Planetary shifting mechanism for a valve and method of driving the same

Abstract

The present application belongs to the technical field of valve, especially relates to a planetary shifting mechanism for valve and a driving method thereof, which comprises a shell, one side of the shell is provided with a driving rod, a transmission assembly for changing transmission path and speed ratio is arranged in the shell, an electromagnet is arranged on one side in the shell, and an output end of the electromagnet is rigidly connected with a shifting piece and a sliding sleeve to drive the sliding sleeve to move in the axial direction, through the double monitoring of the elastic positioning assembly and the position sensor, the wear state of the sliding sleeve and the internal gear ring tooth can be captured in real time without stopping and disassembling, the pressure sensor, the ball and the multi-stage hole of the elastic positioning assembly are used to cross-verify the spring compression amount of the mechanical signal, the groove depth mutation and the displacement signal, interference misjudgment is excluded, meanwhile, the mechanical feedback is formed by the compensation hole and the limiting hole, the overtravel compensation of the sliding sleeve is avoided, the component collision or tooth fracture is effectively prevented, and the sudden failure probability is reduced.

Description

Technical Field

[0001] This invention belongs to the field of valve technology, and particularly relates to a planetary shifting mechanism for valves and its driving method. Background Technology

[0002] As a key control element in industrial pipeline systems, the reliability, efficiency, and lifespan of valves are of paramount importance. To improve driving performance, existing technologies often employ planetary gear shifting mechanisms to switch between two output modes: low-speed high torque and high-speed low torque. This adapts to the different needs of overcoming high static friction in the initial stage of valve opening and rapid and accurate positioning when approaching the target position.

[0003] Currently, the planetary shift mechanism consists of a sun gear, planet gears, a planet carrier, and an internal gear ring. It uses an electromagnet to drive the shift fork to control the axial movement of the shift sleeve, thereby fixing or releasing the internal gear ring and changing the transmission path and speed ratio.

[0004] The reliability of this mechanism relies heavily on the integrity of the locking structure between the sliding sleeve and the internal gear ring. However, during frequent shifting cycles, the meshing teeth of the sliding sleeve and the internal gear ring are prone to wear due to impact and friction, resulting in a reduction in the effective engagement depth and causing the following three problems:

[0005] First: The existing solution relies on a single displacement sensor or shutdown for disassembly and inspection, which cannot reliably monitor the wear status in real time. This poses a risk of sudden failure, resulting in no mechanical feedback for the overtravel compensation of the sliding sleeve, and excessive movement leading to collisions or tooth breakage.

[0006] Second: During the gear switching process of the valve planetary shift mechanism, the teeth of the sliding sleeve and the internal gear ring will wear due to long-term engagement or disengagement, which will cause the effective engagement depth of the two to gradually decrease. In the existing technology, the electromagnetic thrust and stroke are fixed parameters. After the teeth wear, the gap will increase, which will easily lead to insufficient engagement force or loose engagement and slippage, affecting the reliability of valve drive.

[0007] Third: There are no compensation and protection measures designed for different wear stages. There is no precise adjustment for mild wear and no limit shutdown protection for severe wear, which leads to reduced efficiency, irreversible damage to components, and high maintenance costs. Summary of the Invention

[0008] In view of this, the present invention aims to solve three major problems existing in the existing valve planetary shifting mechanism: First, it relies on a single displacement sensor or shutdown inspection, which cannot reliably monitor wear in real time, and the lack of mechanical feedback for overtravel compensation of the sliding sleeve can easily lead to collisions or tooth breakage; Second, the electromagnetic thrust and stroke are fixed, and the increased gap after tooth wear can easily lead to insufficient meshing force or slippage, affecting the reliability of the drive; Third, there are no compensation and protection measures for different wear stages, and there is no precise adjustment for light wear and no limit shutdown protection for heavy wear, resulting in reduced efficiency, component damage, and high maintenance costs.

[0009] To achieve the above objectives, the technical solution of the present invention is implemented as follows:

[0010] This invention discloses a planetary shifting mechanism for valves, comprising a housing, a drive rod disposed on one side of the housing, a transmission component for changing the transmission path and speed ratio inside the housing, an electromagnet disposed on one side inside the housing, the output end of the electromagnet being rigidly connected to a sliding sleeve via a shifting element to drive the sliding sleeve to move axially, a valve port being provided at the end of the housing away from the drive rod, a valve disc being assembled inside the valve port and linked to the transmission component, and a spline being provided inside the housing to constrain the sliding sleeve to move only axially;

[0011] An elastic positioning component is disposed inside the housing and adapted to the sliding sleeve, and is used to detect the change in resistance encountered by the sliding sleeve during its movement to provide feedback on the wear status.

[0012] An adjustable thrust assembly is disposed between the housing and the electromagnet. It is used to adjust the thrust of the electromagnet to change the preload after the teeth of the sliding sleeve and the transmission assembly wear, so as to adapt to the wear gap and maintain a stable meshing thrust.

[0013] Furthermore, the transmission assembly includes:

[0014] The sun gear is coaxially and fixedly connected to the drive rod, and the drive rod can drive the sun gear to rotate synchronously when it rotates.

[0015] The system includes planetary gears and a star carrier. The planetary gears are provided with at least three of them. Each planetary gear is rotatably mounted on the circumferential edge of the star carrier via a pin. The axes of all planetary gears are parallel to the axis of the sun gear. The planetary gears simultaneously mesh with the outer circumferential teeth of the sun gear and the inner circumferential teeth of the inner gear ring.

[0016] An internal gear ring, wherein the outer peripheral wall of the internal gear ring is provided with an external tooth structure, and the inner side wall of the sliding sleeve is provided with a straight section tooth adapted to the external tooth structure.

[0017] Furthermore, the housing has a side groove extending axially along the sliding sleeve on its side wall, and a straight section hole coaxially corresponding to the side groove is formed on the side of the sliding sleeve facing the side groove. The elastic positioning component includes a pressure sensor, a first spring, and a positioning pin. The pressure sensor is fixedly installed at the bottom of the side groove away from the engaging end of the sliding sleeve, and the signal output end of the pressure sensor is electrically connected to the controller of the mechanism. One end of the first spring abuts against the end face of the pressure sensor facing the sliding sleeve, and the other end of the first spring is fixedly connected to one end of the positioning pin. The first spring is always in a pre-compressed state. The end of the positioning pin away from the first spring extends into the straight section hole. The outer peripheral wall of the positioning pin is axially slidingly fitted with the inner wall of the side groove and the inner wall of the straight section hole. A position sensor is fixedly installed on one side of the housing corresponding to the axial movement path of the sliding sleeve. The side of the sliding sleeve facing the position sensor has an axially extending mounting boss. A probe is fixedly connected to one end of the mounting boss, and the other end of the probe extends axially and extends into the detection cavity of the position sensor.

[0018] Furthermore, the elastic positioning component also includes a ball bearing. The end of the positioning pin away from the first spring has a spherical groove. The ball bearing is embedded in the spherical groove, and part of the spherical surface of the ball bearing protrudes from the end face of the positioning pin. The ball bearing can rotate freely in the spherical groove, and its spherical surface protruding from the positioning pin contacts the inner wall of the straight section hole.

[0019] Furthermore, the sliding sleeve has a compensation hole coaxially connected to the straight section hole on one side, which is adapted to the compensation stroke after the sliding sleeve is worn. The groove depth of the compensation hole is half the groove depth of the straight section hole. The sliding sleeve is installed with a gradually widening tooth at a position coaxial with and adjacent to the straight section tooth. The tooth tip width of the gradually widening tooth gradually increases from the end of the straight section tooth to the outside along the axial direction of the sliding sleeve.

[0020] Furthermore, the sliding sleeve has a limiting hole coaxially connected to the compensation hole at the end of the compensation hole away from the straight section hole. The diameter of the limiting hole is adapted to the outer diameter of the ball. An annular mounting groove is formed in the middle of the inner side wall of the limiting hole. A spring-loaded trigger switch is embedded in the annular mounting groove. The trigger end of the trigger switch protrudes from the inner wall of the limiting hole, and its signal output end is electrically connected to the controller through a wire inside the sliding sleeve.

[0021] Furthermore, the housing has an axial hole for axial sliding of the electromagnet, and a first slot in a circular array is formed on the outer side of the housing, communicating with the axial hole. Three second slots are formed on the side of the housing opposite the sliding sleeve to the electromagnet, and the second slots are evenly distributed circumferentially along the axial hole. The adjustable thrust assembly includes:

[0022] A spring limiting rod is fixedly installed in the first slot, and its axis is parallel to the sliding direction of the electromagnet.

[0023] The slider is fixed to the outer peripheral wall of the electromagnet, and the slider is slidably engaged with the spring limiting rod. A reset spring for resetting the electromagnet is sleeved on the spring limiting rod.

[0024] A conical plate is coaxially fixed to the end of the electromagnet away from the sliding sleeve, and its outer peripheral wall is in contact with the inner wall of the axial hole.

[0025] The drive unit is a linear drive element, and there are three drive units. Each group of drive units is fixedly installed in three second slots, with its telescopic end facing the conical plate.

[0026] A metal gasket is magnetically attracted to the telescopic end of the drive motor, and both sidewalls of the metal gasket are set as bevels.

[0027] Furthermore, a current regulation module is installed inside the electromagnet.

[0028] Furthermore, the thicknesses of the three metal gaskets are 0.5 mm, 1.0 mm, and 2.0 mm, respectively.

[0029] A method for driving a planetary shift mechanism for a valve includes the following steps:

[0030] S1: Valve opening / closing and speed ratio switching: When opening / closing is required, the electromagnet drives the sliding sleeve to engage the internal gear ring, and the star frame drives the valve disc at low speed and high torque; when high speed is required, the electromagnet drives the sliding sleeve to disengage from the internal gear ring in the opposite direction, and the transmission returns to high speed and low torque.

[0031] S2: Wear-free monitoring: The positioning pin ball in the elastic positioning component contacts the straight section hole of the sliding sleeve. The pressure sensor and position sensor send basic resistance and normal stroke signals respectively, and the controller determines that the engagement is normal.

[0032] S3: Mild to moderate wear determination: After the teeth wear out, the sliding sleeve over-travels, which drives the positioning pin to compress the spring. The pressure sensor and position sensor send resistance increase and overtravel signals. The controller determines the wear and triggers compensation.

[0033] S4: Confirmation of medium compensation zone: The sliding sleeve enters the compensation stroke, the positioning pin enters the compensation hole, and the constraint force increases sharply due to the halving of the groove depth. The pressure sensor sends a high resistance sudden change signal. Combined with the position signal, the compensation zone is confirmed.

[0034] S5: Thrust Adjustment Compensation: The controller instructs the drive motor to push out the corresponding metal pad according to the degree of wear, and in conjunction with the electromagnet current increase, the thrust is increased to adapt to the wear.

[0035] S6: Over-wear protection: Over-compensation stroke of the sliding sleeve, ball entering the limit hole triggers the switch, combined with the limit signals of the pressure sensor and position sensor, the controller commands a shutdown warning.

[0036] S7: Reset after maintenance: After the component is repaired, the controller commands the metal pad to be retracted, the current to be restored, the electromagnet to be reset, the positioning pin to be returned to the straight section hole, and the system to be restored to its initial state.

[0037] Compared with the prior art, the planetary shifting mechanism for valves and its driving method described in this invention have the following advantages:

[0038] 1. This invention uses a dual monitoring system of an elastic positioning component and a position sensor to capture the wear status of the sliding sleeve and the internal gear ring teeth in real time without stopping the machine for disassembly. Specifically, the elastic positioning component uses a pressure sensor, ball bearings, and multi-stage holes (straight section holes, compensation holes, and limit holes) to cross-verify the spring compression and groove depth changes of mechanical signals with displacement signals, eliminating interference and misjudgment. At the same time, the compensation holes and limit holes form mechanical feedback to avoid excessive over-compensation of the sliding sleeve, effectively preventing component collisions or tooth breakage and reducing the probability of sudden failure.

[0039] 2. This invention, through an adjustable thrust component, combined with wear monitoring results, and through the interplay of overlapping metal shims and electromagnet current adjustment, can dynamically adjust the thrust according to the degree of tooth wear. When the wear gap increases, the mechanical preload and electromagnetic force are simultaneously increased to compensate for the gap effect, avoid insufficient meshing force or slippage caused by fixed thrust, ensure reliable meshing during valve driving, and improve transmission stability.

[0040] 3. This invention designs different solutions for light, moderate, and heavy wear stages. For example, light wear is addressed through precise thrust adjustment, moderate wear through a compensation mechanism triggered by a compensation hole, and heavy wear through a forced shutdown warning via a limit hole and a trigger switch, forming a full-cycle graded protection. This avoids losses caused by over-adjustment during light wear and prevents irreversible damage to components caused by heavy wear, extending the life of the mechanism and reducing maintenance frequency and costs. Moreover, the involute tooth, with its gradually increasing tooth width from the end of the straight section tooth outwards, inserts into the wear gap with a smaller tooth width in the initial stage of meshing. Then, the involute characteristic guides the internal gear ring and the straight section tooth to be precisely aligned, avoiding misalignment, jamming, and rigid collision, reducing meshing impact wear, and helping to improve meshing stability during light and moderate wear. Attached Figure Description

[0041] Figure 1 This is a longitudinal cross-sectional view of the overall structure of the present invention;

[0042] Figure 2 This is a partial schematic diagram of the side of the sliding sleeve of the present invention;

[0043] Figure 3 This is a schematic diagram of the elastic positioning component of the present invention;

[0044] Figure 4This is a schematic diagram of the straight section teeth of the sliding sleeve, the compensation hole, and the limiting hole of the present invention;

[0045] Figure 5 This is for Figure 1 A magnified view of part A in the image;

[0046] Figure 6 This is a schematic diagram of the housing and conical plate of the present invention.

[0047] The markings in the diagram are as follows:

[0048] 1. Housing; 10. Side groove; 100. First groove; 101. Second groove; 11. Drive rod; 12. Transmission assembly; 121. Sun gear; 122. Planet gears; 123. Planetary carrier; 124. Internal gear ring; 13. Electromagnet; 14. Sliding sleeve; 141. Straight section tooth; 1410. Involute tooth; 142. Straight section hole; 1420. Compensation hole; 143. Limiting hole; 144. Trigger switch; 15. Valve port; 16. Valve disc;

[0049] 2. Elastic positioning assembly; 21. Pressure sensor; 22. First spring; 23. Positioning pin; 24. Ball bearing; 25. Position sensor; 26. Detector rod; 211. Adjustable thrust assembly; 212. Spring limit rod; 213. Slider; 214. Conical plate; 215. Drive motor; 216. Metal gasket. Detailed Implementation

[0050] The technical solutions of the embodiments of this application will be clearly described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this application. All other embodiments obtained by those skilled in the art based on the embodiments of this application are within the scope of protection of this application.

[0051] See Figures 1-2As shown, the present invention provides a planetary shifting mechanism for a valve, comprising a housing 1, a drive rod 11 disposed on one side of the housing 1, a transmission assembly 12 for changing the transmission path and speed ratio inside the housing 1, an electromagnet 13 disposed on one side inside the housing 1, the output end of the electromagnet 13 being rigidly connected to a sliding sleeve 14 via a shifting element to drive the sliding sleeve 14 to move axially, a valve port 15 being provided at the end of the housing 1 away from the drive rod 11, a valve disc 16 being fitted inside the valve port 15 and linked to the transmission assembly 12, and a spline being provided inside the housing 1 to constrain the sliding sleeve 14 to move only axially; the transmission assembly 12 includes a sun gear 121, the sun gear 121 being coaxially and fixedly connected to the drive rod 11, and the drive rod 11 rotating to drive the sun gear 121 to rotate synchronously. The transmission assembly 12 consists of planetary gears 122 and a star carrier 123. At least three planetary gears 122 are provided, each of which is rotatably mounted on the circumferential edge of the star carrier 123 via a pin. The axes of all planetary gears 122 are parallel to the axis of the sun gear 121. The planetary gears 122 simultaneously mesh with the outer peripheral teeth of the sun gear 121 and the inner peripheral teeth of the inner gear ring 124, forming a planetary transmission structure. The inner gear ring 124 has an outer tooth structure on its outer peripheral wall, and the inner sidewall of the sliding sleeve 14 has a straight section tooth 141 adapted to the outer tooth structure. When the sliding sleeve 14 moves along the spline axis, it can engage or disengage with the outer tooth structure through the straight section tooth 141 to fix or release the inner gear ring 124, thereby changing the transmission path and speed ratio of the transmission assembly 12.

[0052] It should be noted that the external power source drives the drive rod 11 to rotate, and the sun gear 121, which is coaxially fixed with the drive rod 11, rotates synchronously, transmitting power to the transmission assembly 12. When the sun gear 121 rotates, its outer circumferential teeth drive the meshing planet gears 122 to rotate. The planet gears 122 are mounted on the star carrier 123 through pins. While rotating, they also drive the star carrier 123 to revolve around the axis of the sun gear 121. At this time, the internal gear ring 124 is not fixed and can rotate freely. The transmission assembly 12 is in a high-speed transmission state. The star carrier 123 has a high rotational speed and a small output torque. The controller commands the electromagnet 13 to start, and its output end pushes the sliding sleeve 14 to move along the spline axis of the housing 1 through the lever. The straight section teeth 141 on the inner side of the sliding sleeve 14 mesh with the outer tooth structure on the outer circumference of the internal gear ring 124, fixing the internal gear ring 124. At this time, the planetary gear 122 maintains its rotation under the drive of the sun gear 121, and is constrained by the reaction force of the tooth surface of the internal gear ring 124, and revolves around the axis of the sun gear 121. The planetary gear 122 is stably matched with the star carrier 123, and its revolution directly drives the star carrier 123 to rotate synchronously around the axis of the sun gear 121, forming a same-direction reduction transmission. Finally, the star carrier 123 outputs power at a lower speed and a larger torque. This rotation is transmitted to the valve disc 16 in the valve port 15 through the output shaft, driving the valve disc 16 to rotate or translate, thereby realizing the opening and closing of the valve.

[0053] When it is necessary to switch back to the high-speed state, the electromagnet 13 drives the sliding sleeve 14 to retract along the spline in the reverse direction. The straight section tooth 141 disengages from the outer tooth of the internal gear ring 124, and the internal gear ring 124 resumes free rotation. The planetary transmission returns to the high-speed, low-torque state, and the valve disc 16 operates at the corresponding speed. The power of the drive rod 11 is transmitted to the valve disc 16 through the planetary transmission assembly 12. The speed ratio is switched to adapt to the opening and closing torque requirements of the valve under different working conditions.

[0054] See Figures 1-3 As shown, the housing 1 has a side groove 10 extending axially along the sliding sleeve 14 on its side wall corresponding to the sliding sleeve 14. The sliding sleeve 14 has a straight section hole 142 coaxially corresponding to the side groove 10 on its side facing the side groove 10. An elastic positioning component 2 is disposed inside the housing 1 and adapted to the sliding sleeve 14. It is used to detect changes in resistance experienced by the sliding sleeve 14 during movement to provide feedback on its wear condition. The elastic positioning component 2 includes a pressure sensor 21, a first spring 22, and a positioning pin 23. The pressure sensor 21 is fixedly installed at the bottom of the side groove 10 away from the engaging end of the sliding sleeve 14, and its signal output terminal is electrically connected to the controller of the mechanism. One end of the first spring 22 abuts against the end face of the pressure sensor 21 facing the sliding sleeve 14, and the other end of the first spring 22 is fixedly connected to one end of the positioning pin 23. The first spring 22 is always in a pre-compressed state. The end of the positioning pin 23 away from the first spring 22 extends into the straight section hole 142, and the outer peripheral wall of the positioning pin 23 is flush with the side groove 10. The inner wall of the sliding sleeve 14 and the inner wall of the straight section hole 142 are axially sliding. When the sliding sleeve 14 moves along the spline axis, the positioning pin 23 can slide axially synchronously with the straight section hole 142, and trigger the pressure sensor 21 to feed back the resistance signal through the compression change of the first spring 22. A position sensor 25 is fixedly installed on one side of the housing 1 corresponding to the axial movement path of the sliding sleeve 14. The position sensor 25 is a linear displacement sensor, and its signal output end is electrically connected to the controller of the mechanism. The sliding sleeve 14 has an axially extending mounting boss on the side facing the position sensor 25. One end of the mounting boss is fixedly connected to a probe rod 26, and the other end of the probe rod 26 extends axially and extends into the detection cavity of the position sensor 25. When the sliding sleeve 14 moves along the spline axis, the probe rod 26 moves axially synchronously with the sliding sleeve 14. The position sensor 25 collects the axial position data of the sliding sleeve 14 in real time through the displacement change of the probe rod 26 and transmits the data to the controller, forming a dual monitoring with the pressure signal of the elastic positioning component 2.

[0055] It should be noted that in the initial state without wear: when the sliding sleeve 14 is not worn, its axial movement range is within the normal stroke. The positioning pin 23 extends into the straight section hole 142 of the sliding sleeve 14. Since the first spring 22 is in a pre-compressed state, the positioning pin 23 and the inner wall of the straight section hole 142 remain in contact. At this time, the spring compression is stable, and the pressure sensor 21 feeds back the basic resistance signal, indicating the corresponding no-wear state. At the same time, the position sensor 25 monitors the axial position of the sliding sleeve 14 in real time through the probe rod 26 and outputs a normal stroke signal. If the corresponding new product standard stroke is S, the controller receives two sets of signals and determines that the engagement state of the sliding sleeve 14 is normal.

[0056] When wear occurs (slight to moderate wear): As the teeth of the sleeve 14 and the internal gear ring 124 wear, the sleeve 14 needs to move axially beyond its normal stroke to achieve effective engagement. At this time, the straight section hole 142 of the sleeve 14 drives the positioning pin 23 to move synchronously along the side groove 10. The thrust of the inner wall of the straight section hole 142 on the positioning pin 23 increases, causing the first spring 22 to be further compressed, indicating that the compression increases with the increase of wear. The pressure sensor 21 detects the change in spring compression and outputs a resistance increasing signal. The resistance is positively correlated with the wear and sends feedback to the controller that the sleeve 14 has entered the wear stage. The position sensor 25 simultaneously monitors that the stroke of the sleeve 14 exceeds S and outputs an overtravel displacement signal. The two sets of signals cross-verify, the controller confirms the degree of wear and starts subsequent compensation.

[0057] In the state of excessive wear (near the limit): When wear intensifies and the travel of the sleeve 14 approaches the limit, the locating pin 23 is pushed to the end of the side groove 10 by the straight section hole 142. The compression of the first spring 22 reaches the threshold, the pressure sensor 21 outputs the limit resistance signal, and at the same time the position sensor 25 detects that the travel is close to the safety threshold (e.g., S×120%). The controller receives the dual limit signals, determines the risk of excessive wear, and triggers a warning or shutdown protection to avoid tooth breakage.

[0058] This invention addresses the limitations of traditional single sensors by employing dual verification through mechanical resistance and displacement signals. This effectively avoids misjudgments caused by electromagnetic interference and mechanical vibration, ensuring the accuracy of wear condition perception. Furthermore, the pressure sensor 21 provides real-time feedback on the contact resistance between the sliding sleeve 14 and the positioning pin 23 via spring compression, allowing for early detection of wear trends before the sliding sleeve 14 reaches its limit position. The position sensor 25 precisely quantifies the stroke increment. The combination of these two sensors enables dynamic monitoring and trend prediction, providing timely information for subsequent proactive compensation.

[0059] See Figure 3As shown, the elastic positioning component 2 also includes a ball 24. The end of the positioning pin 23 away from the first spring 22 has a spherical groove. The ball 24 is embedded in the spherical groove, and part of the spherical surface of the ball 24 protrudes from the end face of the positioning pin 23. The ball 24 can rotate freely in the spherical groove. Its spherical surface protruding from the positioning pin 23 contacts the inner wall of the straight section hole 142 to form a rolling connection.

[0060] When the sliding sleeve 14 moves along the spline axis, the inner wall of the straight section hole 142 pushes the ball 24, causing it to rotate freely in the spherical groove. At the same time, it drives the positioning pin 23 to slide synchronously along the side groove 10. At this time, the sliding friction between the positioning pin 23 and the straight section hole 142 is converted into rolling friction, which significantly reduces the frictional resistance. It can also greatly reduce the wear between the positioning pin 23 and the inner wall of the straight section hole 142, avoid hole wall scratches and positioning pin 23 deformation caused by long-term sliding, and extend the service life of the sliding sleeve 14 and the elastic positioning component 2.

[0061] See Figure 2 As shown, the sliding sleeve 14 has a compensation hole 1420 on one side of the straight section hole 142, which is coaxially connected to the straight section hole 142. The axial length of the compensation hole 1420 is 2-3mm, which is adapted to the compensation stroke after the sliding sleeve 14 is worn. The groove depth of the compensation hole 1420 is half the groove depth of the straight section hole 142. The sliding sleeve 14 is coaxial with and adjacent to the straight section tooth 141, and the tooth tip width of the widening tooth 1410 gradually increases from the end of the straight section tooth 141 outward along the axial direction of the sliding sleeve 14.

[0062] It should be noted that when the sliding sleeve 14 moves within the standard stroke (S), the ball 24 of the positioning pin 23 contacts the inner wall of the straight section hole 142. Since the groove depth of the straight section hole 142 is relatively deep (e.g., set to 4mm), the compression of the first spring 22 is stable. The pressure sensor 21 outputs a low resistance reference signal, which matches the displacement signal within S of the position sensor 25. The controller determines that it is in a normal engagement state.

[0063] When tooth wear causes the sleeve 14 to move beyond S (entering the compensation stroke), the end of the straight section hole 142 of the sleeve 14 connects with the compensation hole 1420. The positioning pin 23 moves into the compensation hole 1420 with the sleeve 14. Since the groove depth of the compensation hole 1420 is only half of that of the straight section hole 142 (e.g., 2mm), the radial constraint force of its inner wall on the ball 24 suddenly increases, forcing the positioning pin 23 to move inward to the side groove 10. The first spring 22 is further compressed, and the pressure sensor 21 detects a sudden increase in the resistance signal. With the double verification of the over-S displacement signal from the position sensor 25, the controller confirms that the sleeve 14 has entered the wear compensation zone.

[0064] The axial length of the compensation hole 1420 is set to 2-3mm (matching the preset maximum safety compensation stroke). When the positioning pin 23 moves to the end within the compensation hole 1420, it means that the sliding sleeve 14 has reached the critical value of moderate wear. The pressure sensor 21 continuously outputs a high resistance signal, providing a pre-signal for subsequent excessive wear warning. Compared with the design of a single straight hole 142, the compensation hole 1420 forms a clear mechanical signal threshold through abrupt changes in groove depth, dividing the wear state into two stages: normal and compensation. This avoids the ambiguity caused by slow changes in resistance signal and provides a clear basis for the controller to trigger actions.

[0065] When the teeth of the sliding sleeve 14 and the internal gear ring 124 develop a gap due to wear, during the axial movement and meshing process of the sliding sleeve 14, the involute tooth 1410 contacts the outer teeth of the internal gear ring 124 before the straight tooth 141. Since the tooth tip width of the involute tooth 1410 gradually increases from the end of the straight tooth 141 outwards, the tooth tip width at its initial contact end is relatively small, so it can be inserted into the gap formed by wear first. The gradually increasing tooth tip width guides the outer teeth of the internal gear ring 124 to accurately align with the straight tooth 141 of the sliding sleeve 14, avoiding tooth misalignment, jamming or rigid collision caused by the gap, reducing the impact wear at the moment of meshing, especially in light to moderate wear scenarios, it can help improve meshing stability.

[0066] See Figure 4 As shown, the sliding sleeve 14 has a limiting hole 143 coaxially connected to the compensation hole 1420 at the end of the compensation hole 1420 away from the straight section hole 142. The diameter of the limiting hole 143 is adapted to the outer diameter of the ball 24 to ensure that the ball 24 can be embedded in the limiting hole 143. An annular mounting groove is provided in the middle of the inner side wall of the limiting hole 143. A spring-loaded trigger switch 144 is embedded in the annular mounting groove. The trigger end of the trigger switch 144 protrudes from the inner wall of the limiting hole 143, and its signal output end is electrically connected to the controller through the wire inside the sliding sleeve 14.

[0067] When the sliding sleeve 14 moves to its end within the compensation hole 1420 (i.e., when moderate wear approaches its limit), the ball 24 of the locating pin 23 slides along the inner wall of the compensation hole 1420 to the point where it connects with the limiting hole 143. At this time, the pressure sensor 21 continuously outputs a high resistance signal, and the position sensor 25 reports that the travel is approaching its limit (e.g., S×120%). The controller is already in a warning state. If the tooth wear further intensifies, the sliding sleeve 14 needs to continue moving axially beyond the range of the compensation hole 1420 (entering the limit compensation position). The ball 24 slides into the limiting hole 143 along with the locating pin 23. Since the diameter of the limiting hole 143 matches the outer diameter of the ball 24, the ball 24 is precisely embedded in the hole. Its spherical surface presses against the trigger switch 144 on the inner wall of the limiting hole 143. After being pressed, the trigger switch 144 generates a limit wear signal. The signal is transmitted to the controller via the internal wires of the sliding sleeve 14. It is then triple-verified with the limit resistance signal from the pressure sensor 21 and the over-limit travel signal from the position sensor 25 to confirm that the sliding sleeve 14 has reached an uncompensable wear state. After receiving the limit wear signal, the controller immediately instructs the electromagnet 13 to stop driving and triggers an external warning to forcibly terminate the shifting action. This prevents the sliding sleeve 14 from breaking its teeth or colliding rigidly with other components due to excessive movement. The spring-loaded characteristic of the trigger switch 144 ensures that if the sliding sleeve 14 moves in the opposite direction (such as during maintenance reset), the trigger end can automatically reset without affecting subsequent testing.

[0068] This invention achieves step-by-step monitoring of wear status through three-stage holes: from normal stroke (straight section hole 142) to moderate wear (compensation hole 1420) and then to excessive wear (limiting hole 143). The limiting hole 143 serves as the last line of defense, solving the problem of component damage caused by unlimited compensation and providing ultimate protection for excessive wear of the sliding sleeve 14.

[0069] See Figures 5-6As shown, the housing 1 has an axial hole for the axial sliding of the electromagnet 13. The housing 1 has a first slot 100 arranged in a ring array on the outer side of the electromagnet 13, which communicates with the axial hole. The housing 1 has three second slots 101 on the side of the electromagnet 13 away from the sliding sleeve 14, evenly distributed circumferentially along the axial hole. An adjustable thrust assembly 211 is located between the housing 1 and the electromagnet 13. It is used to adjust the thrust of the electromagnet 13 to change the preload after wear of the meshing teeth of the sliding sleeve 14 and the transmission assembly 12, adapting to the wear gap and maintaining a stable meshing thrust. A current adjustment module is installed inside the electromagnet 13. The adjustable thrust assembly 211 includes a spring limiting rod 212, which is fixedly installed in the first slot 100, with its axis aligned with the electromagnet 13. The sliding direction of 3 is parallel; slider 213, slider 213 is fixed to the outer peripheral wall of electromagnet 13, and slider 213 is slidably engaged with spring limit rod 212, and spring limit rod 212 is sleeved with a reset spring for resetting electromagnet 13; conical plate 214, conical plate 214 is coaxially fixed to the end of electromagnet 13 away from sliding sleeve 14, its outer peripheral wall is in contact with the inner wall of axial hole; drive motor 215, drive motor 215 is a linear drive element, there are three, each group of drive motors 215 is fixedly installed in three second slots 101, and its telescopic end faces conical plate 214; metal shim 216, metal shim 216 is attracted by magnetism in the telescopic end of drive motor 215, both side walls of metal shim 216 are set as inclined surfaces, and the thicknesses of the three metal shims 216 are 0.5mm, 1.0mm and 2.0mm respectively.

[0070] It should be noted that, under the elastic constraint of the return spring on the spring limit rod 212, the electromagnet 13 remains in its initial position within the axial hole. At this time, the conical plate 214 and the metal washer 216 are not in contact. The thrust of the electromagnet 13 is determined by the reference current output by its internal current adjustment module. This thrust matches the meshing requirements of the sliding sleeve 14 when there is no wear, ensuring stable meshing of the teeth in the initial state. The slider 213 fixed on the outer peripheral wall of the electromagnet 13 forms a sliding fit with the spring limit rod 212, strictly limiting the electromagnet 13 to only make linear movements along the axial hole, avoiding thrust offset or component jamming caused by radial sway.

[0071] Based on the degree of wear, such as 0.5mm for light wear, 1.0mm for moderate wear, and 2.0mm for heavy wear of the metal pad 216, the controller instructs the corresponding drive motors 215 in the three second slots 101 to activate. This activates the drive motors 215 that magnetically attract metal pads 216 of matching thicknesses. The controller then activates the drive motors 215 that attract metal pads 216 of different thicknesses. The extension end of the drive motor pushes the metal pads 216 out. Guided by the outer conical surface of the conical plate 214, one inclined side of the metal pad 216 smoothly enters the axial hole and fits tightly against the conical plate 214. Guided by the inclined side of the previous metal pad 216, the other inclined side of the metal pad 216 achieves the desired fit for each group of metal pads. The metal shims 216 are stacked and combined. After the metal shims 216 are attached to the conical plate 214, the radial thrust of the drive motor 215 is converted into axial thrust through the inclined surface. This forces the electromagnet 13 to overcome the spring force of the return spring and move along the axial hole towards the sliding sleeve 14. The magnitude of the mechanical preload is positively correlated with the total thickness of the metal shims 216. The greater the total thickness of the metal shims 216, the greater the axial thrust, the more the electromagnet 13 moves towards the sliding sleeve 14, and the stronger the preload, which can offset a larger wear gap. Moreover, at the same time as the mechanical preload, the current adjustment module inside the electromagnet 13 synchronously responds to the controller signal and increases the input current based on the reference current.

[0072] When the sliding sleeve 14 is repaired after wear, the controller instructs the drive motor 215 to retract the metal pad 216. The metal pad 216 is magnetically re-adsorbed into the telescopic end of the drive motor 215 to prevent it from loosening and falling off. At the same time, the current adjustment module restores the reference current, and the electromagnet 13 returns to its initial position under the elastic force of the reset spring. The conical plate 214 and the metal pad 216 are no longer in contact, and the system waits for the next wear compensation trigger.

[0073] A method for driving a planetary shift mechanism for a valve includes the following steps:

[0074] When the valve needs to be opened or closed, the electromagnet 13 drives the sliding sleeve 14 to move along the spline. Its straight section tooth 141 meshes with the outer tooth of the internal gear ring 124 to fix the internal gear ring 124. The planetary gear 122 only rotates on its own axis, driving the planetary carrier 123 to rotate at low speed and high torque, which drives the valve disc 16 to move. When high speed is required, the electromagnet 13 drives the sliding sleeve 14 to retract in the opposite direction, the internal gear ring 124 is free, and the transmission returns to high speed and low torque.

[0075] When there is no wear, the positioning pin 23 and ball 24 in the elastic positioning component 2 are in contact with the straight section hole 142 of the sliding sleeve 14, the spring is compressed and stable, the pressure sensor 21 sends a basic resistance signal, the position sensor 25 obtains a normal stroke signal through the probe rod 26, the controller receives the two signals and determines that the engagement is normal.

[0076] After the teeth wear out, the sliding sleeve 14 needs to engage beyond the normal stroke, which drives the positioning pin 23 to move and further compress the spring. The pressure sensor 21 sends a resistance increase signal, and the position sensor 25 detects the overtravel. The two signals cross-verify, and the controller determines that the wear is light to moderate and triggers compensation.

[0077] When the sliding sleeve 14 moves to the compensation stroke, the positioning pin 23 enters the compensation hole 1420. Because the groove depth of the compensation hole 1420 is halved, the constraint force on the ball 24 increases sharply, the first spring 22 is compressed again, the pressure sensor 21 sends a high resistance sudden change signal, combined with the overtravel signal of the position sensor 25, the controller confirms that it has entered the medium wear compensation zone.

[0078] According to the degree of wear, the controller instructs the drive motor 215 to push out a metal shim 216 of corresponding thickness or to add a metal shim 216. The inclined surface of the metal shim 216 cooperates with the conical plate 214 to push the electromagnet 13 to move. At the same time, the current adjustment module increases the current, and the mechanical preload and electromagnetic force are combined to increase the thrust.

[0079] When the sliding sleeve 14 exceeds the compensation stroke, the ball 24 slides into the limit hole 143 and presses the trigger switch 144, sending a limit wear signal. Combined with the limit signals from the pressure and position sensors 25, the controller commands the electromagnet 13 to stop and issue a warning to prevent tooth breakage. After maintenance and reset, the trigger switch 144 can spring back.

[0080] After the sliding sleeve 14, teeth and other components are repaired, the controller commands the drive motor 215 to retract the metal pad 216. The metal pad 216 is magnetically attracted back to the telescopic end. The current adjustment module restores the reference current. The electromagnet 13 returns to the initial position under the action of the reset spring. The positioning pin 23 returns to the straight section hole 142 along with the sliding sleeve 14. The pressure and position sensors 25 provide normal signals, and the system returns to the initial transmission and monitoring state.

[0081] The embodiments of this application have been described above with reference to the accompanying drawings. Unless otherwise specified, the embodiments and features in the embodiments of this application can be combined with each other. This application is not limited to the specific embodiments described above. The specific embodiments described above are merely illustrative and not restrictive. Those skilled in the art can make many other forms under the guidance of this application without departing from the spirit and scope of the claims, and all of these forms are within the protection scope of this application.

Claims

1. A planetary shifting mechanism for a valve, comprising a housing (1), characterized in that... A drive rod (11) is provided on one side of the housing (1). A transmission assembly (12) for changing the transmission path and speed ratio is provided inside the housing (1). An electromagnet (13) is provided on one side inside the housing (1). The output end of the electromagnet (13) is rigidly connected to the sliding sleeve (14) through a lever to drive the sliding sleeve (14) to move axially. A valve port (15) is provided at one end of the housing (1) away from the drive rod (11). A valve disc (16) that is linked with the transmission assembly (12) is installed in the valve port (15). A spline is provided inside the housing (1) to constrain the sliding sleeve (14) to move only axially. Elastic positioning component (2), which is disposed inside the housing (1) and adapted to the sliding sleeve (14), is used to detect the change in resistance it receives during the movement of the sliding sleeve (14) in order to provide feedback on the wear status; Adjustable thrust assembly (211), the adjustable thrust assembly (211) is disposed between the housing (1) and the electromagnet (13), and is used to change the preload by adjusting the thrust of the electromagnet (13) after the meshing teeth of the sliding sleeve (14) and the transmission assembly (12) wear, so as to adapt to the wear gap and maintain a stable meshing thrust; The housing (1) has a side groove (10) extending axially along the sliding sleeve (14) on its side wall corresponding to the sliding sleeve (14). The sliding sleeve (14) has a straight section hole (142) coaxially corresponding to the side groove (10) on one side facing the side groove (10). The elastic positioning assembly (2) includes a pressure sensor (21), a first spring (22), and a positioning pin (23). The pressure sensor (21) is fixedly installed at the bottom of the side groove (10) away from the engaging end of the sliding sleeve (14). One end of the first spring (22) abuts against the end face of the pressure sensor (21) facing the sliding sleeve (14). The other end of the first spring (22) abuts against the end face of the pressure sensor (21) facing the sliding sleeve (14). One end is fixedly connected to one end of the positioning pin (23), and the first spring (22) is always in a pre-compressed state. The end of the positioning pin (23) away from the first spring (22) extends into the straight section hole (142). The outer peripheral wall of the positioning pin (23) and the inner wall of the side groove (10) and the inner wall of the straight section hole (142) are axially slidingly fitted. The housing (1) is fixedly installed with a position sensor (25) on one side of the axial movement path of the sliding sleeve (14). The sliding sleeve (14) is provided with an axially extending mounting boss on the side facing the position sensor (25). One end of the mounting boss is fixedly connected to a probe rod (26). The housing (1) has an axial hole for the axial sliding of the electromagnet (13). The housing (1) has a first slot (100) arranged in a ring array on the outside of the electromagnet (13). The first slot (100) communicates with the axial hole. The housing (1) has three second slots (101) on the side of the electromagnet (13) away from the sliding sleeve (14). The second slots (101) are evenly distributed circumferentially along the axial hole. The adjustable thrust assembly (211) includes: A spring limiting rod (212) is fixedly installed in the first slot (100), and its axis is parallel to the sliding direction of the electromagnet (13). The slider (213) is fixed to the outer peripheral wall of the electromagnet (13), and the slider (213) is slidably engaged with the spring limiting rod (212). A reset spring for resetting the electromagnet (13) is sleeved on the spring limiting rod (212). A conical plate (214) is coaxially fixed to the end of the electromagnet (13) away from the sliding sleeve (14), and its outer peripheral wall is in contact with the inner wall of the axial hole; The drive unit (215) is a linear drive element, and there are three of them. Each group of the drive units (215) is fixedly installed in three second slots (101), and its telescopic end faces the conical plate (214). Metal gasket (216), which is magnetically attracted to the telescopic end of the drive (215), and both sidewalls of the metal gasket (216) are set as inclined surfaces.

2. The planetary shifting mechanism for a valve according to claim 1, characterized in that, The transmission assembly (12) includes: The sun gear (121) is coaxially and fixedly connected to the drive rod (11). When the drive rod (11) rotates, it can drive the sun gear (121) to rotate synchronously. Planetary gears (122) and star frame (123), wherein there are at least three planetary gears (122), each planetary gear (122) is rotatably mounted on the circumferential edge of the star frame (123) via a pin, and the axes of all planetary gears (122) are parallel to the axis of the sun gear (121), and the planetary gears (122) simultaneously mesh with the outer peripheral teeth of the sun gear (121) and the inner peripheral teeth of the inner gear ring (124); The inner gear ring (124) has an outer tooth structure on its outer peripheral wall, and the inner side wall of the sliding sleeve (14) has a straight section tooth (141) that is adapted to the outer tooth structure.

3. A planetary shifting mechanism for a valve according to claim 1, characterized in that, The elastic positioning component (2) also includes a ball (24). The end of the positioning pin (23) away from the first spring (22) has a spherical groove. The ball (24) is embedded in the spherical groove, and part of the spherical surface of the ball (24) protrudes from the end face of the positioning pin (23). The ball (24) can rotate freely in the spherical groove, and its spherical surface protruding from the positioning pin (23) contacts the inner wall of the straight section hole (142).

4. A planetary shifting mechanism for a valve according to claim 2, characterized in that, The sliding sleeve (14) has a compensation hole (1420) on one side of the straight section hole (142) that is coaxially connected to the straight section hole (142) and is adapted to the compensation stroke after the sliding sleeve (14) is worn. The groove depth of the compensation hole (1420) is half the groove depth of the straight section hole (142). The sliding sleeve (14) is coaxial with and adjacent to the straight section tooth (141) and has a gradually widening tooth (1410). The tooth tip width of the gradually widening tooth (1410) gradually increases from the end of the straight section tooth (141) outward along the axial direction of the sliding sleeve (14).

5. A planetary shifting mechanism for a valve according to claim 4, characterized in that, The sliding sleeve (14) has a limiting hole (143) coaxially connected to the compensation hole (1420) at one end away from the straight section hole (142). The diameter of the limiting hole (143) is adapted to the outer diameter of the ball (24). An annular mounting groove is provided in the middle of the inner sidewall of the limiting hole (143). A trigger switch (144) capable of rebound is embedded in the annular mounting groove. The trigger end of the trigger switch (144) protrudes from the inner wall of the limiting hole (143).

6. A planetary shifting mechanism for a valve according to claim 1, characterized in that, The electromagnet (13) has a current regulation module installed inside.

7. A planetary shifting mechanism for a valve according to claim 1, characterized in that, The thicknesses of the three metal gaskets (216) are 0.5 mm, 1.0 mm and 2.0 mm, respectively.

8. A planetary shifting mechanism for valves, employing a planetary shifting mechanism for valves as described in any one of claims 1-7, characterized in that: The specific steps are as follows: S1: Valve opening and closing and speed ratio switching: When opening and closing is required, the electromagnet (13) drives the sliding sleeve (14) to engage the internal gear ring (124), and the star frame (123) drives the valve disc (16) at low speed and high torque; when high speed is required, the electromagnet (13) drives the sliding sleeve (14) to disengage from the internal gear ring (124) in the opposite direction, and the transmission returns to high speed and low torque. S2: Wear-free monitoring: In the elastic positioning component (2), the positioning pin (23) and the ball (24) contact the straight section hole (142) of the sliding sleeve (14). The pressure sensor (21) and the position sensor (25) send basic resistance and normal stroke signals respectively, and the controller determines that the engagement is normal. S3: Mild to moderate wear determination: After tooth wear, the sliding sleeve (14) engages beyond the range, which drives the positioning pin (23) to compress the spring. The pressure sensor (21) and the position sensor (25) send resistance increase and overtravel signals. The controller determines the wear and triggers compensation. S4: Confirmation of medium compensation zone: The sliding sleeve (14) enters the compensation stroke, the positioning pin (23) enters the compensation hole (1420), and the constraint force increases sharply due to the halving of the groove depth. The pressure sensor (21) sends a high resistance sudden change signal. Combined with the position signal, the compensation zone is confirmed. S5: Thrust adjustment compensation: The controller commands the drive motor (215) to push out the corresponding metal pad (216) according to the wear degree, and the current of the electromagnet (13) is increased to increase the thrust to adapt to wear. S6: Over-wear protection: Over-compensation stroke of the sliding sleeve (14), ball (24) enters the limit hole (143) trigger switch (144), combined with the limit signal of the pressure sensor (21) and the position sensor (25), the controller commands a shutdown warning; S7: Reset after repair: After the component is repaired, the controller commands to retract the metal pad (216), restore the current, reset the electromagnet (13), return the positioning pin (23) to the straight section hole (142), and restore the system to its initial state.

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