High-speed pulse valve based on rotating fan hole coincidence principle

Abstract

The utility model discloses a high -speed pulse valve based on rotation fan hole coincident principle, including valve body, interface pipeline, valve seat, drive assembly and valve disc subassembly, and valve disc subassembly includes the fixed valve disc and rotary valve disc of end face attachment, and the flow distribution hole on two valve discs is periodic coincident or staggered with the rotation of rotary valve disc to form the pulse air current. The damping assembly is established between drive shaft and rotary valve disc, and drive shaft transmission connection drive disc, and the bearing disc is fixed on rotary valve disc, and drive disc and bearing disc are axially spaced and can rotate relative rotation, and the spring along the circumferential tangential arrangement is established between both. Drive disc rotates bearing disc and rotary valve disc through compression spring to buffer start -stop torque, and when stopping, the end face friction between rotary valve disc and fixed valve disc forms the damping to spring resilience. Fixed pin and limit groove cooperate and limit the maximum relative angle.

Description

Technical Field

[0001] This utility model relates to the field of pulse valve technology, specifically to a high-speed pulse valve based on the principle of overlapping rotating fan holes. Background Technology

[0002] Rotary pulse valves typically have a fixed valve disc and a rotating valve disc with their end faces touching inside the valve body. The rotating valve disc is driven to rotate by a drive component, causing the flow holes on the two valve discs to periodically overlap or stagger, thereby controlling the periodic opening of the gas passage and forming a pulsed airflow.

[0003] In existing rotary pulse valves, the drive shaft is typically rigidly coupled to the rotary valve disc. When the equipment starts, the drive assembly must simultaneously overcome the rotational inertia of the rotary valve disc and the end-face friction between the rotary and stationary valve discs; the drive torque is then quickly transmitted to the rotary valve disc. When the equipment stops, the rotational inertia of the rotary valve disc also directly acts on the drive shaft and its connecting parts.

[0004] Under high-speed start-stop conditions, the aforementioned rigid transmission method can easily generate significant torsional impact between the drive shaft and the rotary valve disc, potentially causing valve disc vibration, loosening of the transmission connection, and wear on the mating surfaces. Therefore, it is necessary to improve the force transmission structure between the drive shaft and the rotary valve disc. Utility Model Content

[0005] The purpose of this invention is to provide a high-speed pulse valve based on the principle of overlapping rotating fan holes, so as to improve the torsional impact generated when the drive shaft rigidly drives the rotating valve disc to start and stop.

[0006] To achieve the above objectives, the present invention adopts the following technical solution: A high-speed pulse valve based on the principle of overlapping rotating fan holes includes a valve body, an interface pipe and a drive assembly on the valve body, a valve seat inside the valve body, and the drive assembly includes a drive shaft extending into the valve body.

[0007] The valve seat is provided with a valve disc assembly, which includes a fixed valve disc fixed on the valve seat and a rotating valve disc located above the fixed valve disc and in contact with its end face. The fixed valve disc and the rotating valve disc are respectively provided with flow distribution holes that periodically overlap as the rotating valve disc rotates.

[0008] A shock-absorbing assembly is provided between the drive shaft and the rotary valve disc. The lower end of the drive shaft is connected to the drive disc. A bearing disc located below the drive disc is fixed on the rotary valve disc. The drive disc and the bearing disc are axially spaced apart and can rotate relative to each other in the circumference. A spring is provided between the drive disc and the bearing disc, arranged tangentially along the circumference, so that the spring is compressed when the drive disc rotates relative to the bearing disc, and the bearing disc and the rotary valve disc are rotated by the spring.

[0009] The support plate has several support grooves arranged at intervals along its circumference, each extending tangentially along the circumference of the support plate, and springs are respectively disposed in the corresponding support grooves. The drive plate has a pushing part corresponding to the end of the spring, so as to push and compress the spring when the drive plate rotates relative to the support plate.

[0010] The drive disc has several circumferentially extending limiting grooves, and the rotary valve disc has several fixing pins located on the outer periphery of the support disc. Each fixing pin extends into a corresponding limiting groove and can move relative to the limiting groove. The fixing pins limit the maximum relative angle between the drive disc and the support disc by abutting against the circumferential ends of the limiting grooves.

[0011] The lower end of the drive shaft is provided with a spline, and the center of the drive disc is provided with a spline hole that mates with the spline. The drive disc is circumferentially connected to the drive shaft via the spline. The drive shaft is provided with an axial limiting part located below the drive disc to restrict the drive disc from moving downward along the drive shaft.

[0012] The spring has guide seats at both ends, which slide in conjunction with the bearing groove. The guide seats have guide parts that extend into the spring, and the pushing part of the drive disc transmits circumferential force to the spring through the guide seats.

[0013] A sealing ring is provided on the outer periphery of the rotary valve disc to seal the outer periphery of the rotary valve disc.

[0014] Compared with the prior art, this utility model sets up a drive disc, a support disc, and a spring between the drive shaft and the rotary valve disc, so that the torque output by the drive shaft is transmitted to the rotary valve disc through the spring. The drive disc and the support disc can generate circumferential relative rotation during start-up and stop. The spring buffers the torque change through compression deformation, thereby reducing the torsional impact on the rotary valve disc and transmission connection parts when the drive assembly starts and stops.

[0015] The axial spacing between the drive disc and the carrier disc prevents end-face friction during relative rotation. The fixed pin engages with the limiting groove to limit the maximum relative angle between them. The spline engages with the axial limiting part to axially position the drive disc while transmitting circumferential torque. The guide seat guides the compression motion of the spring. The end-face friction between the rotary valve disc and the fixed valve disc also dampens the rebound energy released by the spring, thereby reducing reciprocating torsion and valve disc jitter after start-up and shutdown. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the overall structure of a high-speed pulse valve based on the principle of overlapping rotating fan holes. Figure 2 This is a half-sectional schematic diagram of a high-speed pulse valve based on the principle of overlapping rotating fan holes. Figure 3This is a schematic diagram of the valve disc assembly structure of a high-speed pulse valve based on the principle of rotating fan-hole overlap. Figure 4 This is a schematic diagram of the exploded structure of the shock absorption component of a high-speed pulse valve based on the principle of overlapping rotating fan holes. Figure 5 This is a schematic diagram of the exploded structure of the spring in a high-speed pulse valve based on the principle of overlapping rotating fan holes.

[0017] Attached icon number 1. Valve body; 11. Interface pipe; 12. Valve seat; 2. Drive assembly; 21. Drive shaft; 211. Spline; 3. Valve disc assembly; 31. Rotary valve disc; 32. Fixed valve disc; 33. Flow distribution hole; 4. Sealing ring; 5. Vibration damping assembly; 51. Drive disc; 511. Limit groove; 52. Bearing disc; 521. Bearing groove; 53. Spring; 531. Guide seat; 54. Fixing pin. Detailed Implementation

[0018] The technical solutions of this application will now be clearly and completely described with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. The components of this application described and shown in the accompanying drawings can generally be arranged and designed in various different configurations. Therefore, the following detailed description of the embodiments of this application provided in the accompanying drawings is not intended to limit the scope of the claimed application, but merely to illustrate selected embodiments of this application.

[0019] like Figures 1 to 5 As shown, this embodiment provides a high-speed pulse valve based on the principle of overlapping rotating fan holes, including a valve body 1. The valve body 1 is used to form a gas flow space and install various internal structures. An interface pipe 11 is provided on the valve body 1, and the interface pipe 11 communicates with the interior of the valve body 1. In actual use, one interface pipe 11 is connected to the gas supply line, and the other interface pipe 11 is connected to the pulse gas flow output line, allowing the gas to be periodically output through the flow distribution structure inside the valve body 1.

[0020] A drive assembly 2 is located above the valve body 1, and the drive assembly 2 includes a drive shaft 21. The drive shaft 21 extends downward along the axial direction of the valve body 1 into the valve body 1 to provide rotational driving force. The drive assembly 2 can be formed by combining a motor and a reduction mechanism, or it can be other drive structures capable of outputting continuous rotational motion. When the drive assembly 2 is running, the drive shaft 21 rotates around its own axis and transmits torque to the rotating structure located inside the valve body 1.

[0021] A valve seat 12 is provided inside the valve body 1. The valve seat 12 is located below the drive assembly 2 and is fixed to the valve body 1. A valve disc assembly 3 is provided on the valve seat 12. The valve disc assembly 3 includes a fixed valve disc 32 and a rotating valve disc 31. The fixed valve disc 32 is fixedly installed on the valve seat 12, and the rotating valve disc 31 is located above the fixed valve disc 32 and is coaxially arranged with the fixed valve disc 32. The lower end face of the rotating valve disc 31 is in contact with the upper end face of the fixed valve disc 32, so that an end face flow distribution relationship is formed between the two.

[0022] A sealing ring 4 is provided on the outer periphery of the rotary valve disc 31. The sealing ring 4 surrounds the rotary valve disc 31 and is used to seal the outer periphery of the rotary valve disc 31.

[0023] Both the fixed valve disc 32 and the rotary valve disc 31 are provided with flow distribution holes 33. The flow distribution holes 33 can be fan-shaped through holes directly opened on the valve disc, or they can be formed by arranging multiple through holes according to a predetermined fan-shaped area. The flow distribution holes 33 on the fixed valve disc 32 and the flow distribution holes 33 on the rotary valve disc 31 correspond to each other in radial position and have a predetermined misalignment relationship in circumferential direction.

[0024] When the rotary valve disc 31 rotates relative to the fixed valve disc 32, the flow distribution holes 33 on both discs periodically overlap and offset as their relative angular positions change. When the flow distribution hole 33 on the rotary valve disc 31 rotates to a position corresponding to the flow distribution hole 33 on the fixed valve disc 32, a through gas channel is formed between them, allowing gas to flow through the valve disc assembly 3. At this time, the valve disc assembly 3 is in the open state. As the rotary valve disc 31 continues to rotate, the flow distribution holes 33 on the two valve discs gradually offset, and the effective overlapping area between the flow distribution holes 33 decreases until the flow distribution hole 33 on the fixed valve disc 32 is blocked by the solid part of the rotary valve disc 31, cutting off the gas channel. At this time, the valve disc assembly 3 is in the closed state.

[0025] In this embodiment, the pulse refers to the gas passage repeatedly opening and closing at a certain frequency during the continuous rotation of the rotary valve disc 31, causing the airflow through the valve body 1 to change periodically. Each time, the distribution orifice 33 gradually moves from a staggered state to an overlapping state, and the effective flow area of ​​the gas passage gradually increases; after the distribution orifice 33 reaches the predetermined overlapping position, the gas flow rate reaches the corresponding value; as the rotary valve disc 31 continues to rotate, the overlapping area of ​​the two decreases again until the gas passage is closed. The above process is repeated continuously, thereby forming a pulsed airflow with sequential intervals.

[0026] The formation of pulsed airflow does not require the drive assembly 2 to repeatedly start and stop between each pulse. During normal operation, the drive assembly 2 continuously drives the rotary valve disc 31 to rotate, and the valve disc assembly 3 repeatedly enters and exits the open and closed states as the distribution orifices 33 periodically overlap and stagger. The rotational speed of the rotary valve disc 31, as well as the number and distribution pattern of the distribution orifices 33 in the circumferential direction, jointly affect the number of times the gas passage opens and closes per unit time. When the rotational speed of the rotary valve disc 31 increases, the time for the distribution orifices 33 to complete one overlap and stagger is shortened, and the pulse frequency increases accordingly.

[0027] The rotary valve disc 31 and the fixed valve disc 32 maintain end-face contact in both the open and closed states of the valve disc assembly 3. In the open state, the overlapping flow holes 33 allow gas to pass through, and the solid areas of the valve discs around the flow holes 33 remain in contact. When the rotary valve disc 31 rotates, its lower end face slides relative to the upper end face of the fixed valve disc 32. In the closed state, the solid area of ​​the rotary valve disc 31 blocks the flow holes 33 on the fixed valve disc 32, and the two valve discs still maintain the predetermined end-face contact relationship. As the rotary valve disc 31 continues to rotate, sliding friction also exists between them. Therefore, during the continuous generation of pulsed airflow in the valve disc assembly 3, end-face friction occurs throughout the entire process of the flow holes 33 shifting from overlap to misalignment and then back to overlap.

[0028] When the rotary valve disc 31 stops rotating, the contact surfaces of the two valve discs no longer slide relative to each other, and the end-face friction changes from sliding friction to static friction. When the drive assembly 2 restarts, it needs to overcome the rotational inertia of the rotary valve disc 31 and its connecting structure, as well as the static friction between the rotary valve disc 31 and the fixed valve disc 32, in order for the rotary valve disc 31 to enter the rotating state from the stationary state.

[0029] A shock-absorbing assembly 5 is provided between the drive shaft 21 and the rotary valve disc 31, and the shock-absorbing assembly 5 is located above the rotary valve disc 31. The lower end of the drive shaft 21 is connected to the drive disc 51, and the drive disc 51 is coaxially arranged with the drive shaft 21 and rotates with the drive shaft 21. A support disc 52 is fixed on the rotary valve disc 31, and the support disc 52 is located below the drive disc 51 and rotates synchronously with the rotary valve disc 31.

[0030] The drive disk 51 and the support disk 52 are spaced apart along the axial direction of the drive shaft 21, with an axial gap between the lower end face of the drive disk 51 and the upper end face of the support disk 52. This axial gap ensures that the relative disk surfaces of the drive disk 51 and the support disk 52 remain separated when the drive disk 51 rotates circumferentially relative to the support disk 52, preventing end-face friction between them. The circumferential force between the drive disk 51 and the support disk 52 is transmitted through the spring 53, rather than relying on friction generated by the contact of their disk surfaces.

[0031] The support plate 52 is fixed to the upper end face of the rotary valve plate 31. When the support plate 52 is subjected to a circumferential force, it can directly drive the rotary valve plate 31 to rotate. The support plate 52 can be fixed to the rotary valve plate 31 by means of threaded fastening, positioning connection or integral molding. In this embodiment, the support plate 52 and the rotary valve plate 31 are fixedly connected so that the two do not rotate relative to each other in the circumferential direction during operation.

[0032] The support plate 52 is provided with a plurality of support grooves 521, which are arranged circumferentially around the drive shaft 21. Each support groove 521 extends tangentially along its circumferential position and is positioned towards one side of the drive plate 51. Springs 53 are respectively installed in the corresponding support grooves 521, and the axial direction of the springs 53 is consistent with the extension direction of the support grooves 521, so that the springs 53 can extend and contract tangentially along the circumference of the support plate 52.

[0033] The bearing groove 521 supports and limits the spring 53 from below and the side, causing the spring 53 to compress in a predetermined direction when subjected to circumferential force, reducing radial displacement or lateral bending. The circumferential length of the bearing groove 521 is set according to the initial length, pre-compression amount, and allowable compression stroke of the spring 53 to meet the spring deformation requirements when a predetermined relative angle is generated between the drive disk 51 and the bearing disk 52.

[0034] The drive disk 51 is provided with a pushing part corresponding to the end of each spring 53. When the drive disk 51 rotates relative to the support disk 52, the pushing part moves circumferentially with the drive disk 51 and acts on the corresponding end of the spring 53, causing the spring 53 to be gradually compressed along the support groove 521. After the spring 53 is compressed, its other end applies a circumferential force to the support disk 52 through the corresponding limiting position of the support groove 521, thereby driving the support disk 52 to rotate.

[0035] like Figure 5 As shown, guide seats 531 are provided at both ends of the spring 53. The guide seat 531 includes a pressure-bearing portion that abuts against the end of the spring 53 and a guide portion that extends into the interior of the spring 53. The guide portion extends along the axial direction of the spring 53 and radially positions the end of the spring 53; the pressure-bearing portion is used to withstand the force applied by the pushing portion of the drive disc 51 or the corresponding position of the bearing groove 521.

[0036] When the spring 53 is compressed, the guide seats 531 at both ends can move along the extension direction of the bearing groove 521, so that the circumferential force applied by the drive disk 51 is transmitted along the axial direction of the spring 53. The guide seats 531 can reduce the off-center load generated when the end of the spring 53 directly contacts the drive disk 51 or the bearing groove 521, making the compression process of the spring 53 more stable.

[0037] The lower end of the drive shaft 21 is provided with a spline 211, and the center of the drive disk 51 is provided with a spline hole that mates with the spline 211. The drive disk 51 is sleeved on the lower end of the drive shaft 21, and the spline 211 and the spline hole mate with each other, enabling the drive shaft 21 to transmit circumferential torque to the drive disk 51. The drive disk 51 rotates with the drive shaft 21 via the spline 211, but the spline fit does not serve as an axial support structure for the drive disk 51.

[0038] An axial limiting part is provided on the drive shaft 21 below the drive disk 51. The axial limiting part supports the lower side of the drive disk 51 and restricts the drive disk 51 from moving downward along the drive shaft 21. The upper side of the drive disk 51 is limited by a shoulder on the drive shaft 21 or an adjacent positioning structure, so that the drive disk 51 is held in a predetermined axial position. Through the above axial positioning, the drive disk 51 will not slide downward along the spline 211, and the axial clearance between the drive disk 51 and the bearing disk 52 can remain stable during operation.

[0039] Spline 211 provides circumferential transmission between drive shaft 21 and drive disk 51, while the axial limiting part provides axial positioning of drive disk 51. When drive disk 51 rotates synchronously with drive shaft 21, drive disk 51 will not move downwards to contact bearing disk 52 due to its own weight, vibration, or the action of spring 53.

[0040] The drive disc 51 is also provided with several limiting grooves 511, which extend circumferentially along the drive disc 51. Several fixing pins 54 are fixed on the rotary valve disc 31, which are located on the outer periphery of the support disc 52 and extend upward. Each fixing pin 54 extends into the corresponding limiting groove 511. The fixing pin 54 rotates synchronously with the rotary valve disc 31 and the support disc 52, and the limiting groove 511 rotates with the drive disc 51.

[0041] The limiting groove 511 has a predetermined circumferential length, allowing the fixing pin 54 to move relative to each other circumferentially within the limiting groove 511. When the fixing pin 54 is not in contact with the circumferential end of the limiting groove 511, the drive disk 51 and the bearing disk 52 can rotate relative to each other within the angular range allowed by the limiting groove 511, and the spring 53 can buffer the torque change between them through compression deformation.

[0042] When the relative rotation angle between the drive disc 51 and the carrier disc 52 reaches a predetermined value, the fixing pin 54 abuts against the corresponding circumferential end of the limiting groove 511, thereby restricting the relative rotation between the drive disc 51 and the carrier disc 52. The cooperation between the fixing pin 54 and the limiting groove 511 is used to control the maximum compression stroke of the spring 53, reducing the possibility of the spring 53 undergoing permanent deformation or detaching from the carrier groove 521 due to excessive compression.

[0043] During installation, first fix the fixed valve disc 32 on the valve seat 12, then coaxially set the rotating valve disc 31 above the fixed valve disc 32, so that the lower end face of the rotating valve disc 31 fits against the upper end face of the fixed valve disc 32, and install the sealing ring 4 on the outer periphery of the rotating valve disc 31.

[0044] The support plate 52 is fixedly mounted on the rotary valve plate 31, and the fixing pins 54 are respectively fixed to the rotary valve plate 31 and distributed on the outer periphery of the support plate 52. Then, the springs 53 with guide seats 531 are installed in each support groove 521 of the support plate 52, so that the springs 53 are arranged tangentially along the circumference of the corresponding position.

[0045] The drive disc 51 is mounted above the support disc 52, with each fixing pin 54 extending into its corresponding limiting groove 511. Simultaneously, the pushing portion of the drive disc 51 aligns with the guide seat 531 at the end of the spring 53. After the spline 211 at the lower end of the drive shaft 21 engages with the spline hole at the center of the drive disc 51, the axial limiting portion at the lower end of the drive shaft 21 supports the drive disc 51, holding it in a predetermined position above the support disc 52. After assembly, an axial clearance remains between the drive disc 51 and the support disc 52, allowing the fixing pins 54 to move circumferentially within a predetermined range within the limiting groove 511.

[0046] When the equipment is stopped and not subjected to external driving force, the drive shaft 21, drive disc 51, bearing disc 52, and rotary valve disc 31 are all stationary. The rotary valve disc 31 and the fixed valve disc 32 maintain end face contact, forming static friction between them. At this time, the rotary valve disc 31 can stop at a position where the flow holes 33 coincide or at a position where the flow holes 33 are offset, and its stopping position can be determined according to the control method of the drive assembly 2.

[0047] When the drive assembly 2 is started, the drive shaft 21 first drives the drive disk 51 to rotate. Since the bearing disk 52 is fixed to the rotary valve disk 31, and the rotary valve disk 31 has rotational inertia and is hindered by the static friction of the end face of the fixed valve disk 32, in the initial stage when the drive disk 51 starts to rotate, the bearing disk 52 and the rotary valve disk 31 lag behind the drive disk 51 in rotation.

[0048] The pushing part of the drive disc 51 moves with the drive disc 51 and compresses the corresponding spring 53 through the guide seat 531. The compression of the spring 53 gradually increases, and its circumferential elastic force acting on the bearing disc 52 also increases accordingly. When the circumferential force generated by the spring 53 can overcome the rotational inertia of the rotary valve disc 31 and the static friction between the mating end faces of the two valve discs, the bearing disc 52 begins to drive the rotary valve disc 31 to rotate.

[0049] After the rotary valve disc 31 starts to rotate, the friction between it and the fixed valve disc 32 changes from static friction to sliding friction. The partial relative rotation angle formed by the drive disc 51 in the initial stage of startup is absorbed by the compression deformation of the spring 53. The output torque of the drive shaft 21 is gradually transmitted to the bearing disc 52 as the compression of the spring 53 increases, causing the rotary valve disc 31 to gradually accelerate from a stationary state.

[0050] With the above transmission method, when the drive shaft 21 starts to rotate, the rotary valve disc 31 does not need to completely follow the drive shaft 21 to reach the corresponding speed at the same moment. The spring 53 provides a certain elastic stroke between the drive disc 51 and the bearing disc 52, so that the process of overcoming static friction and rotational inertia is distributed within a certain relative rotational stroke, reducing the degree to which the starting torque suddenly acts on the rotary valve disc 31, spline 211 and the contact end face of the two valve discs.

[0051] After the rotary valve disc 31 reaches its operating speed, the drive disc 51, the support disc 52, and the rotary valve disc 31 rotate at essentially the same average angular velocity. Under the working load, the spring 53 maintains a corresponding amount of compression, and a relatively stable angular difference is maintained between the drive disc 51 and the support disc 52. During normal operation, the fixing pin 54 is located between the two circumferential ends of the limiting groove 511, and the spring 53 bears the main circumferential force transmission between the drive disc 51 and the support disc 52.

[0052] During the continuous rotation of the rotary valve disc 31, the flow distribution holes 33 on the fixed valve disc 32 and the rotary valve disc 31 periodically overlap and offset. When the flow distribution holes 33 overlap, the gas passage is open, and gas flows through the valve disc assembly 3 via the interconnected flow distribution holes 33; when the flow distribution holes 33 offset, the gas passage is closed. The average rotational speed of the drive disc 51 and the support disc 52 is the same, enabling the rotary valve disc 31 to continuously complete the above flow distribution process according to the rotational speed set by the drive assembly 2.

[0053] When the valve disc assembly 3 is in the open state, the solid area of ​​the valve disc around the flow distribution hole 33 maintains end-face contact, and sliding friction is generated when the rotating valve disc 31 rotates. When the valve disc assembly 3 is in the closed state, the solid area of ​​the rotating valve disc 31 blocks the flow distribution hole 33 on the fixed valve disc 32, and the end faces of the two valve discs still slide relative to each other. Therefore, the difference between the open and closed states lies in whether the flow distribution hole 33 forms a gas passage, and does not change the basic relationship of the rotating valve disc 31 and the fixed valve disc 32 maintaining end-face contact.

[0054] When drive assembly 2 stops, drive shaft 21 and drive disc 51 connected to it decelerate first. Due to their rotational inertia, the bearing disc 52 and rotary valve disc 31 still tend to continue moving in the original direction of rotation after drive disc 51 begins to decelerate, causing a change in the relative angular position between bearing disc 52 and drive disc 51.

[0055] During this process, the springs 53 at corresponding positions between the bearing disk 52 and the drive disk 51 are compressed, and a portion of the rotational inertial energy of the rotary valve disk 31 is converted into the elastic potential energy of the springs 53. The compression of the springs 53 prevents the inertial force of the rotary valve disk 31 from being fully transmitted to the drive shaft 21 and spline 211 at the moment the drive disk 51 decelerates; instead, it is buffered by the deformation of the springs.

[0056] As the rotary valve disc 31 continues to rotate, its lower end face slides relative to the upper end face of the fixed valve disc 32. The sliding friction between the two valve discs is always opposite to the direction of motion of the rotary valve disc 31. This sliding friction consumes the rotational energy of the rotary valve disc 31 during deceleration and, together with the compression of the spring 53, reduces the rotational speed of the rotary valve disc 31.

[0057] As the rotational speed of the drive shaft 21 and the rotary valve disc 31 decreases, the spring 53 tends to return to its initial length and exerts a rebound effect on the bearing disc 52. Since the bearing disc 52 is fixed on the rotary valve disc 31, when the spring 53 releases its elastic potential energy, it needs to drive the rotary valve disc 31 to overcome the end-face friction between it and the fixed valve disc 32.

[0058] When the rebound of spring 53 is insufficient to overcome the static friction between the two valve discs, the rotating valve disc 31 remains in the stopped position, and the remaining spring force of spring 53 is borne by the static friction on the valve disc end face and the force balance inside the damping assembly 5. When the rebound of spring 53 exceeds the corresponding static friction resistance, the rotating valve disc 31 may rotate slightly, and sliding friction will then form between the two valve discs. Part of the energy released by spring 53 is converted into heat and consumed during the relative sliding process of the end faces.

[0059] If the bearing plate 52 crosses the relative equilibrium position under the action of the spring 53, the spring 53 may also have a reverse recovery tendency. The end face friction between the rotary valve plate 31 and the fixed valve plate 32 always hinders the relative movement between the two, so it can continuously consume energy in the possible reciprocating motion, so that the relative vibration between the bearing plate 52 and the drive plate 51 gradually weakens until the rotary valve plate 31 stops stably.

[0060] During shutdown, spring 53 primarily serves to temporarily store inertial energy and buffer torque. The end-face friction between the rotating valve disc 31 and the fixed valve disc 32 dampens the energy released by spring 53. The end-face friction originates from the original contact and flow distribution relationship of the valve disc assembly 3, eliminating the need for the drive disc 51 and the bearing disc 52 to come into contact, and also eliminating the need for the drive disc 51 to apply additional axial clamping force to the rotating valve disc 31.

[0061] When the rotary valve disc 31 experiences a brief jam during operation, the drive shaft 21 can still drive the drive disc 51 to rotate relative to the support disc 52. The drive disc 51 first compresses the spring 53, so that the instantaneous torque output by the drive assembly 2 is buffered by the deformation of the spring 53. As the relative angle between the drive disc 51 and the support disc 52 increases, the fixing pin 54 gradually approaches the circumferential end of the limiting groove 511.

[0062] When the relative rotation angle reaches the maximum range allowed by the limiting groove 511, the fixing pin 54 abuts against the circumferential end of the limiting groove 511, restricting the drive disc 51 from continuing to rotate relative to the carrier disc 52. At this time, the fixing pin 54 and the limiting groove 511 provide mechanical limiting, preventing the spring 53 from continuing to compress beyond its allowable stroke. After the jamming is released, the spring 53 pushes the carrier disc 52 to resume movement, and the end face friction between the rotary valve disc 31 and the fixed valve disc 32 continues to resist the spring's rebound, causing the rotary valve disc 31 to gradually resume stable rotation.

[0063] In this embodiment, a drive disk 51 and a support disk 52 capable of limited circumferential relative rotation are arranged between the drive shaft 21 and the rotary valve disk 31, and torque is transmitted by a spring 53 disposed between them. During startup, the drive disk 51 first compresses the spring 53, and then the gradually increasing spring force drives the support disk 52 and the rotary valve disk 31 to rotate. During normal operation, the spring 53 maintains a corresponding compressed state under the working torque. During shutdown, the spring 53 absorbs part of the inertial energy of the rotary valve disk 31, and the end-face friction between the rotary valve disk 31 and the fixed valve disk 32 dampens the spring's rebound. In case of abnormal jamming, the fixed pin 54 cooperates with the limiting groove 511 to limit the maximum relative rotation angle. This structure buffers the startup, shutdown, and abnormal obstruction processes of the rotary valve disk 31 while maintaining the working mode of periodically coinciding flow of the distribution holes 33 to form pulsed airflow.

[0064] The above description is merely a preferred embodiment of this application and is not intended to limit this application. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A high-speed pulse valve based on the principle of overlapping rotating fan holes, comprising a valve body (1), wherein the valve body (1) is provided with an interface pipe (11) and a drive assembly (2), wherein the valve body (1) is provided with a valve seat (12), and the drive assembly (2) includes a drive shaft (21) extending into the valve body (1), characterized in that: The valve seat (12) is provided with a valve disc assembly (3), the valve disc assembly (3) includes a fixed valve disc (32) fixed on the valve seat (12) and a rotating valve disc (31) located above the fixed valve disc (32) and in contact with its end face. The fixed valve disc (32) and the rotating valve disc (31) are respectively provided with flow distribution holes (33) that periodically overlap as the rotating valve disc (31) rotates. A shock-absorbing assembly (5) is provided between the drive shaft (21) and the rotary valve disc (31). The lower end of the drive shaft (21) is connected to a drive disc (51). A bearing disc (52) located below the drive disc (51) is fixed on the rotary valve disc (31). The drive disc (51) and the bearing disc (52) are axially spaced apart and can rotate relative to each other in the circumferential direction. A spring (53) is provided between the drive disc (51) and the bearing disc (52) arranged tangentially in the circumference, so that the drive disc (51) compresses the spring (53) when it rotates relative to the bearing disc (52), and the bearing disc (52) and the rotary valve disc (31) are driven to rotate by the spring (53).

2. The high-speed pulse valve based on the principle of overlapping rotating fan holes according to claim 1, characterized in that: The support plate (52) is provided with a plurality of support grooves (521) arranged at intervals along its circumference. Each support groove (521) extends tangentially along the circumference of the support plate (52), and the springs (53) are respectively disposed in the corresponding support grooves (521). The drive disk (51) is provided with a pushing portion corresponding to the end of the spring (53) to push and compress the spring (53) when the drive disk (51) rotates relative to the support disk (52).

3. The high-speed pulse valve based on the principle of overlapping rotating fan holes according to claim 2, characterized in that: The drive disk (51) is provided with a plurality of circumferentially extending limiting grooves (511), and the rotary valve disk (31) is fixed with a plurality of fixing pins (54) located on the outer periphery of the bearing disk (52). Each fixing pin (54) extends into the corresponding limiting groove (511) and can move relative to the limiting groove (511). The fixing pin (54) limits the maximum relative angle between the drive disk (51) and the carrier disk (52) by abutting against the circumferential end of the limiting groove (511).

4. The high-speed pulse valve based on the principle of rotating fan-shaped orifice overlap according to claim 3, characterized in that: The lower end of the drive shaft (21) is provided with a spline (211), and the center of the drive disk (51) is provided with a spline hole that mates with the spline (211). The drive disk (51) is circumferentially connected to the drive shaft (21) through the spline (211). The drive shaft (21) is provided with an axial limiting part located below the drive disk (51), and the axial limiting part is used to restrict the drive disk (51) from moving downward along the drive shaft (21).

5. The high-speed pulse valve based on the principle of rotating fan-shaped orifice overlap according to claim 4, characterized in that: The spring (53) is provided with guide seats (531) at both ends. The guide seats (531) are slidably engaged with the bearing groove (521). The guide seats (531) are provided with guide portions that extend into the spring (53). The pushing part of the drive disc (51) transmits circumferential force to the spring (53) through the guide seat (531).

6. The high-speed pulse valve based on the principle of rotary fan-hole overlap according to claim 5, characterized in that: The outer periphery of the rotary valve disc (31) is provided with a sealing ring (4) surrounding the rotary valve disc (31).

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