and conical.

[0038] Example 4

[0039] In this embodiment, the groove can be a V-shaped groove, a U-shaped groove, a T-shaped groove, or an irregular groove, and a guide groove is provided at the bottom of the groove.

[0040] Example 5

[0041] In this embodiment, a flow guide groove is provided at the bottom of the groove. The flow guide groove serves to pre-guide the liquid to the inner flow channel 15 of the valve core 4 in the small opening range. In valves without a flow guide groove, the valve seat and ball valve will directly resist throttling. Pre-reversal reduces scouring and improves the scouring resistance of the ball valve for regulating flow.

[0042] Example 1 - Valve fully closed like Figure 5As shown, valve core 4 is in the fully closed state. At this time, fluid enters from the front end 10 of the front fixed ring 2, passes through the guide groove of valve seat 3, and the sealing surfaces between the front valve seat 3, the rear valve seat 5 and the valve core 4 are cut off, preventing fluid flow. The first throttling unit 12, the transition zone 13, the second throttling unit 14, the flow channel 15, the fourth throttling unit 16, the transition zone 17, and the fifth throttling unit 18 formed by the throttling unit constitute an S-shape (maximum flow resistance) at an obtuse angle to the fluid flow direction, and the S-shape of the flow channel is in its maximum state.

[0043] Example 2 - Valve operating at small opening like Figure 6 As shown, valve core 4 is in a small opening state. The flow path of the medium within the valve is S-shaped, passing through five throttling units successively: the front fixed annular flow channel 10, the front valve seat flow channel 11, the first throttling unit 12, the transition zone 13, the second throttling unit 14, the flow channel 15, the fourth throttling unit 16, the transition zone 17, the fifth throttling unit 18, the rear valve seat flow channel 19, and the rear fixed annular flow channel 20. Among them, the throttling orifices formed by the first throttling unit 12 and the fifth throttling unit 18 and the valve seat together play the main throttling role. The third throttling unit (flow channel 15) has a large angle with the central axis of the pipeline (i.e., the direction of fluid flow), which is close to perpendicular, resulting in a large flow resistance and also playing a throttling role. The second throttling unit 14 and the fourth throttling unit 18 mainly play a guiding role. At this time, the fluid flow path is a sharp S-shape, with the highest spatial curvature of the flow path.

[0044] In the S-shaped throttling channel formed in this application example, the flow channel 15 in the valve core 4 is nearly perpendicular to the fluid flow direction, resulting in a large flow resistance. This forms a five-stage three-dimensional throttling space that gradually increases and then gradually decreases. In this space that gradually increases and decreases, the flow velocity of the medium gradually decreases, and the pressure is gradually lost, which plays a good role in throttling the medium and dispersing the pressure difference in multiple stages.

[0045] The specific 5-level throttling is as follows: small opening 5-level throttling (including: first throttling unit 12, second throttling unit 14, flow channel 15, fourth throttling unit 16, and fifth throttling unit 18).

[0046] Example 3 - Valve at medium opening like Figure 7As shown, valve core 4 is in the middle opening position. At this time, the medium flows through the valve in an S-shape, passing through three throttling units: transition zone 13, second throttling unit 14, flow channel 15, fourth throttling unit 16, and transition zone 17. The initial throttling is mainly achieved by the transition zone between the first and second throttling units and the throttling orifice formed by the front valve seat. The third throttling unit has a certain angle with the pipeline axis, significantly reducing the flow resistance and thus achieving a certain throttling effect. The subsequent throttling is mainly achieved by the transition zone between the fourth and fifth throttling units and the throttling orifice formed by the rear valve seat. At this point, the fluid flow path gradually changes from a sharp S-shape to a gentler S-shape, and the spatial curvature of the flow path begins to flatten. This transition control is extremely difficult, and turbulence can easily occur, disrupting the flow field stability and thus affecting the throttling stability.

[0047] Medium opening, 3-level throttling (transition zone 13, flow channel 15, transition zone 17).

[0048] Example 4 - Valve Opening at Maximum Degree like Figure 8 As shown, valve core 4 is in a fully open state. At this time, the flow path of the medium within the valve is nearly straight, passing through two throttling units successively: the second throttling unit 14, the flow path 15, and the fourth throttling unit 16. The initial throttling is mainly achieved by the throttling orifice formed by the second throttling unit and the front valve seat. The third throttling unit in the middle section has a very small angle with the central axis of the pipeline and has virtually no throttling effect. The subsequent throttling is mainly achieved by the throttling orifice formed by the fourth throttling unit and the rear valve seat. At this point, the fluid flow path is nearly straight, and the curvature of the flow path space has essentially disappeared.

[0049] Large opening, two-stage throttling (second throttling unit 14, fourth throttling unit 16).

[0050] It should be noted that when the opening is small, the throttling unit area is a double groove that forms two main throttling ports with the valve seat 3 and the rear valve seat 5.

[0051] When the opening is large, the throttling unit area is a double V-shaped port, which together with valve seat 3 and valve seat 5 form two main throttling ports. The two main throttling ports gradually rotate in an S-shaped space as the opening increases, eventually becoming perpendicular to the flow direction. Furthermore, the throttling area of ​​the main throttling ports gradually increases as the opening increases.

[0052] Example 5 - Valve fully open like Figure 9 As shown, valve core 4 is in the fully open state. At this time, the flow path of the medium inside the valve is straight. The third throttling unit mainly plays a throttling role. The angle between the third throttling unit and the central axis of the pipe is zero. The throttling effect of the third throttling unit is consistent with that of a pipe of the same diameter, achieving the minimum throttling resistance for pipes of the same diameter. At this time, the fluid flow path is straight, and the curvature of the flow path space completely disappears.

[0053] When fully open, it is a level 1 throttling (straight-through flow channel). As can be seen, during the valve's adjustment process from fully closed to fully open, a three-dimensional variable flow channel is formed. Not only do the two throttling orifices participate in throttling, but the three-dimensional variable flow channel also participates. Furthermore, the three throttling orifices gradually converge as the opening increases, finally merging into a single throttling orifice at full open. This achieves multi-stage throttling in three-dimensional space, with maximum flow resistance at small openings and minimum flow resistance at full open. The entire process is within a window throttling state, with a concentrated throttling area, facilitating the passage of particulate media. The guide channel prevents particulate media from accumulating at the throttling orifices, providing a self-cleaning function. Controllable, variable, multi-stage throttling is achieved throughout the entire stroke.

[0054] As can be seen from the attached figures, the valve core of this application has a wide opening stroke of 4 degrees, which breaks through the existing design concept of 90-degree full stroke of angular stroke valve.

[0055] It can operate within a wider stroke angle range, for example, a full stroke of 135 degrees, with 0-10 degrees for sealing, 10-70 degrees for external double-groove throttling, 70-90 degrees for curved surface transition, and 90-135 degrees for internal double-groove throttling. A longer control stroke is achieved structurally without compromising throttling performance.

[0056] Experimental example: like Figure 12 As shown, the X-axis represents the valve opening degree, and the Y-axis represents the Cv value.

[0057] It can be seen that, Figure 12 The DN76 valves with three different slotted structures (different external grooves and internal slotted flow channels, with different slot depths and widths) of this application were tested, and three different flow characteristic Cv curves (A, B, and C) were measured. Among them, curve A achieved superlogarithmic characteristics that most valves cannot achieve, solving many problems in the field of fluid control. Figure 10 Compared with existing valves, the technical solution proposed in this application has a larger opening range, stronger control force in the small opening range, and a larger limit for the Cv curve.

[0058] As the valve core 4 rotates, a smooth change in the throttling surface between the valve seat and the valve core 4 is achieved in space, resulting in a controllable transition. This avoids the throttling surface exceeding the preset curve characteristics and also prevents sudden changes and unexpected turbulence. The flow field does not experience large fluctuations or a decrease in stability during the transition. Furthermore, by controlling the width, angle, and shape of each groove, different flow characteristics can be obtained, allowing for further customization of different Cv curves.

[0059] Compared to traditional plunger-type control valves, this type of valve is a circumferential throttling valve (the throttling area between the valve core and the valve seat is a circular ring). In this technical solution, the throttling channels formed between the valve seat and the ball core are concentrated together, with one at the front and one at the back, of the same size but in opposite directions, forming a gradually increasing V-shaped slide. Particles are unlikely to get stuck in the throttling channels, and particles that are blocked in the throttling orifice can easily pass through due to the increased valve opening and larger window.

[0060] In practical applications of the technical solution of this application: On the one hand, the gradually increasing throttling channel (the gradually increasing groove) is itself an expanding throttling space. In this space, the flow velocity in the central part is high and the flow velocity at the edge is low. Moreover, as the flow channel expands, it is not a sudden expansion after the throttling of a traditional valve. This expansion is gradually and orderly expanded with the V-groove, forming a pressure drop gradient (not a sudden decrease in velocity as in the traditional case). The acceleration of the fluid in the expanding flow channel is poor, and the flow velocity will drop rapidly. This is a commonly used theory in high differential pressure valves with labyrinth structures.

[0061] On the other hand, the presence of two throttling channels at the beginning and end, along with a gradually changing S-shaped flow path, creates three or more stages of throttling. The advantage of multi-stage throttling is that the pressure difference is shared across multiple stages. With a smaller pressure difference at each stage, the fluid is less likely to experience sudden and drastic pressure drops, making it less prone to falling below the saturated vapor pressure and thus less susceptible to flash cavitation. Simultaneously, multi-stage throttling lengthens the pressure drop distance, significantly reducing the fluid velocity—approximately 40% compared to a traditional single-stage throttling structure—thus reducing the intensity of erosion damage and improving erosion resistance.

[0062] Cavitation is also an important phenomenon affecting valves.

[0063] 1. Cavitation can cause noise and vibration when fluid passes through a valve, affecting the valve's operational stability and service life.

[0064] 2. This will cause the fluid to flow faster when passing through the valve, resulting in pressure fluctuations and reducing the accuracy of flow and pressure control.

[0065] 3. This causes erosion and wear on the metal surface inside the valve.

[0066] 4. This causes air bubbles and cavities in the fluid near the valve, affecting the fluid's quality and flow performance.

[0067] The technical solution of this application, through multi-stage throttling, lengthens the flow channel and also extends the pressure drop distance, significantly reducing the fluid velocity and effectively controlling the fluid speed to avoid cavitation caused by excessive flow velocity.

[0068] The cross-sectional surface of the transition zone throttling orifice gradually flips from the double groove direction to the double V-shaped throttling orifice. The middle flipped part maintains a smooth R angle. The two V-shaped wings realize that the S-shaped flow channel gradually becomes smoother as the opening increases, and the flow resistance gradually decreases, forming a three-dimensional variable damping flow channel with gradually decreasing flow resistance as the opening increases.

[0069] The cross-sectional surface of the transition zone throttling orifice gradually flips from the double groove direction to the double groove type throttling orifice. The middle flipping part gradually transitions, and the two wings of the groove type realize that the S-shaped flow channel gradually becomes smooth as the opening increases, and the flow resistance gradually decreases, forming a three-dimensional variable damping flow channel with the flow resistance gradually decreasing as the opening increases.

[0070] It is understood that the present invention has been described through some embodiments, and those skilled in the art will recognize that various changes or equivalent substitutions can be made to these features and embodiments without departing from the spirit and scope of the invention. Furthermore, under the teachings of the present invention, these features and embodiments can be modified to adapt to specific situations and materials without departing from the spirit and scope of the invention. Therefore, the present invention is not limited to the specific embodiments disclosed herein, and all embodiments falling within the scope of the claims of this application are within the protection scope of the present invention.

Claims

1. A high-performance valve with a composite throttling structure, comprising a valve body (1), a valve seat, and a valve core (4), wherein the valve core (4) has a flow channel (15) in the middle, a groove is provided on the surface of the valve core (4), and a front valve seat (3) and a rear valve seat (5) are provided at both ends of the valve core (4), characterized in that, The valve core (4) is provided with throttling units on both its outer and inner surfaces. The front valve seat (3) and the rear valve seat (5) are fixed to the valve body (1) by the front fixing ring (2) and the rear fixing ring (6), respectively. The front valve seat (3), valve core (4) and rear valve seat (5) constitute a complete throttling structure.

2. The high-performance valve with a composite throttling structure according to claim 1, characterized in that, The throttling unit is disposed at both ends of the flow channel (15) of the valve core (4); The throttling unit includes a first throttling unit disposed on the outer surface of the valve core (4) near the front valve seat (3) and a second throttling unit disposed on the inner surface of the flow channel (15), and a fourth throttling unit disposed on the outer surface of the valve core (4) near the rear valve seat (5) and a fifth throttling unit disposed on the inner surface of the flow channel (15). As the valve core (4) rotates in the valve body (1), the angle between the flow channel (15) and the central axis of the pipeline where the valve is located forms a third throttling unit.

3. The high-performance valve with a composite throttling structure according to claim 2, characterized in that, The first throttling unit and the second throttling unit, as well as the fourth throttling unit and the fifth throttling unit, are connected by a transition zone, so that the throttling unit extends continuously and gradually from the outer surface of the valve core (4) to the inner surface of the flow channel (15) of the valve core (4), and then extends continuously and gradually from the inner surface of the flow channel (15) of the valve core (4) to the outer surface of the valve core (4) through the third throttling unit.

4. The high-performance valve with a composite throttling structure according to claim 3, characterized in that, The throttling units are centrally symmetrically distributed at both ends of the valve core (4).

5. The high-performance valve with a composite throttling structure according to claim 4, characterized in that, The size of the throttling surface of the throttling unit changes continuously with the opening of the valve core (4). The throttling surface gradually increases in the first half of the valve core (4) opening and gradually decreases in the first and second halves of the valve core (4) opening.

6. The high-performance valve with a composite throttling structure according to claim 5, characterized in that, The first throttling unit, the second throttling unit, the fourth throttling unit and the fifth throttling unit are grooves, and the size and depth of the groove opening gradually increase towards the end of the flow channel (15), and the size and depth of the groove opening gradually decrease towards the center of the inner surface of the flow channel (15) and the outer surface of the valve core (4) away from the end of the flow channel (15).

7. The high-performance valve with a composite throttling structure according to claim 6, characterized in that, The valve core (4) is spherical, cylindrical, frustum cylindrical or conical.

8. The high-performance valve with a composite throttling structure according to claim 7, characterized in that, The groove is a V-shaped groove, a U-shaped groove, or a T-shaped groove, and a guide groove is provided at the bottom of the groove.

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