High-temperature and high-pressure ultrafast pulse control valve

Abstract

The invention discloses a high-temperature and high-pressure ultrafast pulse control valve which comprises a valve body, a valve seat, a valve clack with an air inflation hole and a rotary driving mechanism, and the air inflation hole and a valve seat vent hole are periodically overlapped through rotation of the valve clack to form high-frequency pulse airflow; according to the innovation, a distance fine adjustment mechanism is arranged; a fixing frame is connected with a valve body; a first flow channel pipe is fixed on the fixing frame; the valve seat sleeves the first flow channel pipe and is meshed with the first flow channel pipe through a thread pair, and the valve seat is rotated to drive the valve seat to axially move along the first flow channel pipe; scale marks on the periphery of the valve seat quantify the corresponding relation between the rotation angle and the axial displacement, and precise adjustment of a micro gap smaller than or equal to 0.04 mm between sealing faces is achieved. The gap control bottleneck of a traditional pulse valve under the high-temperature working condition is broken through, the phenomena that noise and sparks are generated due to high-speed rotation of the valve clack are avoided, the leakage rate smaller than or equal to 0.5% at the pulse frequency of 60 Hz is accurately maintained, and the sealing reliability of a fluid scouring test is guaranteed.

Description

Technical Field

[0001] The present invention relates to the field of fluid control technology, and in particular to a high-temperature and high-pressure ultrafast pulse control valve. Background Art

[0002] Core components (such as metal / composite diaphragms) in high-end equipment such as aerospace engine fuel valves, nuclear reactor cooling systems, and deep-sea energy extraction systems face the critical challenge of withstanding extreme transient operating conditions: millisecond-scale pulses of high temperature, high pressure, and highly corrosive fluids. Traditional steady-state material testing methods are unable to effectively simulate the material failure mechanisms caused by these high-energy transient impacts. Therefore, the development of specialized testing equipment that can accurately replicate these extreme millisecond-scale pulse environments is urgently needed.

[0003] A typical pulse generator in the prior art utilizes a rotating valve disc design. Its core principle lies in the fact that both the disc and the fixed seat have through-holes. By driving the disc to rotate at high speed, when the through-holes periodically and completely overlap with those in the seat, the high-pressure airflow path is instantly opened; when the two become dislocated, the path is cut off. By precisely controlling the disc's rotational speed (for example, achieving 60 on-off cycles per second, or a 60Hz pulse frequency), a high-frequency scouring environment can be simulated for the test diaphragm.

[0004] However, this technical solution presents significant bottlenecks. Given the high temperatures encountered in the test environment, the sealing element between the valve disc and the valve seat must be constructed of a hard metal material (such as a special alloy). Conventional soft sealing materials such as rubber or fluoroplastics are unsuitable due to thermal decomposition or softening failure. The disc rotates at high speeds, while the seat is stationary. Direct contact between the two end faces would generate intense friction noise and potential sparks, posing a serious safety hazard. Therefore, a tiny non-contact gap must be maintained between the seals. The size of this gap directly determines the system's leakage rate. To meet test accuracy and safety requirements (typically, leakage must be controlled to ≤0.5%), theoretical calculations and engineering practice have shown that this gap must be strictly limited to an extremely small range (for example, less than 0.04 mm, far below the diameter of a human hair, which is 0.06 mm). Achieving and stably maintaining this submicron non-contact gap while ensuring the disc's free high-speed rotation is a key technical challenge in designing highly reliable, low-leakage pulse valves. Consequently, the development of high-temperature, high-pressure, ultra-fast pulse control valves with precise sealing surface fine-tuning mechanisms is urgently needed. Summary of the Invention

[0005] The purpose of the present invention is to overcome the shortcomings and deficiencies of the prior art and to provide a high-temperature and high-pressure ultrafast pulse control valve.

[0006] To achieve the above-mentioned objectives, the present invention provides the following technical solutions: a high-temperature and high-pressure ultrafast pulse control valve, comprising: a valve body, which is provided with a medium channel; a valve seat, installed in the valve body, and a vent hole connected to the medium channel; a valve disc, whose end face is provided with a plurality of air holes distributed along the circumference, and the valve disc is rotatably supported in the valve body; a rotary drive mechanism, connected to the valve disc, for driving the valve disc to rotate periodically so that the air holes and the air holes periodically coincide to achieve intermittent conduction of the medium channel, and also comprising: a spacing fine-tuning mechanism, for precisely adjusting the axial gap between the valve seat sealing surface and the valve disc sealing surface; the spacing fine-tuning mechanism comprises: a fixing frame, fixedly connected to the valve body; a first flow channel tube, one end of which is fixedly connected to the fixing frame; the valve seat is sleeved on the other end of the first flow channel tube, and is connected to the first flow channel tube by a threaded pair; the outer circumferential surface of the valve seat is evenly distributed with scale lines, for indicating the corresponding relationship between the rotation angle and the axial displacement.

[0007] As a preferred technical solution of the present invention, the inner wall of the valve seat is provided with an internal thread; the outer wall of the first flow channel is provided with an external thread; by rotating the valve seat, the external thread and the internal thread engage to drive the valve seat to move axially along the first flow channel.

[0008] As a preferred technical solution of the present invention, a first O-ring is provided between the outer wall of the first flow channel tube and the inner wall of the valve seat, and a second O-ring is provided between the outer wall of the valve seat and the inner wall of the medium channel; a square spiral groove is provided on the outer peripheral surface of the valve seat, and a cooling inlet and a cooling outlet are provided on the valve body, which are respectively located on both axial sides of the square spiral groove; the two ends of the square spiral groove are respectively connected to the cooling inlet and the cooling outlet.

[0009] As a preferred technical solution of the present invention, the valve body includes a left valve cover, a right valve cover and a rotary chamber formed by the two; the valve disc can be rotatably supported in the rotary chamber; valve seats are fixedly installed in the left valve cover and the right valve cover, and each valve seat is respectively equipped with a set of independent spacing fine-tuning mechanisms.

[0010] As a preferred technical solution of the present invention, it also includes a support base for fixing the valve body; the spacing fine-tuning mechanism also includes: a stepping motor, fixed to the support base, whose output shaft is connected to the driving gear; a transmission gear, coaxially fixed to the outer circumferential surface of the valve seat and meshing with the driving gear; a displacement sensor, fixed to the valve body through a sensor bracket, whose detection end points to the end face of the valve seat, for monitoring the axial displacement of the valve seat.

[0011] As a preferred technical solution of the present invention, the fixing frame includes: a fixing plate, which is connected to the valve body through a support rod; a connecting plate, whose sleeve portion is inserted into the connecting hole of the fixing plate; a baffle, which is arranged at the end of the sleeve portion; an adjusting gasket, which is arranged between the baffle and the fixing plate; a bolt, which passes through the baffle, the adjusting gasket and the fixing plate and is threadedly connected; a first mounting hole and a second mounting hole are coaxially provided on the connecting plate, the first flow channel pipe is fixed to the first mounting hole, and the second flow channel pipe is fixed to the second mounting hole.

[0012] As a preferred technical solution of the present invention, the rotary drive mechanism includes: a drive motor, a second pulley is provided at its output end; a drive shaft, one end of which is connected to the valve disc and the other end of which is provided with a first pulley; a transmission belt, which is sleeved on the first pulley and the second pulley.

[0013] As a preferred technical solution of the present invention, the drive shaft includes a first rotating shaft body connected to the end face of the valve disc; a first stuffing box is opened in the left valve cover; the inner end of the first rotating shaft body extends into the first stuffing box, and a first rotating lip seal ring, a gasket, and a needle bearing are sequentially mounted, and the end of the first stuffing box is closed by a sealing cover.

[0014] As a preferred technical solution of the present invention, the drive shaft also includes a second rotating shaft body, which is connected to the other end of the valve disc; a second stuffing box is opened in the right valve cover; the inner end of the second rotating shaft body extends into the second stuffing box, and is sequentially sleeved with: a second rotating lip seal ring, a one-way thrust ball bearing, and a deep groove ball bearing; the outer end portion of the second rotating shaft body is provided with an external thread and is axially fixed by a locking nut.

[0015] As a preferred technical solution of the present invention, a valve stem core assembly is provided in the first rotating shaft body and the valve stem core assembly is fixed relative to the valve body. The valve stem core assembly includes a plug, a valve core upper end rod, a valve core lower end rod and a water spray disc connected in sequence. A cooling water channel is formed between the plug, the valve core upper end rod and the valve core lower end rod. An inner sleeve is provided in the cooling water channel, and the inner cavity of the inner sleeve constitutes a first fluid channel. One end of the inner sleeve extends into the plug and the other end extends into the water spray disc. A water inlet pipe is provided on the plug, and a cooling chamber is provided in the valve disc. The inner end of the first rotating shaft body is open and communicated with the cooling chamber. The water spray disc is located in the cooling chamber, and a second fluid channel is formed between the inner wall of the first rotating shaft and the outer wall of the lower end rod of the valve core, and the second fluid channel is connected to the cooling chamber. The outer wall of the lower end rod of the valve core is provided with a plurality of through holes, and the inner wall of the lower end rod of the valve core and the outer wall of the inner sleeve form a third fluid channel. The inner wall of the upper end cover of the valve core and the outer wall of the inner sleeve form a fourth fluid channel. The third fluid channel and the fourth fluid channel are connected, and the upper end cover of the valve core is provided with a water outlet pipe connected to the fourth fluid channel. The water inlet pipe, the first fluid channel, the second fluid channel, the third fluid channel, the fourth fluid channel and the water outlet pipe constitute a circulating cooling channel.

[0016] Compared with the prior art, the beneficial effects of the present invention are as follows: the present invention achieves a breakthrough effect through the collaborative design of the spacing fine-tuning mechanism: the valve seat is sleeved on the first flow channel tube of the fixed frame, and the rotation is accurately converted into axial displacement by means of the meshing transmission of the threaded pair, and the quantitative indication of the scale line is combined to achieve precise control of the micro-gap of ≤0.04mm between the sealing pairs, so that the leakage rate under high-frequency pulse conditions is stable at ≤5‰, and the valve disc can be prevented from wearing, making noise, generating sparks and other problems due to high-speed rotation, thereby improving safety performance; the square-tooth spiral groove on the outer wall of the valve seat connects the cooling inlet and the cooling outlet, forcing the cooling medium to flow through the O-ring area (to prevent high-temperature gas from flowing outside), thereby preventing high-temperature gas from affecting the operation of the O-ring, improving service life, and completely solving the bottlenecks of sealing failure and thermal deformation of transient high-energy erosion test equipment. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 This is a schematic structural diagram of the high-temperature and high-pressure ultrafast pulse control valve of the present invention; Figure 2 It is a structural schematic diagram of the spacing fine-tuning mechanism of the present invention; Figure 3 It is a structural schematic diagram of the fixing frame in the present invention; Figure 4 It is a structural schematic diagram of the drive shaft and valve stem core assembly in the present invention; Figure 5 It is a structural schematic diagram of the valve stem core assembly in the present invention; Figure 6 yes Figure 4 Enlarged view of part A; Figure 7 yes Figure 4 Enlarged view of part B; Figure 8 It is a structural schematic diagram of the valve disc end face in the present invention; Figure 9 This is a schematic diagram of the structure of the valve seat driven by the electric control method in the present invention; Figure 10 It is a structural schematic diagram of the first rotating shaft and the first stuffing box in the present invention; Figure 11 It is a structural schematic diagram of the second rotating shaft and the second stuffing box in the present invention.

[0018] Figure numerals: 1, valve body; 2, medium channel; 3, valve seat; 4, vent hole; 5, air hole; 6, rotary drive mechanism; 7, spacing fine-tuning mechanism; 8, fixing frame; 9, first flow channel tube; 10, scale line; 11, first O-ring; 12, second O-ring; 13, cooling inlet; 14, cooling outlet; 15, square-tooth spiral groove; 16, left valve cover; 17, right valve cover; 18, rotary chamber; 19, support base; 20, stepping motor; 21, driving gear; 22, transmission gear; 23, displacement sensor; 24, sensor bracket; 25, fixing plate; 26, support rod; 27, connecting plate; 28, sleeve; 29, connecting hole; 30, baffle; 31, adjusting gasket; 32, bolt; 33, first mounting hole; 34, second mounting hole; 35, second flow channel tube; 36, drive Motor; 37. Second pulley; 38. First pulley; 39. Drive belt; 40. First rotating shaft; 41. First stuffing box; 42. First rotating lip seal; 43. Gasket; 44. Needle roller bearing; 45. Sealing cover; 46. Second rotating shaft; 47. Second stuffing box; 48. Second rotating lip seal; 49. One-way thrust ball bearing; 50. Deep groove ball bearing; 51. Locking nut; 52. Valve stem core assembly; 53. Plug; 54. Upper end rod of valve core; 55. Lower end rod of valve core; 56. Spray disc; 57. Cooling water channel; 58. Inner sleeve; 59. First fluid channel; 60. Second fluid channel; 61. Water inlet pipe; 62. Cooling chamber; 63. Third fluid channel; 64. Fourth fluid channel; 65. Water outlet pipe; 66. Through hole; 67. Valve disc; 68. Fastening screw. DETAILED DESCRIPTION

[0019] In order to make the technical means, creative features, objectives and effects achieved by the present invention easier to understand, the present invention is further described below in conjunction with specific implementation methods.

[0020] In the description of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "installed," "provided with," "connected," etc., should be understood in a broad sense. For example, "connected" may refer to a fixed connection, a detachable connection, or an integral connection; it may refer to a mechanical connection or an electrical connection; it may refer to a direct connection or an indirect connection through an intermediate medium; it may refer to internal communication between two components. Those skilled in the art will be able to understand the specific meanings of the above terms in the present invention based on the specific circumstances.

[0021] like Figure 1-11The high-temperature, high-pressure, ultrafast pulse control valve shown in FIG. 1 includes: a valve body 1 having a medium passage 2 therein; a valve seat 3 mounted within the valve body 1 and having a vent hole 4 therein communicating with the medium passage 2; a valve flap 67 having a plurality of vent holes 5 distributed circumferentially on its end surface, the valve flap 67 being rotatably supported within the valve body 1; a rotary drive mechanism 6 connected to the valve flap 67 and configured to drive the valve flap 67 to periodically rotate so that the vent holes 5 and the vent holes 4 periodically coincide with each other to achieve intermittent communication with the medium passage 2; and further comprising: The spacing fine-tuning mechanism 7 is used to precisely adjust the axial gap between the sealing surface of the valve seat 3 and the sealing surface of the valve disc 67; the spacing fine-tuning mechanism 7 includes: a fixing frame 8, which is fixedly connected to the valve body 1; a first flow channel tube 9, one end of which is fixedly connected to the fixing frame 8; the valve seat 3 is sleeved on the other end of the first flow channel tube 9 and is connected to the first flow channel tube 9 through a threaded pair; the outer peripheral surface of the valve seat 3 is evenly distributed with scale lines 10, which are used to indicate the corresponding relationship between the rotation angle and the axial displacement. In this embodiment, manual adjustment or intelligent control can be selected.

[0022] The present invention achieves a breakthrough through the coordinated design of the spacing fine-tuning mechanism 7: the valve seat 3 is mounted on the first flow channel tube 9 of the fixed frame 8. The threaded engagement transmission precisely converts rotation into axial displacement. Combined with the quantitative indication of the scale lines, this allows precise control of the micro-gap between the sealing pairs to a value of ≤0.04 mm, ensuring a stable leakage rate of ≤5‰ under high-frequency pulse conditions. This also prevents wear, noise, and sparking of the valve disc 67 caused by high-speed rotation, thereby improving safety. The square-tooth spiral groove 15 on the outer wall of the valve seat 3 connects the cooling inlet 13 and the cooling outlet 14, forcing the cooling medium to flow through the O-ring (to prevent high-temperature gas from affecting the operation of the O-ring), preventing high-temperature gas from affecting the operation of the O-ring, extending its service life, and completely resolving the bottlenecks of seal failure and thermal deformation in transient high-energy erosion test equipment. It should be noted that the square-tooth spiral groove 15 forms a closed flow channel with the inner wall of the medium channel 2, allowing cooling water to flow along the path of the square-tooth spiral groove 15. The fine-tuning of the valve seat 3 in this application ensures that the cooling inlet 13 and the cooling outlet 14 are always connected to the square-tooth spiral groove 15.

[0023] Because the medium in this application is high-temperature, high-pressure gas, the valve disc 67 and valve seat 3 sealing pair must be made of metal sealing materials. Furthermore, the relative motion speed of the sealing pair is extremely fast, reaching a linear velocity of 9.18 m / s. If the sealing pair contacts and rubs, it will generate loud noise and sparks, posing a significant safety risk. Therefore, a gap must be left between the sealing pairs. The size of the gap directly affects the leakage rate. The user leakage rate is ≤5‰, which requires precise control of the gap. The following describes two modes of control: manual and intelligent.

[0024] Manual method is adopted: the key mechanism of fine-tuning is the threaded connection between the valve seat 3 and the first flow channel tube 9. The first flow channel tube 9 is kept in a fixed position by the fixing frame 8. The valve seat 3 can realize axial movement by rotation. The outer circumference of the rotating sleeve is engraved with 100 evenly distributed scale lines 10, and the moving distance of each grid is 0.02mm. Before adjustment, perform coarse adjustment through the adjusting gasket 31 on the connecting plate 27, and then perform fine adjustment with the valve seat 3. The fine adjustment method is to first rotate the valve seat 3 so that the end face of the valve seat 3 contacts the end face of the valve disc 67, mark the scale, and then rotate the valve seat 3 (in the current state: the valve seat 3 and the end of the first flow channel tube 9 are not in close contact, leaving an appropriate gap, which is controlled by adjusting the gasket 31), the valve seat 3 is separated from the plane of the valve disc 67, and then rotate the valve seat 3 for fine adjustment, the forward scale is reduced by 2 grids compared with the previous one, and then tighten the positioning screws on the side wall of the valve body 1 so that the inner end of the fastening screw 68 is against the outer wall of the valve seat 3 (to keep the position of the valve seat 3 fixed), so as to ensure that the gap between the valve seat 3 and the end face of the valve disc 67 is 0.04 mm. In this embodiment, a spacing fine-tuning mechanism 7 is provided on both sides of the valve disc 67.

[0025] The intelligent control method for the displacement of the valve seat 3 also includes a support base 19 that secures the valve body 1. The spacing fine-adjustment mechanism 7 also includes a stepper motor 20 secured to the support base 19, its output shaft connected to a driving gear 21. A transmission gear 22 is coaxially fixed to the outer circumference of the valve seat 3 and meshes with the driving gear 21. A displacement sensor 23 is secured to the valve body 1 via a sensor bracket 24, with its detection end pointing toward the end face of the valve seat 3, monitoring the axial displacement of the valve seat 3. The specific control method involves mounting the displacement sensor 23 on the sensor bracket 24, and controlling the movement of the valve seat 3 using the stepper motor 20. During initial valve commissioning, a flowmeter is installed at the outlet to maintain the valve disc 67 in the closed position. The flowmeter then displays the leakage of the sealing pair. The valve has a load flow rate of 1 kg / s, and a volume of 20.79 liters / second (dm³ / s) at 730°C and a pressure of 10 MPa. The allowable leakage of 5‰ is 20.79×5‰=0.104 (L / S). The value measured by the flow meter in real time is sent as a signal to the PLC control center. The control center compares it with the allowable leakage value and sends instructions to the displacement sensor 23 and the micro stepping motor 20. The micro stepping motor 20 is driven by gears, and the valve seat 3 is threadedly matched with the first flow channel tube 9. The axial movement of the valve seat 3 can adjust the gap between the valve disc 67 and the valve seat 3, and change the leakage rate until it is satisfactory. The present invention does not involve improvements in circuit control, so no corresponding circuit control diagram is provided. This is prior art.

[0026] Intelligent control of pulsed airflow frequency: A stepless speed-regulating motor drives the valve stem and disc 67 assembly to rotate at a high speed of 450 r / min. Disc 67 has eight air holes 5 (arc-shaped square holes) evenly distributed around its circumference, while the valve seat 3 has a fixed air vent 4. When the holes in disc 67 and seat 3 overlap, airflow is connected; when they do not, airflow is cut off. This control utilizes the overlap between the holes in disc 67 and seat 3 to achieve 60 on-off cycles per second, creating a 60 Hz pulse effect. Specifically, an encoder (not shown) is installed on the outer circumference of the drive shaft, which operates synchronously with disc 67, to monitor disc 67's speed in real time. Because disc 67 has eight flow holes around its circumference, the ratio of pulsed airflow frequency to disc 67 speed is 1:8. For a desired pulse frequency of 60 Hz, the encoder display should read 60 ÷ 8 = 7.5 r / s. The motor speed, calculated based on the transmission ratio, is 450 r / min. If the encoder's measured data is 7 r / s, that is, the pulse airflow frequency is 7×8=56 (HZ), which does not reach the ideal value, it means that the speed of the stepless speed regulation motor has decreased. At this time, the encoder will send a command to the central control PLC system. The PLC system automatically adjusts the motor speed to 450 r / min through the calculated motor speed. This application briefly explains the principle and does not involve improvements in circuit control. This is existing technology.

[0027] The inner wall of the valve seat 3 is provided with an internal thread; the outer wall of the first flow channel tube 9 is provided with an external thread; by rotating the valve seat 3, the external thread engages with the internal thread and drives the valve seat 3 to move axially along the first flow channel tube 9.

[0028] A first O-ring 11 is installed between the outer wall of the first flow channel 9 and the inner wall of the valve seat 3, and a second O-ring 12 is installed between the outer wall of the valve seat 3 and the inner wall of the medium channel 2. A square-thread spiral groove 15 is formed on the outer circumference of the valve seat 3. A cooling inlet 13 and a cooling outlet 14 are provided on the valve body 1, located axially on either side of the square-thread spiral groove 15. The two ends of the square-thread spiral groove 15 connect the cooling inlet 13 and the cooling outlet 14, respectively. The gas temperature within the first and second flow channel 9 and 35 is 1000K. To prevent leakage of high-temperature gas, fluororubber O-rings are installed on the outside of the valve seat 3 and the first flow channel 9. To ensure the proper function of the O-rings, a cleverly designed square-thread pair is employed. The cooling inlet 13, the square-thread spiral groove 15, and the cooling outlet 14 enable water circulation, achieving an ideal cooling effect.

[0029] The valve body 1 includes a left valve cover 16, a right valve cover 17 and a rotary chamber 18 formed by the two; the valve disc 67 can be rotatably supported in the rotary chamber 18; valve seats 3 are fixedly installed in the left valve cover 16 and the right valve cover 17, and each valve seat 3 is respectively equipped with a set of independent spacing fine-tuning mechanisms 7.

[0030] The fixing frame 8 includes: a fixing plate 25, which is connected to the valve body 1 through a support rod 26 (the connection method is a common method in the mechanical field, which is existing technology and is therefore not elaborated in detail); a connecting plate 27, whose sleeve portion 28 is inserted into the connecting hole 29 of the fixing plate 25; a baffle 30, which is arranged at the end of the sleeve portion 28; an adjusting gasket 31, which is arranged between the baffle 30 and the fixing plate 25; a bolt 32, which passes through the baffle 30, the adjusting gasket 31 and is threadedly connected to the fixing plate 25; a first mounting hole 33 and a second mounting hole 34 are coaxially provided on the connecting plate 27, the first flow channel tube 9 is fixed to the first mounting hole 33, and the second flow channel tube 35 is fixed to the second mounting hole 34.

[0031] The rotary drive mechanism 6 includes: a drive motor 36 , an output end of which is provided with a second pulley 37 ; a drive shaft, one end of which is connected to the valve disc 67 , and the other end of which is provided with a first pulley 38 ; a transmission belt 39 , which is sleeved on the first pulley 38 and the second pulley 37 .

[0032] The drive shaft includes a first rotating shaft 40 connected to the end face of the valve disc 67. A first stuffing box 41 is defined within the left valve cover 16. The inner end of the first rotating shaft 40 extends into the first stuffing box 41 and is fitted with a first rotating lip seal 42, a gasket 43, and a needle roller bearing 44 (a single-row needle roller bearing 44) in sequence. The end of the first stuffing box 41 is sealed by a sealing gland 45. In this application, a needle roller bearing 44 is installed between the first rotating shaft 40 and the first stuffing box 41. The needle roller bearing 44 is compact and occupies little space. The inner ring of the needle roller bearing 44 rotates at high speed with the valve stem, while the outer ring contacts the first stuffing box 41, ensuring easy and frictionless sealing and effortless opening and closing. The second rotating shaft 46 also incorporates a one-way thrust ball bearing 49 and a deep groove ball bearing 50, reducing torque by 40%.

[0033] The drive shaft also includes a second rotating shaft body 46, which is connected to the other end of the valve disc 67; a second stuffing box 47 is opened in the right valve cover 17; the inner end of the second rotating shaft body 46 extends into the second stuffing box 47, and is sequentially sleeved with: a second rotating lip seal ring 48, a one-way thrust ball bearing 49, and a deep groove ball bearing 50; the outer end of the second rotating shaft body 46 is provided with an external thread and is axially fixed by a locking nut 51.

[0034] A valve stem core assembly 52 is provided in the first rotating shaft body 40 and the valve stem core assembly 52 is fixed relative to the valve body 1 (it automatically remains fixed when welded or connected with bolts 32 or connected with a rigid water pipe). The valve stem core assembly 52 includes a plug 53, a valve core upper end rod 54, a valve core lower end rod 55 and a water spray plate 56 connected in sequence. A cooling water channel 57 is formed between the plug 53, the valve core upper end rod 54 and the valve core lower end rod 55. An inner sleeve 58 is provided in the cooling water channel 57, and the inner cavity of the inner sleeve 58 constitutes a first fluid channel 59. One end of the inner sleeve 58 extends into the plug 53 and the other end extends into the water spray plate 56. A water inlet pipe 61 is provided on the plug 53. A cooling chamber 62 is provided in the valve disc 67. The inner end of the first rotating shaft body 40 is open and communicates with the cooling chamber 62. The water spray plate 56 is located in the cooling chamber 62. A second fluid channel 60 is formed between the inner wall of the first rotating shaft 40 and the outer wall of the lower end rod 55 of the valve core, and the second fluid channel 60 is connected to the cooling chamber 62. A plurality of through holes 66 are provided on the outer wall of the lower end rod 55 of the valve core. A third fluid channel 63 is formed by the inner wall of the lower end rod 55 of the valve core and the outer wall of the inner sleeve 58. A fourth fluid channel 64 is formed by the inner wall of the upper end cover of the valve core and the outer wall of the inner sleeve 58. The third fluid channel 63 and the fourth fluid channel 64 are connected. A water outlet pipe 65 connected to the fourth fluid channel 64 is provided on the upper end cover of the valve core. The water inlet pipe 61, the first fluid channel 59, the second fluid channel 60, the third fluid channel 63, the fourth fluid channel 64 and the water outlet pipe 65 constitute a circulating cooling channel. In this embodiment, the plug 53, the upper end rod 54 of the valve core, the lower end rod 55 of the valve core and the water spray plate 56 are fixed.

[0035] The above shows and describes the basic principles, main features and advantages of the present invention. Those skilled in the art should understand that the present invention is not limited to the above embodiments. The above embodiments and descriptions are only preferred examples of the present invention and are not used to limit the present invention. Without departing from the spirit and scope of the present invention, the present invention may have various changes and improvements, and these changes and improvements fall within the scope of the present invention to be protected. The scope of protection of the present invention is defined by the attached claims and their equivalents.

Claims

1. A high-temperature, high-pressure, ultrafast pulse control valve, comprising: A valve body (1) is provided with a medium channel (2); a valve seat (3) is installed in the valve body (1), and a vent hole (4) is provided in the valve seat (3) and is communicated with the medium channel (2); a valve flap (67) has a plurality of vent holes (5) distributed along the circumference of the end surface thereof, and the valve flap (67) is rotatably supported in the valve body (1); a rotary drive mechanism (6) is connected to the valve flap (67) and is used to drive the valve flap (67) to rotate periodically so that the vent holes (5) and the vent holes (4) are periodically overlapped to achieve intermittent conduction of the medium channel (2). The invention is characterized in that it further comprises: a spacing fine-tuning mechanism (7) for precisely adjusting the axial gap between the sealing surface of the valve seat (3) and the sealing surface of the valve disc (67); the spacing fine-tuning mechanism (7) comprises: a fixing frame (8) fixedly connected to the valve body (1); a first flow channel tube (9) one end of which is fixedly connected to the fixing frame (8); the valve seat (3) is sleeved on the other end of the first flow channel tube (9) and connected to the first flow channel tube (9) through a threaded pair; and scale lines (10) are uniformly distributed on the outer peripheral surface of the valve seat (3) for indicating the corresponding relationship between the rotation angle and the axial displacement.

2. The high-temperature, high-pressure, ultrafast pulse control valve according to claim 1, characterized in that: The inner wall of the valve seat (3) is provided with an internal thread; the outer wall of the first flow channel (9) is provided with an external thread; by rotating the valve seat (3), the external thread engages with the internal thread to drive the valve seat (3) to move axially along the first flow channel (9).

3. The high-temperature, high-pressure, ultrafast pulse control valve according to claim 1, characterized in that: A first O-ring (11) is provided between the outer wall of the first flow channel tube (9) and the inner wall of the valve seat (3), and a second O-ring (12) is provided between the outer wall of the valve seat (3) and the inner wall of the medium channel (2); a square-tooth spiral groove (15) is provided on the outer peripheral surface of the valve seat (3); a cooling inlet (13) and a cooling outlet (14) are provided on the valve body (1), and the cooling inlet (13) and the cooling outlet (14) are respectively located on both axial sides of the square-tooth spiral groove (15); and the two ends of the square-tooth spiral groove (15) are connected to the cooling inlet (13) and the cooling outlet (14).

4. The high-temperature, high-pressure, ultrafast pulse control valve according to claim 1, characterized in that: The valve body (1) comprises a left valve cover (16), a right valve cover (17) and a rotary chamber (18) formed by the left and right valve covers; the valve flap (67) is rotatably supported in the rotary chamber (18); valve seats (3) are fixedly installed in the left valve cover (16) and the right valve cover (17), and each valve seat (3) is respectively equipped with a set of independent spacing fine-tuning mechanisms (7).

5. The high-temperature, high-pressure, ultrafast pulse control valve according to claim 1, characterized in that: The invention also includes a support base (19) for fixing the valve body (1); the spacing fine-tuning mechanism (7) also includes: a stepping motor (20) fixed to the support base (19), the output shaft of which is connected to the driving gear (21); a transmission gear (22) coaxially fixed to the outer circumferential surface of the valve seat (3) and meshing with the driving gear (21); a displacement sensor (23) fixed to the valve body (1) through a sensor bracket (24), the detection end of which points to the end face of the valve seat (3) and is used to monitor the axial displacement of the valve seat (3).

6. The high-temperature, high-pressure, ultrafast pulse control valve according to claim 5, characterized in that: The fixing frame (8) includes: a fixing plate (25) connected to the valve body (1) through a support rod (26); a connecting plate (27), a sleeve portion (28) of which is inserted into a connecting hole (29) of the fixing plate (25); a baffle (30) arranged at the end of the sleeve portion (28); an adjusting gasket (31) arranged between the baffle (30) and the fixing plate (25); a bolt (32) passing through the baffle (30), the adjusting gasket (31) and the fixing plate (25) for threaded connection; a first mounting hole (33) and a second mounting hole (34) are coaxially provided on the connecting plate (27); the first flow channel tube (9) is fixed to the first mounting hole (33), and the second flow channel tube (35) is fixed to the second mounting hole (34).

7. The high-temperature, high-pressure, ultrafast pulse control valve according to any one of claims 4 to 6, characterized in that: The rotary drive mechanism (6) comprises: a driving motor (36), the output end of which is provided with a second pulley (37); a driving shaft, one end of which is connected to the valve flap (67) and the other end of which is provided with a first pulley (38); and a transmission belt (39) which is sleeved on the first pulley (38) and the second pulley (37).

8. The high-temperature, high-pressure, ultrafast pulse control valve according to claim 7, characterized in that: The drive shaft includes a first rotating shaft body (40) connected to the end face of the valve disc (67); a first stuffing box (41) is opened in the left valve cover (16); the inner end of the first rotating shaft body (40) extends into the first stuffing box (41), and a first rotating lip seal ring (42), a gasket (43), and a needle bearing (44) are sequentially sleeved thereon, and the end of the first stuffing box (41) is closed by a sealing cover (45).

9. The high-temperature, high-pressure, ultrafast pulse control valve according to claim 8, characterized in that: The drive shaft also includes a second rotating shaft (46), which is connected to the other end of the valve disc (67); a second stuffing box (47) is opened in the right valve cover (17); the inner end of the second rotating shaft (46) extends into the second stuffing box (47) and is sequentially sleeved with: a second rotating lip seal (48), a one-way thrust ball bearing (49), and a deep groove ball bearing (50); the outer end of the second rotating shaft (46) is provided with an external thread and is axially fixed by a locking nut (51).

10. The high-temperature, high-pressure, ultrafast pulse control valve according to claim 8 or 9, characterized in that: A valve stem core assembly (52) is provided in the first rotating shaft (40), and the valve stem core assembly (52) is fixed relative to the valve body (1). The valve stem core assembly (52) includes a plug (53), a valve core upper end rod (54), a valve core lower end rod (55) and a water spray disc (56) connected in sequence. A cooling water channel (57) is formed between the plug (53), the valve core upper end rod (54) and the valve core lower end rod (55). An inner sleeve (58) is provided in the cooling water channel (57), and the inner cavity of the inner sleeve (58) constitutes a first fluid channel (59). One end of the inner sleeve (58) extends into the plug (53) and the other end extends into the water spray disc (56). A water inlet pipe (61) is provided on the plug (53). A cooling chamber (62) is provided in the valve disc (67). The inner end of the first rotating shaft (40) is open and communicates with the cooling chamber (62). The water spray The disk (56) is located in the cooling chamber (62), a second fluid channel (60) is formed between the inner wall of the first rotating shaft (40) and the outer wall of the lower end rod (55) of the valve core, and the second fluid channel (60) is connected to the cooling chamber (62), the outer wall of the lower end rod (55) of the valve core is provided with a plurality of through holes (66), the inner wall of the lower end rod (55) of the valve core and the outer wall of the inner sleeve (58) form a third fluid channel (63), the inner wall of the upper end cover of the valve core and the outer wall of the inner sleeve (58) form a fourth fluid channel (64), the third fluid channel (63) and the fourth fluid channel (64) are connected, the upper end cover of the valve core is provided with a water outlet pipe (65) connected to the fourth fluid channel (64), the water inlet pipe (61), the second fluid channel (59), the second fluid channel (60), the third fluid channel (63), the fourth fluid channel (64) and the water outlet pipe (65) constitute a circulating cooling channel.

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