High-temperature self-sealing multi-stage pressure reducing control valve and control method

Abstract

The application provides a high-temperature self-sealing multi-stage pressure-reducing regulating valve and a control method, and belongs to the technical field of regulating valves. The valve body, valve seat, valve rod, valve core, balance cylinder, cylinder cover and actuator are provided. The inner sleeve and outer sleeve are arranged on the valve seat. The balance cylinder is arranged on the outer sleeve, inner sleeve and valve core. The sealing ring pressure cover is arranged on the balance cylinder. The cylinder outer sealing assembly is arranged between the sealing ring pressure cover and the valve body. The cylinder inner sealing assembly is arranged between the inner sleeve and the valve core. The threaded connection port is arranged on the valve body. The cylinder cover is threadedly connected to the threaded connection port. The valve body, valve seat, inner sleeve, outer sleeve, balance cylinder, sealing ring pressure cover, cylinder inner sealing assembly, cylinder outer sealing assembly and cylinder cover form a sealed connection whole. In the application, double sealing is formed to completely solve the industry pain point that the two key sealing parts of the valve body cavity and the inner cavity of the traditional regulating valve are prone to leakage under the working conditions of high temperature, high pressure, high flow rate and high pressure difference.

Description

Technical Field

[0001] This invention relates to the field of regulating valve technology, specifically to a high-temperature self-sealing multi-stage pressure-reducing regulating valve and its control method. Background Technology

[0002] Currently, in the control valve regulation of high-temperature and high-pressure media in fields such as power, chemical, and oil refining, the structural shortcomings of high-temperature and high-pressure regulating valves appearing in the market and in materials are obvious. For example, the valve body cavity uses a sealing structure with a bolted connection to the valve cover, which is prone to leakage when the pressure is too high. Another example is a valve body cavity with a self-sealing structure, where components such as the valve seat, sleeve, and balance cylinder cannot form a fixed, unchanging sealed connection with the valve body cavity. The higher the fluid pressure, the greater the change in the connection gap of these components as the self-sealing valve core moves upward, and the greater the leakage. Summary of the Invention

[0003] The purpose of this invention is to overcome the shortcomings and deficiencies of the existing technology and to provide a high-temperature self-sealing multi-stage pressure reducing regulating valve and control method.

[0004] The technical solution adopted by this invention is as follows: Firstly, this application provides a high-temperature self-sealing multi-stage pressure-reducing regulating valve, comprising a valve body, a valve seat, a valve stem, a valve core, a balance cylinder, a cylinder head, and an actuator. The valve body includes an inlet chamber and an outlet chamber, with a connecting port between the inlet chamber and the outlet chamber. The valve seat is disposed at the connecting port, and the valve seat is provided with an inner sleeve and an outer sleeve. The inner sleeve has several first through holes, and the outer sleeve has several second through holes offset from the first through holes. The valve core and the valve stem are connected, and... The balance cylinder is mounted on the outer sleeve, inner sleeve, and valve core, and is slidably disposed within the inner sleeve. A sealing ring cover is provided on the balance cylinder, and an external sealing assembly is provided between the balance cylinder and the valve body. An internal sealing assembly is provided between the balance cylinder and the inner sleeve and valve core. A threaded connection port is provided on the valve body, and the cylinder cover is threadedly connected to the threaded connection port, so that the valve body, valve seat, inner sleeve, outer sleeve, balance cylinder, sealing ring cover, internal sealing assembly, external sealing assembly, and cylinder cover constitute a sealed connection unit.

[0005] In some embodiments, the upper end of the valve seat is provided with an inner positioning boss and an outer positioning boss, and the inner sleeve and the outer sleeve are respectively sleeved on the inner positioning boss and the outer positioning boss. The inner sleeve and the outer sleeve are coaxially arranged, and a radial gap is provided between them.

[0006] In some embodiments, the lower end of the balance cylinder has an inner circumference provided with a first annular groove for installing an in-cylinder sealing assembly, and the upper end has an outer circumference provided with a second annular groove for installing an external sealing assembly.

[0007] In some embodiments, the in-cylinder sealing assembly includes a disc spring, an in-cylinder ring gasket, and an in-cylinder sealing ring arranged sequentially from bottom to top. The end face of the in-cylinder sealing ring that abuts against the first ring groove is configured as a first conical surface that is adapted to it, and the upper side of the first conical surface converges toward the valve stem.

[0008] In some embodiments, the external cylinder sealing assembly includes an external cylinder ring gasket and an external cylinder sealing ring that abut against each other, wherein the abutting end faces of the external cylinder ring gasket and the external cylinder sealing ring are configured as a matching second conical surface, and the upper side of the second conical surface of the external cylinder ring gasket converges toward the valve stem.

[0009] In some embodiments, a valve cover is provided on the valve body, a four-ring is provided between the valve cover and the valve body, a self-sealing valve sleeve is provided on the valve stem, the self-sealing valve sleeve includes a cylindrical portion disposed between the valve stem and the valve cover and a disc portion disposed within the valve body, a self-sealing ring gasket and a self-sealing pressure gasket are abutting between the disc portion and the four-ring, and the end faces of the self-sealing ring gasket and the four-ring that abut against each other are configured as a matching third conical surface.

[0010] In some embodiments, a cooling chamber is formed between the self-sealing valve sleeve, the valve cover, and the four-ring open. The valve body is provided with an inlet and an outlet corresponding to the cooling chamber. The cylinder cover is provided with a plurality of first channels along the axial direction. The sealing ring cover is provided with a second channel corresponding to the first channels. The balance cylinder is provided with a cooling flow channel. The disc is provided with a flow channel pipe. The upper end of the flow channel pipe communicates with the cooling chamber, and its lower end passes through the first channel and communicates with the second channel and the cooling flow channel.

[0011] Secondly, this application provides a control method for the aforementioned high-temperature self-sealing multi-stage pressure reducing regulating valve, comprising the following steps:

[0012] Step S1: Set the target displacement and allowable displacement deviation value corresponding to the target opening degree that the valve core needs to achieve. At the same time, set the basic driving force, single force amplification amplitude and maximum driving force threshold of the actuator, and preset the target outlet flow range corresponding to the target opening degree.

[0013] Step S2: The actuator drives the valve core to move with the basic driving force, and the actual displacement of the valve core is collected in real time by the displacement sensor, and the actual flow rate of the outlet cavity is collected in real time by the flow sensor installed in the outlet cavity.

[0014] Step S3: If the actual displacement of the valve core is less than the difference between the target displacement and the allowable displacement deviation value, and this state continues for a specified duration, and the actual flow rate of the outlet chamber is less than the lower limit of the target outlet flow rate range, then it is determined that the valve core is stuck.

[0015] Step S4: The actuator gradually increases the driving force according to the set single force increase range, and maintains it for the first preset time after each force increase, while continuously monitoring the actual displacement of the valve core and the actual flow rate of the outlet cavity;

[0016] If, during the force-increasing process, the actual displacement of the valve core is not less than the difference between the target displacement and the allowable displacement deviation, and the actual flow rate of the outlet chamber is within the target outlet flow rate range, then the force-increasing process is stopped, and the current driving force is maintained to stabilize the valve core position.

[0017] Step S5: If the actual displacement of the valve core still does not reach the judgment standard or the actual flow rate of the outlet chamber does not enter the target outlet flow rate range after the driving force output by the actuator reaches the maximum driving force threshold, the actuator will immediately reduce the driving force to the basic driving force and output a jamming alarm.

[0018] During the power increase process, if the displacement sensor detects that the vibration amplitude of the valve core exceeds the preset vibration threshold, the power increase operation will be paused for a second preset duration and then restarted to avoid the valve core overshooting caused by the sudden release of the jamming.

[0019] In some embodiments, in step S4, while maintaining the current driving force to stabilize the valve core position, the actual displacement of the valve core and the actual flow rate of the outlet cavity are detected once every third preset time interval; if the actual displacement of the valve core falls back to below the difference between the target displacement and the allowable displacement deviation value, or the actual flow rate of the outlet cavity is less than the lower limit of the target outlet flow rate range, then the force increase operation of step S4 is repeated, and the cumulative force increase number does not exceed the preset number.

[0020] In some embodiments, the valve operating temperature is obtained by a temperature sensor, the rate of change of the valve operating temperature per unit time is calculated, and a temperature change rate threshold is preset.

[0021] If the rate of change is greater than the preset temperature change rate threshold, and the valve operating temperature is within the preset high temperature range, then it is determined to be a heat deformation-dominated jamming type.

[0022] If the rate of change is less than or equal to the preset temperature change rate threshold, or if the valve operating temperature is within the preset low temperature range, it is determined to be a foreign object-dominated jamming type.

[0023] If the jamming is determined to be caused by thermal deformation, during the force increase process in step S4, the cooling medium circulation is simultaneously started or the cooling medium flow rate is increased. The cooling medium flow rate increases accordingly with the increase of the temperature change rate until the temperature change rate is ≤ the preset temperature change rate threshold.

[0024] If the obstruction is determined to be caused by a foreign object, during the force increase process in step S4, the actual displacement increment of the valve core is monitored after each force increase. If the displacement increment is less than the preset minimum effective increment, the actuator drives the valve core to move the set displacement in the opposite direction and then resumes the forward force increase. Otherwise, the forward force increase continues at the original force increase amplitude.

[0025] The beneficial effects of this invention are as follows: This invention utilizes the pressing action of the cylinder head on the balance cylinder, sleeve, and valve seat, combined with the self-sealing design of the valve body cavity, to form a double sealing guarantee. This completely solves the industry pain point of easy leakage in the two key sealing parts of the valve body cavity and inner cavity under high temperature, high pressure, high flow rate, and high pressure differential conditions in traditional control valves. Furthermore, the double-hole pressure-reducing cage formed by the inner sleeve and outer sleeve eliminates valve flashing and cavitation phenomena through a two-stage throttling and pressure-reducing mechanism. The medium is initially throttled through the first through-hole of the inner sleeve, and then undergoes secondary pressure reduction through the misaligned second through-hole of the outer sleeve, gradually distributing the high pressure differential at the inlet end and always maintaining the medium pressure above its saturated vapor pressure. This fundamentally avoids the erosion of the valve core and sleeve by flashing and cavitation, significantly extending the service life of the control valve under harsh operating conditions. Attached Figure Description

[0026] 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, obtaining other drawings based on these drawings without creative effort still falls within the scope of the present invention.

[0027] Figure 1 This is a schematic diagram of the high-temperature self-sealing multi-stage pressure reducing regulating valve of the present invention;

[0028] Figure 2 This is a partial schematic diagram of the high-temperature self-sealing multi-stage pressure reducing regulating valve of the present invention. Figure 1 ;

[0029] Figure 3 This is a partial schematic diagram of the high-temperature self-sealing multi-stage pressure reducing regulating valve of the present invention. Figure 2 ;

[0030] Figure 4 This is a partial schematic diagram of the high-temperature self-sealing multi-stage pressure reducing regulating valve of the present invention. Figure 3 ;

[0031] In the diagram: 1-Valve body, 100-Inlet cavity, 101-Outlet cavity, 102-Connecting port, 103-Threaded connection port, 104-Liquid inlet, 105-Liquid outlet, 2-Valve seat, 200-Inner positioning boss, 201-Outer positioning boss, 3-Valve stem, 4-Valve core, 5-Balance cylinder, 500-First annular groove, 501-Second annular groove, 5000-Cooling flow channel, 6-Cylinder head, 600-First channel, 7-Actuator, 8-Inner sleeve, 80-First through hole, 9-Outer sleeve, 90-Second through hole, 10- 1000-Second channel, 11-External cylinder sealing assembly, 110-External cylinder ring gasket, 111-External cylinder sealing ring, 112-Second conical surface, 12-Internal cylinder sealing assembly, 120-Disc spring, 121-Internal cylinder ring gasket, 122-Internal cylinder sealing ring, 123-First conical surface, 13-Valve cover, 14-Four-open ring, 15-Self-sealing valve sleeve, 150-Cylinder section, 151-Disc section, 16-Self-sealing ring gasket, 17-Self-sealing pressure pad, 18-Third conical surface, 19-Cooling chamber, 20-Flow channel pipe. Detailed Implementation

[0032] The following description provides specific application scenarios and requirements for this specification, intended to enable those skilled in the art to make and use the contents of this specification. Various partial modifications to the disclosed embodiments will be apparent to those skilled in the art, and the general principles defined herein can be applied to other embodiments and applications without departing from the spirit and scope of this specification. Therefore, this specification is not limited to the embodiments shown, but rather to the widest scope consistent with the claims.

[0033] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "longitudinal", "lateral", "radial", "length", "width", "thickness", "upper", "lower", "left", "right", "front", "rear", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are mainly for the purpose of better describing this application and its embodiments, and are not intended to limit the indicated device, element or component to have a specific orientation, or to be constructed and operated in a specific orientation.

[0034] It should be noted that the terms "first," "second," and similar words do not indicate any order, quantity, or importance, but are only used to distinguish different components and should not be construed as limiting the embodiments of this application.

[0035] It should be noted that the terms "installation," "setup," "equipped with," "connection," and "connected" should be interpreted broadly. For example, they can refer to fixed connections, detachable connections, or integral structures; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium, or internal connections between two devices, components, or parts.

[0036] It should be noted that the terms "in some embodiments," "exemplarily," and "for example" are used to indicate examples, illustrations, or descriptions. Any embodiment or design described in this application as "in some embodiments," "exemplarily," or "for example" should not be construed as being more preferred or advantageous than other embodiments or designs. Specifically, the use of terms such as "in some embodiments," "exemplarily," and "for example" is intended to present related concepts in a specific manner, meaning that a particular feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of this application. The appearance of the above terms in various places in the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment mutually exclusive with other embodiments. Those skilled in the art will explicitly and implicitly understand that the embodiments described herein can be combined with other embodiments.

[0037] Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0038] Regarding the accompanying drawings of this application, it should be clearly understood that the drawings are for illustrative and descriptive purposes only and are not intended to limit the scope of this specification. It should also be understood that the drawings are not necessarily drawn to scale.

[0039] like Figures 1 to 4 As shown, this application provides a high-temperature self-sealing multi-stage pressure reducing regulating valve, including a valve body 1, a valve seat 2, a valve stem 3, a valve core 4, a balance cylinder 5, a cylinder cover 6, and an actuator 7. The valve body 1 includes an inlet chamber 100 and an outlet chamber 101, with a connecting port 102 between the inlet chamber 100 and the outlet chamber 101. The valve seat 2 is located at the connecting port 102. The valve seat 2 is provided with an inner sleeve 8 and an outer sleeve 9. The inner sleeve 8 has several first through holes 80, and the outer sleeve 9 has several second through holes 90 offset from the first through holes 80. When the medium flows through, it needs to change its flow direction multiple times and pass through a narrow channel to achieve multi-stage treatment of throttling, pressure reduction, and energy dissipation, effectively reducing the direct impact of high-pressure medium on the valve core 4 and extending the service life of the valve core 4.

[0040] The valve core 4 and valve stem 3 are connected and slide up and down within the inner sleeve 8. The balance cylinder 5 is sleeved on the outer sleeve 9, the inner sleeve 8, and the valve core 4. The balance cylinder 5 is provided with a sealing ring cover 10. An external sealing assembly 11 is provided between the balance cylinder 5, the sealing ring cover 10, and the valve body 1. An internal sealing assembly 12 is provided between the balance cylinder 5, the inner sleeve 8, and the valve core 4. The valve body 1 is provided with a threaded connection port 103. The cylinder cover 6 is threadedly connected to the threaded connection port 103, so that the valve body 1, valve seat 2, inner sleeve 8, outer sleeve 9, balance cylinder 5, sealing ring cover 10, internal sealing assembly 12, external sealing assembly 11, and cylinder cover 6 constitute a sealed connection whole. In this way, the sealing reliability between valve core 4 and balance cylinder 5, and between valve body 1 and valve seat 2 is guaranteed. At the same time, with the help of the pressure self-reinforcing effect, as the medium pressure increases, the contact pressure of each sealing surface increases synchronously, and the sealing performance is even better. Meanwhile, the sliding of valve core 4 in inner sleeve 8 is not restricted by the structure, and the valve can be opened and closed and the flow can be adjusted smoothly, avoiding the jamming problem caused by the conflict between sealing and sliding requirements in traditional structures.

[0041] Specifically, the pressing action of the cylinder head 6 on the balance cylinder 5, sleeve and valve seat 2, combined with the self-sealing design of the valve body 1 cavity, forms a "double sealing guarantee": on the one hand, the threaded connection of the cylinder head 6 provides basic pre-tightening force to ensure the initial sealing of each component; on the other hand, as the medium pressure increases, the self-sealing structure pushes the valve core 4 to press the self-sealing ring, further strengthening the sealing effect, and completely solving the industry pain point of easy leakage in the two key sealing parts of the valve body cavity and inner cavity under high temperature, high pressure, high flow rate and high pressure difference conditions of traditional control valves.

[0042] In addition, the double-hole pressure-reducing cage formed by the inner sleeve 8 and the outer sleeve 9 eliminates valve flashing and cavitation through a "double throttling and pressure reduction" mechanism. The medium is first initially throttled through the first through hole 80 of the inner sleeve 8, and then pressure is reduced a second time through the misaligned second through hole 90 of the outer sleeve 9. The high pressure difference at the inlet end is gradually distributed, and the medium pressure is always maintained above its saturated vapor pressure. This avoids the corrosion of the valve core and sleeve by flashing and cavitation from the source, and significantly extends the service life of the control valve under harsh working conditions. In some embodiments, the upper end of the valve seat 2 is provided with an inner positioning boss 200 and an outer positioning boss 201. The inner sleeve 8 and the outer sleeve 9 are respectively sleeved on the inner positioning boss 200 and the outer positioning boss 201. The inner sleeve 8 and the outer sleeve 9 are coaxially arranged, and a radial gap is provided between them. This boss structure can accurately position the installation position of the inner and outer sleeves, ensure their coaxiality, and avoid problems such as misalignment of through holes and poor medium flow caused by installation offset. The reserved radial gap can buffer the thermal expansion of the inner and outer sleeves under high temperature conditions, prevent the sleeves from jamming due to mutual compression caused by thermal deformation, and at the same time, no excessive calibration is required during assembly. Positioning can be completed simply by sleeved along the boss, which greatly improves assembly efficiency. It is understandable that the inner positioning boss 200 and the outer positioning boss 201, as mounting structures for positioning the inner sleeve 8 and the outer sleeve 9, can also be mounting grooves adapted to the inner sleeve 8 and the outer sleeve 9. As long as the inner sleeve 8 can be embedded in the inner mounting groove of the valve seat 2 and the outer sleeve 9 can be embedded in the outer mounting groove, the same positioning effect can be achieved, adapting to different processing requirements. Similarly, the balance cylinder 5 can also be set with a similar positioning structure. With this setting, positioning is formed at both the upper and lower ends of the inner sleeve 8 and the outer sleeve 9, ensuring their reliability during valve operation.

[0043] In some embodiments, the inner circumference of the lower end of the balance cylinder 5 is provided with a first annular groove 500 for installing the internal sealing assembly 12, and the outer circumference of its upper end is provided with a second annular groove 501 for installing the external sealing assembly 11. The first annular groove 500 provides a stable installation space for the internal sealing assembly 12, ensuring that the sealing assembly can accurately fit the gap between the inner sleeve 8 and the valve core 4; the second annular groove 501 limits the external sealing assembly 11, preventing it from shifting due to pressure fluctuations during valve operation. Through the positioning of the sealing assembly by the annular groove, combined with the pressing action of the balance cylinder 5 on the sleeve, the upper and lower ends of the inner sleeve 8 and the outer sleeve 9 are reliably fixed. Even under the impact of high-pressure medium, the sleeve will not experience axial movement, ensuring the structural stability of the valve during long-term operation.

[0044] In some embodiments, the in-cylinder sealing assembly 12 includes a disc spring 120, an in-cylinder ring gasket 121 and an in-cylinder sealing ring 122 arranged sequentially from bottom to top. The end face of the in-cylinder sealing ring 122 that abuts against the first ring groove 500 is configured as a first conical surface 123 that is adapted to it. The upper side of the first conical surface 123 converges toward the valve stem 3. Among them, the disc spring 120 has excellent elastic compensation capability, which can continuously provide pre-tightening force for the cylinder sealing ring 122. Even if the sealing component ages and wears due to long-term high-temperature use, the disc spring 120 can compensate for the sealing force through its own deformation, thus avoiding the decay of sealing performance. The cylinder ring gasket 121 plays a transition buffer role, preventing the rigid force of the disc spring 120 from acting directly on the cylinder sealing ring 122, and preventing the sealing ring from being damaged due to excessive local stress. The design of the first conical surface 123 further enhances the self-sealing effect. When the medium pressure acts on the conical surface, it will generate a component force towards the sealing gap, pushing the cylinder sealing ring 122 to fit more tightly against the first ring groove 500 and the outer wall of the valve core 4. The higher the pressure, the tighter the fit, completely blocking the path of medium leakage from the cylinder gap.

[0045] In some embodiments, the external cylinder sealing assembly 11 includes an external cylinder ring gasket 110 and an external cylinder sealing ring 111 that abut against each other. The abutting end faces of the external cylinder ring gasket 110 and the external cylinder sealing ring 111 are configured as compatible second conical surfaces 112, with the upper side of the second conical surface 112 of the external cylinder ring gasket 110 converging towards the valve stem 3. Under the clamping force of the sealing ring gland 10, the external cylinder ring gasket 110 transmits the force evenly to the external cylinder sealing ring 111 through the second conical surface 112, so that the sealing ring tightly fits the second annular groove 501 of the balance cylinder 5 and the inner wall of the valve body 1.

[0046] This design ensures the sealing reliability of the valve body 1 cavity in all aspects. Even if a single sealing component suffers slight damage, the other sealing component can play a backup role to avoid the risk of leakage.

[0047] In some embodiments, a valve cover 13 is provided on the valve body 1, and a four-ring 14 is provided between the valve cover 13 and the valve body 1. A self-sealing valve sleeve 15 is fitted on the valve stem 3. The self-sealing valve sleeve 15 includes a cylindrical portion 150 disposed between the valve stem 3 and the valve cover 13 and a disc portion 151 disposed inside the valve body 1. A self-sealing ring gasket 16 and a self-sealing pressure gasket 17 are abutted between the disc portion 151 and the four-ring 14. The end faces of the self-sealing ring gasket 16 and the four-ring 14 that abut against each other are configured as a matching third conical surface 18. The cylindrical portion 150 of the self-sealing valve sleeve 15 can fill the gap between the valve stem 3 and the valve cover 13, and a stuffing box is provided between the two to prevent the medium from leaking along the valve stem; while the design of the third conical surface 18 forms a self-sealing at the valve stem, solving the problem that traditional valve stem packing seals are prone to leakage under high pressure.

[0048] In some embodiments, a cooling chamber 19 is formed between the self-sealing valve sleeve 15, the valve cover 13, and the four-ring 14. The valve body 1 is provided with an inlet 104 and an outlet 105 corresponding to the cooling chamber 19. The cylinder cover 6 is provided with a plurality of first channels 600 along the axial direction. The sealing ring cover 10 is provided with a second channel 1000 corresponding to the first channels 600. The balance cylinder 5 is provided with a cooling flow channel 5000. The disc portion 151 is provided with a flow channel pipe 20. The upper end of the flow channel pipe 20 is connected to the cooling chamber 19, and its lower end passes through the first channel 600 and is connected to the second channel 1000 and the cooling flow channel 5000. The cooling medium enters the cooling chamber 19 through the inlet 104, passes through the flow channel 20, the first channel 600, and the second channel 1000, and enters the cooling flow channel 500 of the balance cylinder 5 to dissipate heat from the balance cylinder 5 and the two sealing components, preventing the sealing components from losing elasticity due to long-term high temperature. Finally, the cooling medium flows out from the cooling flow channel 5000, forming a complete cooling cycle, ensuring that the key sealing components of the valve are always in a suitable temperature range, maintaining sealing performance and service life.

[0049] This application also provides an assembly method for the aforementioned high-temperature self-sealing multi-stage pressure reducing regulating valve, comprising the following steps: first, installing the valve seat 2 onto the connecting port 102; then, fitting the inner sleeve 8 and outer sleeve 9 onto the valve seat 2; next, inserting the valve core 4 into the inner sleeve 8; then, installing the cylinder sealing assembly 12 into the lower end of the balance cylinder 5, and fitting it onto the outer sleeve 9, inner sleeve 8, and valve core 4; then, fitting the cylinder outer sealing assembly 11 onto the upper end of the balance cylinder 5, and fixing it to the balance cylinder 5 via the sealing ring gland 10; finally, connecting the cylinder cover 6 to the threaded connection port 103, thus fixing the valve body 1, valve seat 2, inner sleeve 8, outer sleeve 9, balance cylinder 5, sealing ring gland 10, cylinder inner sealing assembly 12, cylinder outer sealing assembly 11, and cylinder cover 6 into a sealed connection unit. This assembly method is simple, convenient, and highly efficient.

[0050] This application also provides a control method for the above-mentioned high-temperature self-sealing multi-stage pressure reducing regulating valve, comprising the following steps:

[0051] Step S1: Set the target displacement and allowable displacement deviation value corresponding to the target opening degree to be achieved by valve core 4. The allowable displacement deviation value is set according to the valve core stroke. For example, when the stroke is ≤50mm, it is set to ±0.1mm, and when the stroke is >50mm, it is set to ±0.2mm. Small displacement deviations of short-stroke valve cores will directly lead to excessive opening deviations and must be strictly controlled. The displacement deviation of long-stroke valve cores has a relatively small impact on the opening degree and can be appropriately relaxed to ensure adjustment accuracy and avoid frequent misjudgments due to excessively strict deviation thresholds.

[0052] Simultaneously, the basic driving force, single-stage force amplification amplitude, and maximum driving force threshold of actuator 7 are set. The basic driving force is based on the force analysis of valve core 4. The larger the nominal diameter, the larger the area of ​​medium pressure borne by the valve core. The required basic driving force must be sufficient to overcome the initial friction and medium resistance to ensure that the valve core can start moving. The single-stage force amplification amplitude is reasonably set based on the basic driving force to avoid excessive single-stage force amplification that would cause the valve core to "jump" and overshoot. Smooth adjustment is achieved by gradually increasing the force in small increments. Setting the maximum driving force threshold can protect the valve.

[0053] And preset the target outlet flow range corresponding to the target opening degree;

[0054] Step S2: Actuator 7 drives valve core 4 to move with basic driving force. The actual displacement of valve core 4 is collected in real time by displacement sensor. The displacement sensor is set corresponding to the valve stem and preferably far away from the valve body to reduce interference from high-temperature medium. The actual flow of outlet 101 is collected in real time by flow sensor installed in outlet 101. The sensor adopts high-precision turbine flow meter and is installed in the straight pipe section of outlet 101. The flow of outlet 101 directly reflects the valve regulation effect. The straight pipe section installation can avoid the interference of medium eddy current on flow detection and make up for the lag of single displacement monitoring.

[0055] Step S3: If the actual displacement of valve core 4 is less than the difference between the target displacement and the allowable displacement deviation, and this state continues for a specified duration, while the actual flow rate of outlet chamber 101 is less than the lower limit of the target outlet flow rate range, then valve core 4 is determined to be stuck. Both insufficient displacement and insufficient flow rate conditions must be met simultaneously, rather than being triggered by a single condition. If only the displacement is insufficient, it may be due to a temporary lack of power in the actuator, such as voltage fluctuations, rather than true sticking. If only the flow rate is insufficient, it may be due to a drop in inlet medium pressure, such as fluctuations in upstream pump output, which is unrelated to the valve core state. Only when both conditions are abnormal simultaneously does it indicate that the valve core cannot move to the target position due to sticking, resulting in the flow rate failing to meet the standard.

[0056] In general, the jamming is determined only after 3-5 seconds, rather than being triggered instantaneously. Under high temperature and high pressure conditions, the medium pressure may fluctuate instantaneously, such as water hammer in the pipeline, which may cause a brief displacement deviation of the valve core or flow fluctuation. If the determination is instantaneous, it will cause unnecessary force increase operation and increase the wear of the actuator and valve core. The 3-5 second delay can filter out instantaneous interference and ensure that the determination result is a true jamming.

[0057] In this way, the multi-condition joint verification mechanism significantly reduces the false alarm rate of jamming, avoids over-response caused by instantaneous interference or abnormal single parameter, reduces invalid actuator actions, extends the service life of components, and ensures accurate identification when jamming occurs, without missing any faults.

[0058] Step S4: Actuator 7 gradually increases the driving force according to the set single increase amplitude, and holds it for a first preset time after each increase, while continuously monitoring the actual displacement of valve core 4 and the actual flow rate of outlet chamber 101; If, during the increase process, the actual displacement of valve core 4 is not less than the difference between the target displacement and the allowable displacement deviation value, and the actual flow rate of outlet chamber 101 is within the target outlet flow rate range, then the increase is stopped, and the current driving force is maintained to stabilize the position of valve core 4; There are differences in the degree of jamming, such as slight foreign object jamming or severe thermal deformation jamming. Gradual increase of force can dynamically adapt the driving force according to the degree of jamming. Slight jamming may be resolved with one increase of force, while severe jamming requires multiple increases of force; The 1-2s holding time provides a response buffer for the valve core. Due to the existence of medium pressure and component inertia, the valve core needs time to overcome the jamming and move stably, avoiding valve core overshoot after the jamming is suddenly released due to excessive force increase.

[0059] In step S4, while maintaining the current driving force to stabilize the position of valve core 4, the actual displacement of valve core 4 and the actual flow rate of outlet chamber 101 are detected every third preset time interval. If the actual displacement of valve core 4 falls below the difference between the target displacement and the allowable displacement deviation value, or the actual flow rate of outlet chamber 101 is less than the lower limit of the target outlet flow rate range, the force increase operation in step S4 is repeated, and the cumulative number of force increases does not exceed the preset number. For example, the parameters are detected every 5-10 seconds, and the cumulative number of force increases does not exceed 3-5 times. Some jamming may be intermittent, such as when a foreign object is temporarily stuck and then loosened by the medium flushing. Intermittent detection can detect the parameter drop in time and avoid continuous high driving force operation. The cumulative number limit is to prevent blind force increase. If the jamming cannot be relieved after 3-5 force increases, it indicates that the cause of the jamming is complex, such as foreign object jamming or component deformation. Continuing to increase the force may cause irreversible damage such as valve core bending or valve stem breakage. It is necessary to stop the force increase and wait for manual maintenance.

[0060] This approach balances adjustment accuracy with component protection: gradual force increase avoids overshoot, dynamic monitoring ensures parameter stability, and the number of cycles limits prevent overload, forming a dual mechanism of self-adaptation and self-protection. It effectively removes minor jamming while providing a safety boundary for serious faults.

[0061] Step S5: If the driving force output by actuator 7 reaches the maximum driving force threshold, but the actual displacement of valve core 4 still does not reach the judgment standard or the actual flow rate of outlet chamber 101 does not enter the target outlet flow rate range, actuator 7 will immediately reduce the driving force to the basic driving force and output a jamming alarm. Long-term operation of the actuator above the rated driving force will cause the motor windings to overheat and the transmission gears to wear more. Immediately reducing the force can prevent the actuator from being overloaded and damaged. Audible and visual alarms or remote signals can notify the staff in time to avoid the jamming from causing abnormal medium flow and affecting downstream processes.

[0062] During the force increase process, if the displacement sensor detects that the vibration amplitude of valve core 4 exceeds the preset vibration threshold, the force increase operation will be paused for a second preset time before being restarted to avoid overshooting of valve core 4 due to sudden release of the jamming. Valve core vibration exceeding the threshold usually means that the jamming is about to be released. For example, if a foreign object loosens, the valve core will generate high-frequency, small-amplitude vibrations. Continuing to increase the force at this time will cause the valve core to move rapidly after the jamming is suddenly released, leading to overshooting. The 2-3 second pause allows the valve core to stabilize during vibration, and force increase can only be resumed after the jamming naturally releases or the vibration weakens, ensuring adjustment accuracy. This setting provides a safety baseline for the actuator and valve core through a limit protection mechanism, preventing overload damage; the vibration warning addresses the risk of instantaneous jamming release, further improving adjustment accuracy; and the alarm function visualizes faults, shortens fault response time, and prevents cascading problems caused by jamming.

[0063] Step S6: By recording the jamming type, corresponding operating parameters, and effective compensation parameters for each jamming event, a historical jamming database is established. The database is used to analyze the occurrence patterns of similar jamming events. In subsequent operations, when the similarity between the real-time monitored operating parameters and the operating characteristics of similar jamming events in the database reaches a preset threshold, on the one hand, predictive adjustments are performed in advance to avoid jamming risks; on the other hand, if jamming still occurs, the corresponding effective single-time force increase amplitude in the database is directly called, without the need for trial and error from the basic driving force, which greatly improves the adjustment efficiency.

[0064] In some embodiments, in step S3, the valve operating temperature is obtained by a temperature sensor. The sensor is installed on the outer wall of the valve body 1 near the communication port 102. The communication port 102 is the core area for medium throttling and pressure reduction. The valve core and sleeve have the most significant thermal deformation at this location. Temperature changes can directly reflect the degree of thermal deformation. The rate of change of the valve operating temperature per unit time is calculated, and a temperature change rate threshold is preset.

[0065] If the rate of change is greater than the preset temperature change rate threshold, and the valve operating temperature is within the preset high temperature range, it is determined to be a heat deformation-dominated jamming. If it is determined to be a heat deformation-dominated jamming, during the force increase process in step S4, the cooling medium circulation is simultaneously started or the cooling medium flow rate is increased. The cooling medium flow rate increases accordingly with the increase of the temperature change rate until the temperature change rate is less than or equal to the preset temperature change rate threshold.

[0066] The root cause of thermal deformation is excessive component temperature. Cooling with a cooling medium, such as demineralized water, which has a high specific heat capacity and good thermal conductivity, can reduce the temperature of the valve core and sleeve, minimize thermal expansion, restore component clearance, and assist in releasing the jamming force. Dynamically adjusting the flow rate with the rate of temperature change can avoid insufficient or excessive cooling. This approach overcomes the current jamming force while eliminating the root cause of thermal deformation through temperature reduction, thus reducing the frequency of subsequent jamming.

[0067] If the rate of change is less than or equal to the preset temperature change rate threshold, or if the valve operating temperature is within the preset low temperature range, it is determined to be a foreign object-dominated jamming. If it is determined to be a foreign object-dominated jamming, during the force increase process in step S4, the actual displacement increment of the valve core 4 is monitored after each force increase. If the displacement increment is less than the preset minimum effective increment, the actuator 7 drives the valve core 4 to move in the opposite direction by a set displacement, and then resumes forward force increase; otherwise, it continues to increase the force in the forward direction at the original force increase amplitude. For example, after force increase, the displacement increment is monitored, and the preset minimum effective increment is 0.05mm. If the displacement increment is <0.05mm, the valve core is driven to move in the opposite direction by 0.2-0.5mm before forward force increase. A displacement increment <0.05mm indicates that the foreign object has not been loosened, and forward force increase may not be able to break through the jamming, or even compact the foreign object. Reverse movement can loosen the foreign object stuck in the gap between the valve core and the sleeve through the impact effect, and it is easier to release the jamming when forward force is increased again. A reverse displacement of 0.2-0.5mm can effectively loosen the foreign object without causing a large fluctuation in flow. This avoids the compaction of foreign objects caused by blindly increasing force, significantly improves the efficiency of releasing foreign object blockages, and reduces frictional damage to the valve core and sleeve.

[0068] In summary, after reading this detailed disclosure, those skilled in the art will understand that the foregoing detailed disclosure is presented by way of example only and is not restrictive. Although not explicitly stated herein, those skilled in the art will understand that the requirements of this application encompass various reasonable changes, improvements, and modifications to the embodiments. These changes, improvements, and modifications are intended to be made by this application and are within the spirit and scope of the exemplary embodiments of this application.

[0069] Furthermore, it should be understood that in the foregoing description of the embodiments of this application, various features are combined in a single embodiment, drawing, or description for the purpose of simplifying the understanding of a feature. However, this does not mean that the combination of these features is necessary, and those skilled in the art may readily identify some of the devices as separate embodiments when reading this application. That is, the embodiments in this application can also be understood as an integration of multiple sub-embodiments. It is also valid when each sub-embodiment contains fewer than all the features of a single foregoing disclosed embodiment.

[0070] Finally, it should be understood that the embodiments disclosed herein are illustrative of the principles of the embodiments of this application. Other modified embodiments are also within the scope of this application. Therefore, the embodiments disclosed herein are merely examples and not limitations. Those skilled in the art can adopt alternative configurations to implement the applications in this application based on the embodiments in this application. Therefore, the embodiments of this application are not limited to the embodiments precisely described in the application.

Claims

1. A high-temperature self-sealing multi-stage pressure reducing regulating valve, characterized in that, The valve assembly includes a valve body, valve seat, valve stem, valve core, balance cylinder, cylinder head, and actuator. The valve body includes an inlet chamber and an outlet chamber, with a connecting port between them. The valve seat is located at the connecting port and has an inner sleeve and an outer sleeve. The inner sleeve has several first through holes, and the outer sleeve has several second through holes offset from the first through holes. The valve core and valve stem are connected and slide vertically within the inner sleeve. The balance cylinder is fitted onto the outer sleeve, inner sleeve, and valve core. The balance cylinder has a sealing ring cover, with an external sealing assembly between the balance cylinder cover and the valve body, and an internal sealing assembly between the balance cylinder cover, the inner sleeve, and the valve core. The valve body has a threaded connection port, and the cylinder head is threaded into this connection port, allowing the valve body, valve seat, and actuator to... The inner sleeve, outer sleeve, balance cylinder, sealing ring gland, in-cylinder sealing assembly, out-of-cylinder sealing assembly, and cylinder head constitute a sealed connection unit. The inner circumference of the lower end of the balance cylinder is provided with a first annular groove for installing the in-cylinder sealing assembly, and the outer circumference of its upper end is provided with a second annular groove for installing the out-of-cylinder sealing assembly. The in-cylinder sealing assembly includes a disc spring, an in-cylinder ring gasket, and an in-cylinder sealing ring arranged in sequence from bottom to top. The end face of the in-cylinder sealing ring that abuts with the first annular groove is set as a matching first conical surface, and the upper side of the first conical surface converges towards the valve stem. The out-of-cylinder sealing assembly includes an out-of-cylinder ring gasket and an out-of-cylinder sealing ring arranged in abutting position. The end faces of the out-of-cylinder ring gasket and the out-of-cylinder sealing ring that abut with each other are set as matching second conical surfaces, and the upper side of the second conical surface of the out-of-cylinder ring gasket converges towards the valve stem.

2. The high-temperature self-sealing multi-stage pressure reducing regulating valve according to claim 1, characterized in that, The valve seat is provided with an inner positioning boss and an outer positioning boss at its upper end. The inner sleeve and the outer sleeve are respectively fitted on the inner positioning boss and the outer positioning boss. The inner sleeve and the outer sleeve are coaxially arranged and a radial gap is provided between them.

3. The high-temperature self-sealing multi-stage pressure reducing regulating valve according to claim 1, characterized in that, The valve body is provided with a valve cover, and a four-ring is provided between the valve cover and the valve body. A self-sealing valve sleeve is fitted on the valve stem. The self-sealing valve sleeve includes a cylindrical part disposed between the valve stem and the valve cover and a disc part disposed within the valve body. A self-sealing ring gasket and a self-sealing pressure gasket are abutted between the disc part and the four-ring. The end face of the self-sealing ring gasket and the four-ring that abuts is configured as a matching third conical surface.

4. The high-temperature self-sealing multi-stage pressure reducing regulating valve according to claim 3, characterized in that, A cooling chamber is formed between the self-sealing valve sleeve, the valve cover, and the four-ring. The valve body is provided with an inlet and an outlet corresponding to the cooling chamber. The cylinder cover is provided with several first channels along the axial direction. The sealing ring cover is provided with second channels corresponding to the first channels. The balance cylinder is provided with a cooling channel. The disc is provided with a channel pipe. The upper end of the channel pipe is connected to the cooling chamber, and its lower end passes through the first channel and is connected to the second channel and the cooling channel.

5. A control method applied to the high-temperature self-sealing multi-stage pressure reducing regulating valve as described in any one of claims 1 to 4, characterized in that, Includes the following steps: Step S1: Set the target displacement and allowable displacement deviation value corresponding to the target opening degree that the valve core needs to achieve. At the same time, set the basic driving force, single force amplification amplitude and maximum driving force threshold of the actuator, and preset the target outlet flow range corresponding to the target opening degree. Step S2: The actuator drives the valve core to move with the basic driving force, and the actual displacement of the valve core is collected in real time by the displacement sensor, and the actual flow rate of the outlet cavity is collected in real time by the flow sensor installed in the outlet cavity. Step S3: If the actual displacement of the valve core is less than the difference between the target displacement and the allowable displacement deviation value, and this state continues for a specified duration, and the actual flow rate of the outlet chamber is less than the lower limit of the target outlet flow rate range, then it is determined that the valve core is stuck. Step S4: The actuator gradually increases the driving force according to the set single force increase range, and maintains it for the first preset time after each force increase, while continuously monitoring the actual displacement of the valve core and the actual flow rate of the outlet cavity; If, during the force-increasing process, the actual displacement of the valve core is not less than the difference between the target displacement and the allowable displacement deviation, and the actual flow rate of the outlet chamber is within the target outlet flow rate range, then the force-increasing process is stopped, and the current driving force is maintained to stabilize the valve core position. Step S5: If the actual displacement of the valve core still does not reach the judgment standard or the actual flow rate of the outlet chamber does not enter the target outlet flow rate range after the driving force output by the actuator reaches the maximum driving force threshold, the actuator will immediately reduce the driving force to the basic driving force and output a jamming alarm. During the power increase process, if the displacement sensor detects that the vibration amplitude of the valve core exceeds the preset vibration threshold, the power increase operation will be paused for a second preset duration and then restarted to avoid the valve core overshooting caused by the sudden release of the jamming.

6. The control method for the high-temperature self-sealing multi-stage pressure reducing regulating valve according to claim 5, characterized in that, In step S4, while maintaining the current driving force to stabilize the valve core position, the actual displacement of the valve core and the actual flow rate of the outlet cavity are detected every third preset time interval. If the actual displacement of the valve core falls below the difference between the target displacement and the allowable displacement deviation value, or the actual flow rate of the outlet cavity is less than the lower limit of the target outlet flow rate range, the force increase operation in step S4 is repeated, and the cumulative number of force increases does not exceed the preset number.

7. The control method for the high-temperature self-sealing multi-stage pressure reducing regulating valve according to claim 5, characterized in that, The valve's operating temperature is obtained through a temperature sensor, the rate of change of the valve's operating temperature per unit time is calculated, and a temperature change rate threshold is preset. If the rate of change is greater than the preset temperature change rate threshold, and the valve operating temperature is within the preset high temperature range, then it is determined to be a heat deformation-dominated jamming type. If the rate of change is less than or equal to the preset temperature change rate threshold, or if the valve operating temperature is within the preset low temperature range, it is determined to be a foreign object-dominated jamming type. If the jamming is determined to be caused by thermal deformation, during the force increase process in step S4, the cooling medium circulation is simultaneously started or the cooling medium flow rate is increased. The cooling medium flow rate increases accordingly with the increase of the temperature change rate until the temperature change rate is ≤ the preset temperature change rate threshold. If the obstruction is determined to be caused by a foreign object, during the force increase process in step S4, the actual displacement increment of the valve core is monitored after each force increase. If the displacement increment is less than the preset minimum effective increment, the actuator drives the valve core to move the set displacement in the opposite direction and then resumes the forward force increase. Otherwise, the forward force increase continues at the original force increase amplitude.

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