Abrasion-proof large-diameter ball valve

Abstract

The invention relates to the technical field of valves, in particular to an anti-abrasion large-diameter ball valve which comprises a valve body and a main valve element, a valve cavity is formed in the valve body, a liquid inlet is formed in one end of the valve body, two liquid outlets are formed in the other end of the valve body, one liquid outlet and the liquid inlet are coaxial, and an included angle is formed between the other liquid outlet and the axis of the liquid inlet. The main valve element is rotationally arranged in the valve cavity. The main valve element is arranged, and the first spherical surface, the second spherical surface and the third spherical surface of the main valve element are concentric spherical surfaces, so that stress concentration points cannot be formed on the circumferences of the first spherical surface, the second spherical surface and the third spherical surface due to the fact that the main valve element bears recoil force; therefore, the problem that the sealing element between the main valve element and the valve cavity is deflected and abraded due to non-uniform circumferential stress and then leaks can be effectively solved, and the purpose of prolonging the service life of the sealing element is achieved.

Description

Technical Field

[0001] This invention relates to the field of valve technology, and in particular to a wear-resistant large-diameter ball valve. Background Technology

[0002] Ball valves are a commonly used type of valve in pipeline fluid control. Their opening and closing element is a ball, which is driven by the valve stem and rotates around the axis to achieve on / off / reversal.

[0003] Ball valves can be divided into three main categories based on the shape of their valve cores: complete ball valves, main valve core ball valves, and eccentric hemispherical ball valves. Among them, main valve core ball valves have significant advantages over conventional complete ball valves in terms of operating torque, flow resistance, and sealing stability. They can be adapted to harsh industrial conditions, which is the core reason why they replace conventional ball valves in large-diameter (DN500 and above) and high-pressure (PN100 and above) projects.

[0004] However, the main valve core ball valve also has certain drawbacks: because the ball system is not a centrally symmetrical body, when the non-linear channel is connected, the fluid generates a backlash force on the main valve core. This backlash force causes the sealing force of the valve seat to be unevenly distributed along the circumference of the fluid channel, which can easily cause the seal to wear and become misaligned, leading to leakage. Summary of the Invention

[0005] Therefore, it is necessary to provide a wear-resistant, large-diameter ball valve to address the problems existing in current ball valves, which can easily cause misalignment and wear of the seals, leading to leakage.

[0006] The above objectives are achieved through the following technical solutions: A wear-resistant large-diameter ball valve includes: The valve body has a valve chamber inside; The liquid inlet is located at one end of the valve body; Two liquid outlets are located at the other end of the valve body. One liquid outlet is coaxial with the liquid inlet, and the other liquid outlet is arranged at an angle to the axis of the liquid inlet. The main valve core is rotatably disposed in the valve cavity and has a first, second and third spherical surface that are spaced apart and concentric along the rotation axis. The first, second and third spherical surfaces are all slidably sealed in the valve cavity, with the first spherical surface facing the liquid outlet and the second and third spherical surfaces facing the liquid inlet. The main valve core has a first state and a second state. In the first state, the inlet and outlet of the coaxial axis are connected through the main valve core. In the second state, the inlet and outlet of the axis are connected through the main valve core.

[0007] Preferably, a hard sealing ring is embedded in both the first and second spherical surfaces, and the end of the hard sealing ring facing the cavity wall of the valve cavity is an arc surface and is slidably connected to the cavity wall of the valve cavity.

[0008] Preferably, a secondary valve core is rotatably provided inside the valve cavity and near the liquid inlet. The rotation axis of the secondary valve core coincides with that of the main valve core, and the secondary valve core is configured to rotate synchronously with the main valve core around the rotation axis.

[0009] Preferably, the secondary valve core has a fourth spherical surface at the end facing the main valve core. The fourth spherical surface is concentric with the third spherical surface, and a transmission column is eccentrically arranged on the spherical surface. The axis of the transmission column is arranged at an angle to the rotation axis of the secondary valve core. A transmission groove is eccentrically arranged on the third spherical surface. The width of the transmission groove is adapted to the diameter of the transmission column, and the transmission groove and the transmission column cooperate with each other.

[0010] Preferably, the transmission groove is an oblong groove, and there is a preset distance between the fourth spherical surface and the third spherical surface.

[0011] Preferably, the end of the secondary valve core away from the fourth spherical surface is sealed on the cavity wall of the valve chamber.

[0012] Preferably, the valve body is provided with a rotating pin on its external rotation. The rotating pin is coaxial with the main valve core and is inserted into the main valve core, and the two are configured to rotate synchronously.

[0013] Preferably, a packing gland is also provided on the outside of the valve body, and a sealed chamber for accommodating packing is formed between the packing gland and the valve body. The packing gland is sleeved on the outside of the rotating pin, and the packing gland is configured to rotate relative to the rotating pin.

[0014] Preferably, a valve support seat is also provided inside the valve cavity to support the main valve core.

[0015] Preferably, a first bearing is also provided inside the valve cavity, and the first bearing is sleeved on the outside of the main valve body.

[0016] The beneficial effects of this invention are: This invention features a main valve core. Because the first, second, and third spherical surfaces of the main valve core are concentric, they do not form stress concentration points on their circumference due to the recoil force acting on the main valve core. This means the sealing force on the main valve core is uniformly distributed along the circumference of the fluid channel. In contrast, in existing technologies, the first and third spherical surfaces of the main valve core are not concentric, causing stress concentration points on their circumference due to the recoil force acting on the main valve core. This results in a non-uniform distribution of the sealing force on the main valve core along the circumference of the fluid channel. Consequently, the seal between the main valve core and the valve cavity is prone to wear due to localized stress concentration. Therefore, this invention effectively solves the problem of leakage caused by uneven circumferential force on the seal between the main valve core and the valve cavity, thus extending the service life of the seal. Attached Figure Description

[0017] Figure 1 This is an overall schematic diagram of a wear-resistant large-diameter ball valve according to the present invention; Figure 2 for Figure 1 Top view; Figure 3 for Figure 2 Sectional view of AA; Figure 4 This is a schematic diagram of the second state of the main valve core in a wear-resistant large-diameter ball valve according to the present invention; Figure 5 for Figure 4 A magnified schematic diagram of the structure at point B in the middle; Figure 6 This is a schematic diagram of the main valve core in a wear-resistant large-diameter ball valve according to the present invention; Figure 7 This is a schematic diagram of the secondary valve core in a wear-resistant large-diameter ball valve according to the present invention.

[0018] in: 100. Valve body; 110. Valve chamber; 101. Liquid inlet; 102. Liquid outlet; 200. Main valve core; 210. First spherical surface; 220. Second spherical surface; 230. Third spherical surface; 231. Transmission groove; 300. Hard sealing ring; 400, secondary valve core; 410, fourth spherical surface; 420, transmission column; 500. Rotating pin; 510. Packing gland; 600. Support valve seat; 700. First bearing; 800, Second Bearing. Detailed Implementation

[0019] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below through embodiments and in conjunction with the accompanying drawings. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.

[0020] The component designations used in this document, such as "first" and "second," are merely for distinguishing the described objects and do not have any sequential or technical meaning. The terms "connection" and "linkage" used in this invention, unless otherwise specified, include both direct and indirect connections (linkages). It should be understood that the terms "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," and "counterclockwise," indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings and are used only for the convenience of describing the invention and simplifying the description. They do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as limiting the invention.

[0021] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0022] like Figures 1 to 7 As shown, a wear-resistant large-diameter ball valve includes a valve body 100 and a main valve core 200. The valve body 100 has a valve cavity 110 inside. One end of the valve body 100 has an inlet 101, and the other end has two outlets 102. One outlet 102 is coaxial with the inlet 101, and the other outlet 102 is angled to the axis of the inlet 101. The main valve core 200 is rotatably mounted within the valve cavity 110. The main valve core 200 has a first spherical surface 210, a second spherical surface 220, and a third spherical surface 230 that are sequentially spaced and concentric along the rotation axis. The first spherical surface 210... 10. The second spherical surface 220 and the third spherical surface 230 are both slidably sealed in the valve cavity 110, and the first spherical surface 210 faces the liquid outlet 102, while the second spherical surface 220 and the third spherical surface 230 face the liquid inlet 101. The main valve core 200 is provided with a flow passage to connect the liquid inlet 101 and the liquid outlet 102. The main valve core 200 has a first state and a second state. In the first state, the coaxial liquid inlet 101 and liquid outlet 102 are connected through the main valve core 200. In the second state, the liquid inlet 101 and liquid outlet 102, whose axes are arranged at an angle, are connected through the main valve core 200.

[0023] The main valve core 200 is in the first state, such as Figure 3As shown, at this time, the inlet 101 and outlet 102 of the coaxial line are connected through the main valve core 200. The fluid medium flows into the valve chamber 110 from the inlet 101, passes through the flow hole of the main valve core 200, and flows out from the outlet 102 of the coaxial line.

[0024] When the inlet 101 and outlet 102, whose axes are required to be at an angle, are connected through the main valve core 200, the main valve core 200 rotates circumferentially by a preset angle, such as... Figures 4-5 As shown, at this time, the main valve core 200 switches from the first state to the second state, and the fluid medium flows into the valve chamber 110 from the inlet 101, passes through the flow hole on the main valve core 200, and flows out from the outlet 102, which is configured at an angle to the axis.

[0025] When the main valve core 200 is in the second state, because the fluid channel is not straight but bends at the inlet 101 and the flow hole of the main valve core 200, the fluid medium generates a backlash force on the main valve core 200, causing it to tend to rotate. Since the first spherical surface 210, the second spherical surface 220, and the third spherical surface 230 of the main valve core 200 are concentric spherical surfaces, and these surfaces slide and seal against the cavity wall of the valve chamber 110, they will not form stress concentration points on their circumference due to the backlash force on the main valve core 200. Therefore, the seal between the main valve core 200 and the valve chamber 110 will not fail. The present invention addresses the problem of uneven circumferential stress. In the prior art, the first spherical surface 210 and the third spherical surface 230 of the main valve core 200 are non-concentric spherical surfaces. Therefore, stress concentration points will form on the circumference of the first spherical surface 210 and the third spherical surface 230 due to the recoil force of the main valve core 200. As a result, the sealing pressure formed between one end of the main valve core 200 and the valve cavity 110 will be unevenly distributed along the circumference of the fluid channel. At this time, the seal between the main valve core 200 and the valve cavity 110 is prone to skewed wear due to local stress concentration. Therefore, the present invention can effectively solve the problem of skewed wear of the seal between the main valve core 200 and the valve cavity 110 due to uneven circumferential stress, thereby extending the service life of the seal.

[0026] In a further embodiment, to allow the main valve core 200 to rotate within the valve cavity 110, such as... Figure 5 As shown, a first bearing 700 is provided on the cavity wall of the valve cavity 110. The axis of the first bearing 700 coincides with the rotation axis of the main valve core 200, and the inner ring of the first bearing 700 is fixedly sleeved on the outside of the main valve core 200.

[0027] The first bearing 700 provides support to offset some of the recoil force on the main valve core 200. However, this causes significant wear on the first bearing 700, affecting the coaxiality of its inner and outer rings. When the coaxiality of the inner and outer rings decreases, the main valve core 200 will slide slightly around the centers of the first spherical surface 210, the second spherical surface 220, and the third spherical surface 230 under the influence of recoil force. If the first spherical surface 210 and the third spherical surface 230 are not concentric at this time, then the first spherical surface 210 or... Stress concentration will form on the circumference of the seal between the third spherical surface 230 and the valve cavity 110, causing the seal to wear unevenly and fail. However, by making the first spherical surface 210 and the third spherical surface 230 concentric spherical surfaces, stress concentration on the circumference of the seal between the first spherical surface 210, the third spherical surface 230 and the valve cavity 110 can be avoided. At this time, the main valve core 200 slides with an approximately constant pressure relative to the seal at the first spherical surface 210 and the third spherical surface 230 to absorb the recoil force. Therefore, the seal will not fail due to uneven wear.

[0028] In a further embodiment, such as Figure 4 and Figure 5 As shown, a hard sealing ring 300 is embedded on both the first spherical surface 210 and the second spherical surface 220, and the end of the hard sealing ring 300 facing the cavity wall of the valve cavity 110 is an arc surface and is slidably connected to the cavity wall of the valve cavity 110.

[0029] A hard sealing ring 300 is provided to form a rigid guide support for the main valve core 200. When the coaxiality between the inner and outer rings of the first bearing 700 is reduced, the main valve core 200 is forced to rotate only slightly around the center of the first spherical surface 210, the second spherical surface 220 and the third spherical surface 230 under the action of the recoil force.

[0030] It should also be noted that the hard sealing ring 300 on the first spherical surface 210 and the hard sealing ring 300 on the second spherical surface 220 can cooperate with each other to limit the movement of the main valve core 200 in the direction of its rotation axis.

[0031] In a further embodiment, such as Figure 4As shown, a support valve seat 600 is also provided in the valve cavity 110. The support valve seat 600 is used to support the main valve core 200. Specifically, there are three support valve seats 600. One support valve seat 600 is located in the valve cavity 110 and is coaxial with the main valve core 200. The support valve seat 600 is slidably sealed with the third spherical surface 230. Another support valve seat 600 is located in the valve cavity 110 and is coaxial with one of the liquid outlets 102. The support valve seat 600 is slidably sealed with the first spherical surface 210. The last support valve seat 600 is located in the valve cavity 110 and is coaxial with another liquid outlet 102. The support valve seat 600 is slidably sealed with the first spherical surface 210.

[0032] In a further embodiment, such as Figure 3 As shown, the valve body 100 is externally rotatably provided with a rotating pin 500. The rotating pin 500 is coaxial with the main valve core 200, and the rotating pin 500 is inserted into the main valve core 200, and the two are configured to rotate synchronously.

[0033] When the main valve core 200 needs to switch from the first state to the second state, the operator rotates the rotating pin 500 clockwise by a preset angle. Since the rotating pin 500 is inserted into the main valve core 200 and configured to rotate synchronously, the rotating pin 500 drives the main valve core 200 to rotate synchronously, thereby changing the circumferential position of the flow hole on the main valve core 200. Conversely, when the main valve core 200 needs to switch from the second state to the first state, the operator simply rotates the rotating pin 500 in the opposite direction by a preset angle.

[0034] Understandably, due to the frictional force of the sliding seal between the support valve seat 600 and the main valve core 200, and the sliding seal between the hard sealing ring 300 and the main valve core 200, the main valve core 200 has a large rotational resistance. Therefore, the main valve core 200 will not rotate freely around its rotation axis due to the flow of the fluid medium.

[0035] In a further embodiment, such as Figure 3 As shown, a packing gland 510 is also provided on the outside of the valve body 100. A sealing chamber for accommodating packing is formed between the packing gland 510 and the valve body 100. The packing gland 510 is sleeved on the outside of the rotating pin 500 and is configured to rotate relative to the rotating pin 500.

[0036] A packing gland 510 is provided to form a sealing chamber outside the rotating pin 500 for accommodating packing. This allows sealing packing, such as flexible graphite, to be filled in the sealing chamber to prevent fluid medium from leaking outward along the axis of the rotating pin 500 and to prevent external impurities / moisture from entering the valve chamber 110.

[0037] In a further embodiment, such as Figure 3 and Figure 4 As shown, a secondary valve core 400 is rotatably provided inside the valve cavity 110 and near the liquid inlet 101. The rotation axis of the secondary valve core 400 coincides with that of the main valve core 200, and the secondary valve core 400 is configured to rotate synchronously with the main valve core 200 around the rotation axis.

[0038] Since the rotation axes of the auxiliary valve core 400 and the main valve core 200 coincide, and the auxiliary valve core 400 is configured to rotate synchronously with the main valve core 200 around the rotation axis, the auxiliary valve core 400 can rotate synchronously with the main valve core 200 when the main valve core 200 is rotated. In addition, since the auxiliary valve core 400 is located inside the valve cavity 110 and close to the inlet 101, the recoil force mainly impacts the auxiliary valve core 400. When the auxiliary valve core 400 is severely worn, it can be replaced without replacing the main valve core 200 at the same time, thus reducing maintenance and replacement costs.

[0039] It is understandable that if the part where the auxiliary valve core 400 is located is designed as a fixed part of the valve body 100, then when the main valve core 200 is in the first state or the second state, a dead zone area will inevitably be formed between the main valve core 200 and the valve body 100. At this time, the main valve core 200 will be subjected to additional water flow resistance, which will lead to increased wear of the main valve core 200.

[0040] In addition, since the third spherical surface 230 is a spherical surface and slides and seals with the valve cavity 110, if the part where the auxiliary valve core 400 is located is designed as a fixed part of the valve body 100, then when machining the valve cavity 110, the milling cutter needs to be inserted into the valve cavity 110 to machine a large spherical surface that matches the curvature of the spherical surface of the third spherical surface 230. At this time, the constraint of the cavity wall of the valve cavity 110 is not conducive to the milling cutter running along the optimal tool path, so the milling is more difficult and the machining accuracy is not easy to guarantee. However, if this part is designed as a detachable auxiliary valve core 400, this problem does not exist. This part can be machined and milled separately, so it is easier to machine and the machining accuracy is easier to guarantee.

[0041] Furthermore, such as Figure 4 As shown, in order to allow the secondary valve core 400 to rotate within the valve cavity 110, a second bearing 800 is provided within the valve cavity 110. The axis of the second bearing 800 coincides with the rotation axis of the secondary valve core 400, and the inner ring of the second bearing 800 is fixedly sleeved on the outside of the secondary valve core 400.

[0042] In a further embodiment, such as Figure 3 , Figure 6 and Figure 7As shown, the secondary valve core 400 has a fourth spherical surface 410 at one end facing the main valve core 200. The fourth spherical surface 410 is concentric with the third spherical surface 230, and a transmission column 420 is eccentrically arranged on the fourth spherical surface 410. The axis of the transmission column 420 is arranged at an angle to the rotation axis of the secondary valve core 400. A transmission groove 231 is eccentrically arranged on the third spherical surface 230. The width of the transmission groove 231 is adapted to the diameter of the transmission column 420, and the transmission groove 231 cooperates with the transmission column 420.

[0043] Since the transmission column 420 is eccentrically arranged on the fourth spherical surface 410 and the transmission groove 231 is eccentrically arranged on the third spherical surface 230, and the width of the transmission groove 231 is adapted to the diameter of the transmission column 420, and the transmission groove 231 cooperates with the transmission column 420, when the main valve core 200 rotates, the main valve core 200 can drive the auxiliary valve core 400 to rotate synchronously through the cooperation of the transmission groove 231 and the transmission column 420.

[0044] In a further embodiment, such as Figure 3 and Figure 6 As shown, the transmission groove 231 is an oblong groove, and there is a preset distance between the fourth spherical surface 410 and the third spherical surface 230.

[0045] When the main valve core 200 is in the second state, if the secondary valve core 400 is subjected to the back pressure of the fluid medium, and the coaxiality of the inner and outer rings of the second bearing 800 decreases at this time, the secondary valve core 400 can slide a certain distance along the length of the transmission groove 231. At this time, the impact force on the secondary valve core 400 will not be fully transmitted to the main valve core 200, which helps to reduce the magnitude of the impact force on the main valve core 200 and extend the service life of the seal between the main valve core 200 and the valve cavity 110.

[0046] In a further embodiment, such as Figure 4 As shown, the end of the secondary valve core 400 away from the fourth spherical surface 410 is sealed on the cavity wall of the valve cavity 110. Specifically, a hard sealing ring 300 is embedded on the end face of the secondary valve core 400 away from the fourth spherical surface 410. The end of the hard sealing ring 300 away from the secondary valve core 400 is attached to the cavity wall of the valve cavity 110, and the transmission column 420 abuts against the bottom of the transmission groove 231.

[0047] Under the action of the hard sealing ring 300, the transmission groove 231 and the transmission column 420, the auxiliary valve core 400 can be constrained to limit the movement of the auxiliary valve core 400 in the direction of its rotation axis.

[0048] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0049] The embodiments described above are merely illustrative of several implementations of the present invention, and while the descriptions are specific and detailed, they should not be construed as limiting the scope of the invention. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these modifications and improvements all fall within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the appended claims.

Claims

1. A wear-resistant large-diameter ball valve, characterized in that, include: The valve body has a valve chamber inside; The liquid inlet is located at one end of the valve body; Two liquid outlets are located at the other end of the valve body. One liquid outlet is coaxial with the liquid inlet, and the other liquid outlet is arranged at an angle to the axis of the liquid inlet. The main valve core is rotatably disposed in the valve cavity and has a first spherical surface, a second spherical surface, and a third spherical surface that are spaced apart and concentric along the rotation axis. The first spherical surface, the second spherical surface, and the third spherical surface are all slidably sealed in the valve cavity. The first spherical surface faces the liquid outlet, and the second and third spherical surfaces face the liquid inlet. The main valve core has a first state and a second state. In the first state, the inlet and outlet of the coaxial axis are connected through the main valve core. In the second state, the inlet and outlet of the axis are connected through the main valve core.

2. The wear-resistant large-diameter ball valve according to claim 1, characterized in that, Hard sealing rings are embedded in both the first and second spherical surfaces, and the end of the hard sealing ring facing the cavity wall of the valve cavity is an arc surface, which is slidably connected to the cavity wall of the valve cavity.

3. The wear-resistant large-diameter ball valve according to claim 1, characterized in that, A secondary valve core is rotatably installed inside the valve chamber and near the liquid inlet. The rotation axis of the secondary valve core coincides with that of the main valve core, and the secondary valve core is configured to rotate synchronously with the main valve core around the rotation axis.

4. The wear-resistant large-diameter ball valve according to claim 3, characterized in that, The secondary valve core has a fourth spherical surface at the end facing the main valve core. The fourth spherical surface is concentric with the third spherical surface, and a transmission column is eccentrically arranged on the spherical surface. The axis of the transmission column is arranged at an angle with the rotation axis of the secondary valve core. A transmission groove is eccentrically arranged on the third spherical surface. The width of the transmission groove is adapted to the diameter of the transmission column, and the transmission groove and the transmission column cooperate with each other.

5. A wear-resistant large-diameter ball valve according to claim 4, characterized in that, The transmission groove is an oblong groove, and there is a preset distance between the fourth spherical surface and the third spherical surface.

6. The wear-resistant large-diameter ball valve according to claim 4, characterized in that, The end of the secondary valve core furthest from the fourth spherical surface is sealed on the wall of the valve cavity.

7. The wear-resistant large-diameter ball valve according to claim 1, characterized in that, The valve body is externally rotatable with a rotating pin. The rotating pin is coaxial with the main valve core and is inserted into the main valve core, and the two are configured to rotate synchronously.

8. The wear-resistant large-diameter ball valve according to claim 7, characterized in that, A packing gland is also provided on the outside of the valve body. A sealed chamber for accommodating packing is formed between the packing gland and the valve body. The packing gland is sleeved on the outside of the rotating pin and is configured to rotate relative to the rotating pin.

9. A wear-resistant large-diameter ball valve according to claim 1, characterized in that, A valve support seat is also provided inside the valve cavity to support the main valve core.

10. A wear-resistant large-diameter ball valve according to claim 1, characterized in that, A first bearing is also installed inside the valve cavity, and the first bearing is sleeved on the outside of the main valve body.

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