Angle valve drive mechanism with overload protection clutch

Abstract

The application discloses an angular valve driving mechanism with overload protection clutch and relates to the technical field of angular valves. The 90-degree water channel structure design of the angular valve is designed in view of the fact that the inflow direction of the medium pumped into the valve body is kept parallel to the movement direction of the valve rod structure, so that the valve rod structure is more easily affected by the large fluctuation of the medium pressure. In order to overcome the stress damage to the valve rod structure, a simulation clutch structure is used, and the specific performance is that the lower moving disc has a moving trend relative to the upper moving disc, and the angle deflection process of the differential moment pressure rod to the constant pressure guide sleeve is formed. The essence is to transfer the stress influence on the valve rod structure according to the change of the medium pressure. In addition, the length and the rotating force arm distance of the differential moment pressure rod structure are improved, so that the constant pressure guide rod and the ball head rod can freely move at multiple angles. The stress damage to the key structure is reduced through the unloading mode.

Description

Technical Field

[0001] This invention relates to the field of angle valve technology, and more specifically to an angle valve drive mechanism with an overload protection clutch. Background Technology

[0002] The difference between an angle valve and a conventional valve body lies in the water channel design set at 90°, such as the structure of a common faucet. Considering the valve body structure, the valve body will experience overload problems due to fluctuations in medium pressure, which specifically affects the valve body structure (shell) and valve core structure.

[0003] Furthermore, considering the 90° water channel structure of the angle valve: the 90° turning design of the angle valve will cause a sudden change in the fluid direction, which is prone to generating eddies and local high pressure zones when pressure fluctuates, which may aggravate the wear of the sealing surface and make it more likely to affect the valve body, valve core and valve stem and other structures. Under high pressure differential conditions (such as PN16-PN40), the contact stress between the valve core and the valve seat of the angle valve will change significantly with pressure fluctuations. In particular, since angle valves usually do not have an active pressure reducing function (unlike pressure reducing valves), when the medium pressure rises sharply, they need to rely on manual adjustment or external control systems to maintain a stable flow rate, and the response speed is slow. The valve stem mainly achieves the opening switching action through rotation or sliding action, which is essentially changing the valve core opening through linear movement. In particular, for angle valve structures used in industrial fields (such as petrochemical pipelines), when the medium pressure fluctuation exceeds the upper limit of the valve body design, the valve stem directly bears the medium pressure fluctuation, causing the valve stem to deform. This invention proposes a solution to this problem. Summary of the Invention

[0004] The purpose of this invention is to provide an angle valve drive mechanism with an overload protection clutch, which is designed for applications with high pressure fluctuations, such as angle valve structures used in petrochemical pipelines in the industrial field. In particular, when the medium pressure rises suddenly, the valve stem directly bears the medium pressure fluctuations before other components, which can lead to problems such as local deformation of the valve stem.

[0005] The objective of this invention can be achieved through the following technical solution: an angle valve drive mechanism with an overload protection clutch, applied in the valve body of an angle valve, the valve body including a valve core, a valve core seat and an elastic valve stem, an upper moving plate and a lower moving plate are arranged sequentially from top to bottom in the upper position of the valve body corresponding to the elastic valve stem, and a clutch elastic component is arranged between the upper moving plate and the lower moving plate; A ball joint is installed at the center point of the upper surface of the upper moving plate, and the upper moving plate forms a dynamic fluctuation mode with the lower moving plate through the clutch elastic component. A constant pressure guide sleeve is provided on the outside of the ball joint. Multiple sets of directional seats are installed on the upper surface of the upper moving plate, and a differential torque pressure rod is provided in the directional seat. Multiple directional levers are installed on the upper surface of the lower moving plate.

[0006] The valve core seat is further configured such that it is installed on the lower side of the valve body, the valve core is disposed in the valve core seat, and the elastic valve stem is disposed directly above the valve core.

[0007] The following configuration is further provided: a wave-pulsing sub-shaft is installed at the center point of the lower surface of the lower moving plate; the upper part of the elastic valve stem maintains a sliding connection with the wave-pulsing sub-shaft; and the valve core forms an opening adjustment method through the elastic valve stem, the wave-pulsing sub-shaft, and the valve core seat.

[0008] Further configured: the directional lever extends upward through the upper moving plate and maintains a sliding connection with it; the directional lever is divided into a long-distance section and a short-distance section according to its length; a spring cap corresponding to the upper surface of the upper moving plate is provided at the top position of the directional lever corresponding to the long-distance section; and the top position of the directional lever corresponding to the short-distance section matches one end of the torque differential pressure rod. Further configured: the setting direction of the torque differential pressure rod is parallel to the diameter direction of the upper moving plate; and the linear distance between the directional seat and the ball joint is not equal.

[0009] The configuration is further defined as follows: the differential torque pressure bar and the directional seat maintain a rotatable connection, and the other end of the differential torque pressure bar is located at the lower end of the outer wall of the constant pressure guide sleeve. The differential torque pressure bar is arranged in a ring array along the ball head bar.

[0010] The design further includes: a large arc groove is provided at the lower end of the outer wall of the pressure guide sleeve, and a spherical movable joint is formed between the pressure guide sleeve and the ball head rod, wherein the inner diameter of the pressure guide sleeve is larger than the outer diameter of the ball head rod.

[0011] The configuration is further defined as follows: a drive spindle is rotatably mounted at the upper end of the ball joint, the drive spindle and the valve body maintain a threaded transmission mode, and the outer walls of the upper and lower moving plates maintain a sliding relationship with the valve body.

[0012] The present invention has the following beneficial effects: 1. This invention is based on the angle valve and is an improvement on it. The main reason is that the 90° water channel structure design in the angle valve makes the valve stem structure more susceptible to stress damage caused by media stress fluctuations. Specifically, the linear movement direction of the valve stem structure is relatively parallel to the flow direction of the medium pumped into the valve body. To address this, a clutch structure is simulated for the movement process of the valve stem structure. The basis of this is that the elastic structure in the clutch elastic structure is used to cooperate with the changes in media pressure fluctuations, and on the other hand, a linear movement trend of the lower moving plate relative to the upper moving plate is formed. 2. In addition to the above, the key aspects of this invention lie in the soft connection between the upper and lower moving plates. Furthermore, several directional levers are positioned between them, with some levers serving as short-distance sections. These levers cooperate with the differential torque lever to create a multi-angle deflection process. The differential torque lever also cooperates with the constant pressure guide sleeve. The key to this is the improvement of the length and rotation arm distance of the differential torque lever structure. This avoids problems such as jamming between the differential torque lever and the constant pressure guide sleeve during the angle deflection process. Furthermore, the difference in the deflection amplitude of the differential torque lever allows the constant pressure guide sleeve to move freely at multiple angles. The crucial point is that the stress impact on the valve stem structure is "transferred" through relative movement, reducing stress damage to key structural components through stress relief. Attached Figure Description

[0013] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0014] Figure 1 This is a schematic diagram of the angle valve drive mechanism with overload protection clutch proposed in this invention; Figure 2 For the present invention Figure 1 Sectional view of the middle valve body; Figure 3 This is a schematic diagram of the valve core seat and valve core in this invention; Figure 4 This is a schematic diagram of the upper moving plate and the lower moving plate in this invention; Figure 5 In this invention Figure 4 A split diagram; Figure 6 For the present invention Figure 4 Schematic diagram of the upper and middle moving plate; Figure 7 In this invention Figure 1 A sectional view.

[0015] In the diagram: 1. Valve body; 2. Drive spindle; 3. Upper moving plate; 4. Lower moving plate; 5. Flushing sub-shaft; 6. Elastic valve stem; 7. Valve core; 8. Valve core seat; 9. Constant pressure guide sleeve; 10. Differential torque rod; 11. Orienting seat; 12. Spring cap; 13. Orienting lever; 14. Clutch elastic assembly; 15. Ball joint rod. Detailed Implementation

[0016] The technical solution of the present invention will be clearly and completely described below with reference to the embodiments. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0017] Example 1: For applications requiring high pressure fluctuations, such as angle valves used in petrochemical pipelines in industrial fields, especially when the medium pressure suddenly increases, the valve stem directly bears the pressure fluctuations before other components, leading to localized deformation of the valve stem. The following technical issues are addressed: Reference Figures 1-7 In this embodiment, the angle valve drive mechanism with overload protection clutch is applied in the valve body 1 of the angle valve. The valve body 1 includes a valve core 7, a valve core seat 8 and an elastic valve stem 6. The upper moving plate 3 and the lower moving plate 4 are arranged sequentially from top to bottom in the upper position of the valve body 1 corresponding to the elastic valve stem 6. A clutch elastic component 14 is arranged between the upper moving plate 3 and the lower moving plate 4. A ball joint rod 15 is installed at the center point of the upper surface of the upper moving plate 3, and the upper moving plate 3 forms a dynamic fluctuation with the lower moving plate 4 through the clutch elastic component. A constant pressure guide sleeve 9 is provided on the outside of the ball joint rod 15. Multiple sets of directional seats 11 are installed on the upper surface of the upper moving plate 3, and a differential torque pressure rod 10 is provided in the directional seat 11. Multiple directional levers 13 are installed on the upper surface of the lower moving plate 4. The valve core seat 8 is installed on the lower side of the valve body 1, and the valve core 7 is set in the valve core seat 8. The elastic valve stem 6 is set directly above the valve core 7. A drive spindle 2 is rotatably installed at the upper end of the ball joint rod 15. The drive spindle 2 maintains a threaded transmission with the valve body 1, and the outer walls of the upper moving plate 3 and the lower moving plate 4 maintain sliding with the valve body 1.

[0018] Operating principle: A simple explanation of the angle valve structure: Refer to... Figure 2 The opening at its lower end is set as the inlet, and the opening at another position is set at 90° to it and set as the outlet. When the medium is injected into the inlet, the contact degree between the valve core 7 and the valve core seat 8 is changed by moving the elastic valve stem 6 up and down. In this way, the opening degree during the flow of the medium is changed. This part is the normal operating principle of the angle valve. All valve body structures are affected by fluctuations in medium pressure. While angle valves are relatively simple, the only difference between them and other valve body structures lies in the 90° water channel. (See reference...) Figure 2Explanation: Because the medium is mainly pumped directly into the valve body 1 along the length direction parallel to the elastic valve stem 6, when the medium fluctuates significantly, the elastic valve stem 6 takes priority over other components to directly bear the pressure change. This is especially important for high-pressure valve body applications in the industrial field. For example, take the relevant angle valve structure used in oil pipelines in the petrochemical field. If the elastic valve stem 6 is subjected to varying degrees of medium pressure changes over a long period of time, deformation will inevitably occur due to stress changes. To address this, the present invention is based on an improvement of a clutch-like structure. Essentially, it simulates a clutch protection method based on the operation of the elastic valve stem 6. Its purpose is to address the issue of medium pressure changes by simulating clutch operation to provide overload protection and reduce stress damage to the elastic valve stem 6 caused by medium pressure.

[0019] Example 2: Based on the technical content of Example 1, the following supplementary explanation is provided regarding the action process of the clutch elastic component when the pressure of the engaging medium changes: A wave-pulsing sub-shaft 5 is installed at the center point of the lower surface of the lower moving plate 4. The upper part of the elastic valve stem 6 maintains a sliding connection with the wave-pulsing sub-shaft 5. The valve core 7 forms an opening adjustment method through the elastic valve stem 6, the wave-pulsing sub-shaft 5, and the valve core seat 8. The directional lever 13 passes through the upper moving plate 3 upward and maintains a sliding connection with the upper moving plate 3. The directional lever 13 is divided into a long-distance part and a short-distance part according to its length. A spring cap corresponding to the upper surface of the upper moving plate 3 is provided at the top of the directional lever 13 corresponding to the long-distance part. 12. The top of the directional lever 13 corresponding to the short distance part matches one end of the differential torque lever 10. The differential torque lever 10 and the directional seat 11 maintain a rotatable connection. The other end of the differential torque lever 10 corresponds to the lower end of the outer wall of the constant pressure guide sleeve 9. The differential torque lever 10 is arranged in a ring array along the ball head rod 15. A large arc groove is opened at the lower end of the outer wall of the constant pressure guide sleeve 9. A spherical movable joint is formed between the constant pressure guide sleeve 9 and the ball head rod 15. The inner diameter of the constant pressure guide sleeve 9 is larger than the outer diameter of the ball head rod 15.

[0020] Solution Description: First, let's explain the opening adjustment method between valve core 7 and valve core seat 8: When the high-pressure medium enters the valve body 1, the pressure exerted by the medium on the valve core 7 can drive the elastic valve stem 6 to move slightly. However, in reality, the elastic valve stem 6 mainly achieves the opening adjustment through the oscillating sub-shaft 5. The elastic valve stem 6 is also equipped with a spring, the purpose of which is to use the elastic potential energy of the spring to buffer and reduce energy when subjected to large pressure fluctuations. This part is also a conventional structural design of the valve stem. In this invention, it is required that the wave-type secondary shaft 5, the lower moving plate 4, and the upper moving plate 3 only need to slide along the length direction of the elastic valve stem 6. This is based on the drive main shaft 2, which maintains a threaded transmission between the drive main shaft 2 and the overall valve body 1, and cooperates with the rotational connection between the drive main shaft 2 and the ball head rod 15 to ensure that the upper moving plate 3 and the lower moving plate 4 maintain a sliding connection with the inner wall of the valve body 1. Reference Figure 5 Explanation: Theoretically, the upper moving plate 3 and the lower moving plate 4 are in a "soft connection mode". The two are mainly "connected" through the clutch elastic component 14. The clutch elastic component 14 is essentially composed of multiple elastic elements with elasticity. For example, when the upper moving plate 3 moves downward, it continuously compresses the clutch elastic component 14, and under the action of the clutch elastic component 14, it indirectly drives the lower moving plate 4 to move downward. Regarding the components of the clutch elastic assembly 14, please refer to... Figure 5 The relevant structures in, and refer to Figure 7 The cross-sectional view of the clutch elastic component 14 in the figure is intended to ensure that the upper moving plate 3 and the lower moving plate 4 can move synchronously or asynchronously, using the clutch elastic component 14 as a soft connection structure.

[0021] Example 3: Supplementary explanation of the overall solution based on the technical content of Example 2: Reference Figure 6 To explain, a constant pressure guide sleeve 9 is provided on the outside of the ball head 15. The constant pressure guide sleeve 9 and the ball head 15 have multi-angle mobility, and the constant pressure guide sleeve 9 can perform a synchronous linear movement process with the ball head 15. In order to maintain the above multi-angle mobility, it is also necessary to further limit the differential design between the inner diameter of the constant pressure guide sleeve 9 and the outer diameter of the ball head 15. In conjunction with the technical content of Embodiments 2 and 1, it is explained that when the medium pressure inside the valve body 1 fluctuates significantly, the connection between the lower moving plate 4 and the elastic valve stem 6 is also affected by the change in medium pressure. Specifically, when the medium pressure rises sharply, the lower moving plate 4 will also tend to move upward due to the influence of the medium pressure. This can be referred to... Figure 4 Explanation: When the lower moving plate 4 has an upward tendency, the directional lever 13 of the short-pitch part moves upward, while the differential torque pressure rod 10 and the directional seat 11 maintain a hinged state. When the directional lever 13 moves upward, it causes the differential torque pressure rod 10 to rotate directionally along its rotation point. The key action is that one end of the differential torque pressure rod 10 further presses the constant pressure guide sleeve 9 downward. It can be understood that when the lower moving plate 4 has an upward tendency, the directional rotation process of the differential torque pressure rod 10 will also generate a downward force tendency on the upper moving plate 3 through the constant pressure guide sleeve 9. In addition to the above, it should be noted that when the lower moving plate 4 has an upward tendency, stress will also be transmitted through the clutch elastic component 14. However, the upper moving plate 3 and the drive spindle 2 are only rotated, so the position of the upper moving plate 3 will not change. Similarly, the position of the constant pressure guide sleeve 9 will not change. The key function is to change the movement trend of the lower moving plate 4 according to the change of medium pressure. On the one hand, the clutch elastic component 14 can be used for elastic buffering action, which is relatively simple and will not be explained in detail. On the other hand, the upward movement trend of the lower moving plate 4 changes the rotation mode of the differential torque pressure rod 10, thereby generating downward pressure on the upper moving plate 3. Theoretically, it will cause the upper moving plate 3 to move downward, but in actual case, under the premise that the drive spindle 2 does not undergo helical transmission, the upper moving plate 3 will not change displacement. To address this, the structural characteristics of the differential torque lever 10 need to be improved. The setting direction of the differential torque lever is parallel to the diameter direction of the upper moving plate. The linear distance between the directional seat and the ball head rod is not equal. Because the upward movement trend of the lower moving plate 4 will not undergo angular deviation but can only move linearly, the upward movement distance of each short-distance directional lever 13 is completely equal. However, the upper moving plate 3 does not have displacement capability when the drive spindle 2 is not started. Therefore, it can only rely on the multi-angle movement capability of the constant pressure guide sleeve 9. Because the linear distance between each directional seat and the ball head rod is limited to a difference, the deflection angle of each differential torque lever 10 is different when each directional lever 13 moves upward, thereby driving the constant pressure guide sleeve 9 to deflect the directional angle. If one of the differential torque rods 10 deflects at a large angle, then the other differential torque rods 10 will deflect at a relatively low angle. The purpose is to make the constant pressure guide sleeve 9 deflect at a directional angle. This is so that the "transfer structure" of the constant pressure guide sleeve 9 can consume the kinetic energy of the medium pressure fluctuation, thereby reducing stress damage to key structures such as the upper moving plate 3, the drive spindle 2, and the elastic valve stem 6.

[0022] In summary: Regarding the 90° waterway structure design in angle valves, because the inflow direction of the medium pumped into the valve body is parallel to the movement direction of the valve stem structure, it is more susceptible to large fluctuations in medium pressure. To address this, a simulated clutch structure is used to overcome stress damage to the valve stem structure, specifically as follows: The lower moving plate has a tendency to move relative to the upper moving plate. The angle deflection process formed by the differential torque rod on the constant pressure guide sleeve is essentially a "transfer" of the stress influence on the valve stem structure based on the change of medium pressure. In this regard, the length and rotation arm distance of the differential torque rod structure characteristics have been improved to enable the constant pressure guide rod and the ball head rod to move freely at multiple angles, thereby reducing stress damage to key structural components by unloading force.

[0023] The above description is merely an example and illustration of the structure of the present invention. Those skilled in the art can make various modifications or additions to the specific embodiments described, or use similar methods to replace them, as long as they do not deviate from the structure of the invention or exceed the scope defined in the claims, all of which should fall within the protection scope of the present invention.

[0024] In the description of this specification, references to terms such as "an embodiment," "example," "specific example," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the invention. In this specification, illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0025] The preferred embodiments of the present invention disclosed above are merely illustrative of the invention. These preferred embodiments do not exhaustively describe all details, nor do they limit the invention to specific implementations. Clearly, many modifications and variations can be made based on the content of this specification. This specification selects and specifically describes these embodiments to better explain the principles and practical applications of the invention, thereby enabling those skilled in the art to better understand and utilize the invention. The invention is limited only by the claims and their full scope and equivalents.

Claims

1. An angular valve driving mechanism with overload protection clutch, applied in a valve body (1) of an angular valve, the valve body (1) comprising a valve core (7), a valve core seat (8) and an elastic valve rod (6), characterized in that, The valve body (1) is provided with an upper moving plate (3) and a lower moving plate (4) in the upper position corresponding to the elastic valve stem (6) in the direction from top to bottom. A clutch elastic component (14) is provided between the upper moving plate (3) and the lower moving plate (4). A ball joint rod (15) is installed at the center point of the upper surface of the upper moving plate (3), and the upper moving plate (3) forms a dynamic fluctuation mode with the lower moving plate (4) through the clutch elastic component (14). A constant pressure guide sleeve (9) is provided on the outside of the ball joint rod (15). Multiple sets of directional seats (11) are installed on the upper surface of the upper moving plate (3). A differential torque pressure rod (10) is provided in the directional seat (11). Multiple directional levers (13) are installed on the upper surface of the lower moving plate (4). The valve core seat (8) is installed on the lower side of the valve body (1), the valve core (7) is disposed in the valve core seat (8), and the elastic valve stem (6) is disposed directly above the valve core (7). A wave-pulsing sub-shaft (5) is installed at the center point of the lower surface of the lower moving plate (4). The upper part of the elastic valve stem (6) is slidably connected to the wave-pulsing sub-shaft (5). The valve core (7) forms an opening adjustment mode through the elastic valve stem (6), the wave-pulsing sub-shaft (5) and the valve core seat (8). The directional lever (13) extends upward through the upper moving plate (3) and maintains a sliding connection with the upper moving plate (3). The directional lever (13) is divided into a long-distance part and a short-distance part according to its length. A spring cap (12) corresponding to the upper surface of the upper moving plate (3) is provided at the top position of the directional lever (13) corresponding to the long-distance part. The top position of the directional lever (13) corresponding to the short-distance part matches the position of one end of the differential torque pressure bar (10). The setting direction of the differential torque pressure bar (10) is parallel to the diameter direction of the upper moving plate (3), and the linear distance between the directional seat (11) and the ball head rod (15) is not equal; The differential torque pressure bar (10) and the directional seat (11) maintain a rotatable connection, and the other end of the differential torque pressure bar (10) is located at the lower end of the outer wall of the constant pressure guide sleeve (9). The differential torque pressure bar (10) is arranged in a ring array along the ball head rod (15).

2. An angular valve actuation mechanism with an overload protection clutch as in claim 1, wherein The pressure guide sleeve (9) has a large arc groove at the lower end of its outer wall, and a spherical movable joint is formed between the pressure guide sleeve (9) and the ball head rod (15). The inner diameter of the pressure guide sleeve (9) is larger than the outer diameter of the ball head rod (15).

3. An angular valve actuation mechanism with an overload protection clutch as in claim 2, wherein The upper end of the ball head rod (15) is rotatably mounted with a drive spindle (2). The drive spindle (2) and the valve body (1) maintain a threaded transmission mode. The outer walls of the upper moving plate (3) and the lower moving plate (4) maintain sliding with the valve body (1).

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