Gas inlet valve with independent rotating seal ring

Abstract

The application discloses a gas inlet valve with an independent rotating sealing ring, belongs to the technical field of valves and engine gas fuel supply, and solves how to develop a gas inlet valve with the following characteristics: a main valve core keeps non-rotation, only a low-mass independent sealing working part carries out limited rotation in a disengagement stage, can be reliably locked after falling into a seat, and a rotating mechanism failure does not affect the main closing function. An independent ring-shaped sealing part which can be axially followed and relatively limited circumferentially rotated is kept on the main valve core in the valve body. When the main valve is opened, a pressure difference is formed between a high static pressure area of a supply cavity and a low static pressure area near an opening throttling gap, auxiliary gas is driven to rotate the sealing part by a tangential micro-injection port by a distance of a positioning tooth pitch, and a stop pawl then prevents continuous rotation. When the main valve falls into the seat again, a first axial displacement removes the stop, a second axial displacement completes low-load micro-wiping, and then locking is achieved. The application only rotates an independent low-mass ring-shaped sealing part, and reduces the rotating inertia and coupling with a guide structure, an execution structure and a detection structure.

Description

Technical Field

[0001] This invention belongs to the field of valve and engine gas fuel supply technology, and specifically relates to a gas intake valve with an independent indexable sealing ring. This invention is applicable to marine natural gas engines, marine natural gas / liquid fuel dual-fuel engines, stationary gas engines, dual-fuel generator sets, and other internal combustion engines requiring high-frequency, rapid on / off supply of gaseous fuel. Background Technology

[0002] Marine dual-fuel engines typically introduce gaseous fuels, such as natural gas, periodically into the intake or scavenging passages via a gas intake valve, allowing the fuel to mix with air before entering the cylinders. The flow capacity, sealing performance, and circulation consistency of the gas intake valve directly affect the fuel supply to each cylinder and the engine's operational safety.

[0003] The gas intake valve requires frequent opening and closing during engine operation. The main valve core or valve plate repeatedly moves away from and impacts the fixed valve seat under the combined action of the return spring, actuator, and gas pressure differential. Its sealing surface endures cyclic impacts and must also limit gaseous fuel leakage when closed. With the main valve core's circumferential position remaining essentially unchanged, the valve core sealing surface repeatedly contacts the same circumferential area of ​​the fixed valve seat over a long period. Manufacturing errors, thermal deformation, and localized particles can further concentrate the contact load, potentially leading to localized indentations and uneven wear. Tiny particles from the natural gas pipeline, metal shavings from processing or maintenance, and contaminants entering from the intake passage in reverse can accumulate near the sealing strip. When particles are trapped between the sealing surfaces, localized contact stress increases, potentially causing closing gaps and continuous leakage.

[0004] Existing engine valve rotators can use spring load changes, ball ramps, or ratchet mechanisms to gradually rotate the entire valve and related retaining components; other solutions utilize fluid acting on the valve head vanes to slowly rotate the entire lift valve around the valve stem axis, thereby changing the contact position between the valve and the valve seat.

[0005] However, for high-speed gas intake valves, directly rotating the main valve core, valve stem, armature, and moving parts connected to the actuator as a whole will increase the moment of inertia and may couple with the valve stem guide, electromagnetic clearance, hydraulic pilot connection, or position detection structure, which is not conducive to maintaining rapid axial response and stable guidance.

[0006] Furthermore, if the sealing surface is forced to slide in a large circumferential direction under a high sealing load when fully closed, abrasive scratches may be amplified; if it is driven by continuous tangential airflow without single-step stop, the seal may rotate continuously, making it difficult to guarantee the next seating position and the life of the mechanism.

[0007] Therefore, a gas intake valve is needed that keeps the main valve core non-rotating, allows only the low-mass independent sealing component to rotate to a limited extent during the off-seat phase, reliably locks after seating, and whose main shut-off function is not affected by the failure of the rotation mechanism. Summary of the Invention

[0008] In view of this, in order to solve the problems of how to periodically change the circumferential seating position of the gas intake valve sealing surface without rotating the main valve core, valve stem and actuator as a whole, so as to reduce local wear caused by repeated impacts in a fixed position for a long time; how to make the independent annular seal complete a limited rotation step only in an appropriate off-seat state and stop after reaching the adjacent positioning position, so as to avoid the auxiliary airflow causing it to rotate continuously; how to achieve optional micro-wiping and particle discharge with a small contact load in the initial closing stage, and prohibit circumferential sliding after complete closure, so as to balance the cleaning effect and the protection of the high-load sealing surface; how to separate the micro-rotation function from the main closing load transmission path, so that the gas intake valve can still close axially and cut off the gas when the micro-nozzle is blocked, the positioning component is stuck or the sealing ring cannot rotate; and how to avoid the auxiliary gas forming a bypass leakage around the fixed valve seat, and make the single-step stop release, low-load micro-wiping and final locking occur in a determined axial stroke sequence, this invention proposes a gas intake valve with an independent rotation sealing ring.

[0009] To achieve the above objectives, the present invention adopts the following technical solution: a gas intake valve with an independent indexing sealing ring, comprising a valve body, a fixed valve seat, a main valve core driven by a valve stem and selectively sealing with the fixed valve seat, an independent annular seal, a micro-indexing drive structure, a one-way positioning component, a seat locking component, and an axial bearing structure. The main valve core is restricted from circumferential rotation relative to the valve body by a guide anti-rotation structure and can reciprocate along its own axis. An independent annular seal is provided on the side of the main valve core facing the fixed valve seat. The independent annular seal moves axially with the main valve core and can be rotated in a limited circumferential direction relative to the main valve core in the rotated state separated from the fixed valve seat. The micro-rotation drive structure is used to apply circumferential driving force to the independent annular seal in the rotated state. The one-way positioning component is used to allow the independent annular seal to rotate from the current positioning position to the adjacent positioning position and to maintain a single-step stop state after reaching the adjacent positioning position. During the reseating process, after the annular seal initially contacts the fixed valve seat, the first axial displacement of the independent annular seal relative to the main valve core releases the single-step stop state. The reseating locking component then engages and restricts the circumferential movement of the independent annular seal when it is fully seated. The axial bearing structure includes an axial bearing shoulder disposed on the main valve core. The axial bearing shoulder can transmit axial closing load to the independent annular seal without relying on the action of the micro-rotation drive structure, the one-way positioning component and the seat locking component, so that when the rotation, stop or locking action cannot be completed, the independent annular seal can still be pressed against the fixed valve seat.

[0010] Preferably, the main valve core has an annular mounting portion on the side facing the fixed valve seat, and an independent annular seal is provided in the annular mounting portion. The independent annular seal has an annular sealing band for cooperating with the fixed valve seat. The annular mounting section is provided with an annular retainer, an axial elastic element, and an axial floating gap. The annular retainer restricts the independent annular seal from detaching from the main valve core. The axial elastic element allows the independent annular seal to float slightly axially relative to the main valve core between a first axial position after being fully seated and a second axial position after being dismounted. The axial elastic element is a wave spring, disc spring, elastic washer ring, or an axial spring spaced along the circumference. The axial floating gap is 0.02 to 0.30 mm.

[0011] Preferably, the micro-rotation drive structure includes a micro-rotation drive channel, an auxiliary gas inlet communicating with the upstream high static pressure region of the gas supply chamber, and a tangential micro-nozzle facing the independent annular seal; the tangential micro-nozzle opens on the upstream side of the fixed valve seat and is adjacent to the local low static pressure region of the opening throttling gap formed after the main valve core leaves the seat. When the main valve core leaves the seat, the main gas is accelerated through the opening throttling gap, making the static pressure Ps of the upstream high static pressure region higher than the static pressure Pt of the local low static pressure region, and forming a driving pressure difference at both ends of the micro-rotation drive channel; the tangential micro-nozzle opens on the upstream side of the fixed valve seat and is adjacent to the local low static pressure region of the opening throttling gap formed after the main valve core leaves the seat. The nozzle causes the auxiliary gas, driven by the pressure difference, to generate a velocity component along the circumferential direction of the independent annular seal; the tangential micro-nozzle and its corresponding flow receiving area are both located upstream of the fixed valve seat, and the auxiliary gas, after being discharged from the tangential micro-nozzle, still enters the upstream gas space controlled by the main valve core and the fixed valve seat; when the main valve core is completely closed, the static pressure of the upstream high static pressure area and the local low static pressure area tend to be consistent, and the micro-rotation drive flow channel cannot bypass the fixed valve seat and directly connect to the gas outlet; the micro-rotation drive flow channel is provided with a flow limiting orifice or a throttling section.

[0012] Preferably, the independent annular seal has flow-receiving portions arranged at intervals along the circumference, wherein the flow-receiving portions are at least one of miniature flow-receiving blades, tangential grooves, oblique flow-receiving grooves, and flow-receiving cavities.

[0013] Preferably, chip removal grooves are provided on the radially inner side, radially outer side, or both sides of the annular sealing strip. These grooves extend radially or inclined relative to the radial direction to guide particles into the main gas flow path. The chip removal grooves are located outside the effective continuous sealing area of ​​the annular sealing strip, or terminate within the effective continuous sealing area without penetrating its entire radial width, to avoid forming a direct through-flow path from the gas supply chamber to the gas outlet in the fully seated state. The jet from at least one of the tangential micro-nozzles covers the adjacent area of ​​the annular sealing strip or the chip removal grooves to purge the gas after the independent annular seal is removed. The chip removal grooves guide impurities out under the jet action of the tangential micro-nozzles to prevent impurity accumulation from affecting the sealing performance of the annular sealing strip.

[0014] Preferably, the unidirectional positioning assembly includes annular positioning teeth disposed on the independent annular seal, an elastic positioning element disposed on the main valve core, a single-step stop portion, a reset guide portion, a pivot, a stop reset spring, and a stop groove; the single-step stop portion is a stop pawl pivotally mounted on the main valve core via a pivot, and biased by the stop reset spring in a direction engaging with the stop groove of the annular positioning teeth; the elastic positioning element allows the independent annular seal to cross a positioning tooth pitch in a predetermined direction, and the stop pawl enters the stop groove after crossing the first positioning tooth pitch and prevents it from crossing a second positioning tooth pitch; after the annular sealing strip initially contacts the fixed valve seat, the reset guide portion uses the first segment of axial displacement of the independent annular seal relative to the main valve core to cause the stop pawl to exit the stop groove; the annular positioning teeth are provided with N positioning positions along the circumference, and the single-step rotation angle Δθ corresponding to adjacent positioning positions is 360° / N, and Δθ is 1°~10°.

[0015] Preferably, the seating locking assembly includes a first locking structure disposed on the main valve core and a second locking structure disposed on the independent annular seal. The first locking structure and the second locking structure are engaged or rubbed together at the first axial position and separated from each other at the second axial position. At least one of the first locking structure and the second locking structure is provided with an inclined guide surface. After the stop pawl is disengaged from the stop groove by the reset guide, the inclined guide surface generates a circumferential relative displacement smaller than the single-step rotation angle by the continued second axial displacement, so that the annular sealing strip performs micro-wiping relative to the fixed valve seat under a contact load lower than the fully closed load, and after the micro-wiping, the first locking structure and the second locking structure enter the final locking state.

[0016] Preferably, the guide anti-rotation structure includes a guide key, an axial spline, a non-circular cross section, or a limiting pin groove structure disposed between the valve stem guide sleeve and the valve stem.

[0017] Preferably, the main valve core is driven by an electromagnetic, hydraulic, pneumatic, or pilot-operated actuator and biased in the closing direction by a return spring.

[0018] Preferably, the independent annular seal is made of wear-resistant alloy, ceramic matrix composite material, or metal material with a wear-resistant coating on its surface.

[0019] Preferably, a removable filter is provided upstream of the auxiliary gas inlet.

[0020] Preferably, the axial bearing shoulder forms a continuous annular bearing surface, and the independent annular seal forms an annular force-bearing surface corresponding to the continuous annular bearing surface. When fully closed, the axial closing load is transmitted sequentially along the main valve core, the continuous annular bearing surface, the annular force-bearing surface, the annular sealing strip, and the fixed valve seat. The one-way positioning component and the seat locking component are disposed outside the continuous annular bearing surface and have an axial clearance or elastic relief structure to prevent the transmission of the axial closing load from being blocked when the rotation or locking component is stuck.

[0021] A marine dual-fuel engine gas supply system includes a gas fuel supply source, a safety shut-off valve, a gas conditioning and filtering assembly, a common gas rail or a gas main, a gas branch pipe, and the aforementioned gas intake valve; the gas intake valve is installed on the cylinder head or gas installation channel of the engine, its gas inlet is connected to the common gas rail or gas main via the gas branch pipe, and its gas outlet is connected to the engine's intake channel or scavenging channel.

[0022] Preferably, the engine is a marine two-stroke or four-stroke natural gas / liquid fuel dual-fuel engine, and the gas intake valve is used to periodically supply natural gas to the intake passage or scavenging passage in gas fuel operation mode; the safety shut-off valve cuts off the upstream gas fuel when the gas intake valve is stopped or malfunctions.

[0023] Compared with the prior art, the advantages of the gas intake valve with an independent indexing sealing ring described in this invention are: (1) Compared with the technology that rotates the entire valve core, the present invention only rotates the independent low-mass annular seal without changing the circumferential position of the valve stem, armature and actuator, thus reducing the rotational inertia and coupling with the guiding, actuating and detection structures.

[0024] (2) The present invention enables the annular seal to rotate in a low-resistance state and stop circumferential movement in a high-load state through the release and full-seat locking separation and rotation stage and the high-load sealing stage.

[0025] (3) The present invention uses a single-step stop structure that can only be reset after axial state change to mechanically limit the amount of each rotation between adjacent positioning positions, thereby reducing the possibility of continuous rotation or excessive rotation caused by micro-airflow pressure and duration fluctuations.

[0026] (4) By periodically changing the circumferential contact position of the sealing strip, the present invention disperses the impact load caused by manufacturing errors, local thermal deformation and particles among multiple circumferential positions, which is beneficial to reduce repeated indentation and uneven wear in a single area.

[0027] (5) In this invention, low-load micro-wiping, airflow purging and chip removal groove work together to deal with particulate contamination; the contact micro-wiping can be eliminated according to the sealing material and contamination characteristics, and only off-seat rotation and airflow purging are retained to avoid scratches under unsuitable working conditions.

[0028] (6) In this invention, the independent axial bearing path makes the rotation function an additional function rather than a prerequisite for the main shut-off function; when the rotation structure fails, the valve only loses the periodic rotation and corresponding cleaning effect, but does not lose the basic ability to axially cut off the gas.

[0029] (7) In this invention, the auxiliary microchannel only draws out a small portion of gaseous fuel. While maintaining the effective flow capacity of the main channel, it can provide rotation energy for the low-mass independent annular seal by utilizing the local static pressure difference formed by the opening of the main valve and throttling. It can also automatically suppress the auxiliary flow when the main valve is closed and the pressure difference tends to disappear.

[0030] (8) The independent annular seal of the present invention can be used as a replaceable wear part, which facilitates the maintenance of the sealing working surface without replacing the main valve core, valve stem and actuator. Attached Figure Description

[0031] The accompanying drawings, which form part of this invention, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings: Figure 1 This is a schematic cross-sectional view of the gas intake valve of the present invention. Figure 2 This is a partially enlarged schematic diagram of the main valve core, independent annular seal, and fixed valve seat of the present invention; Figure 3 This is a top view and a partial cross-sectional view of the independent annular seal of the present invention; Figure 4 This is a schematic diagram of the micro-rotation airflow drive principle and the relationship between the high and low static pressure regions when the main valve is opened, wherein (a) is a schematic diagram of the airflow drive of the independent annular seal, and (b) is a schematic diagram of the relationship between the high and low static pressure regions when the main valve is opened. Figure 5The diagram shows the preparation, rotation, stopping and reset states of the single-step stop mechanism of the present invention, wherein (a) represents the preparation state of the single-step stop mechanism, (b) represents the rotation state of the single-step stop mechanism, (c) represents the stopping state of the single-step stop mechanism, and (d) represents the reset state of the single-step stop mechanism. Figure 6 This is a schematic diagram of the initial contact, stop release, micro-wiping, final locking, and axial force path when the present invention is repositioned, where (a) represents initial contact, (b) represents stop release, (c) represents micro-wiping, and (d) represents final locking and axial force. Figure 7 This is a schematic diagram showing the installation relationship of the gas intake valve of the present invention in the gas supply system of a marine dual-fuel engine.

[0032] Explanation of reference numerals in the attached drawings: 1-Gas intake valve; 8-Engine; 10-Valve body; 11-Gas inlet; 12-Gas supply chamber; 13-Gas outlet; 14-Fixed valve seat; 20-Main valve core; 21-Valve stem; 22-Valve stem guide sleeve; 23-Guide anti-rotation structure; 24-Reset spring; 25-Actuator assembly; 30-Independent annular seal; 31-Annular mounting part; 32-Annular sealing strip; 33-Chip discharge groove; 34-Axial elastic element; 35-Annular retaining element; 36-Axial floating clearance; 40-Micro-indexing drive flow channel; 41-Auxiliary gas inlet; 42-Tangential... Micro-nozzle; 43-flow receiving part; 50-one-way positioning component; 51-ring positioning tooth; 52-elastic positioning element; 53-single-step stop part; 54-reset guide part; 55-pivot; 56-stop reset spring; 57-stop groove; 61-first locking structure; 62-second locking structure; 63-inclined guide surface; 70-axial bearing shoulder; 80-cylinder head or gas installation channel; 81-gas fuel supply source; 82-safety shut-off valve; 83-gas conditioning and filtering component; 84-gas common rail or gas main; 85-gas branch pipe; 86-intake channel or scavenging channel. Detailed Implementation

[0033] The present invention will now be described in further detail with reference to the accompanying drawings and specific embodiments. It should be understood that the specific embodiments described herein are for illustrative purposes only and are not intended to limit the invention. Furthermore, it should be noted that, for ease of description, only the parts relevant to the invention are shown in the drawings, and not all of them. Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. The terminology used herein is for the purpose of describing specific embodiments only and is not intended to limit the invention.

[0034] The present invention provides a gas intake valve, comprising a valve body 10, a fixed valve seat 14, a main valve core 20 driven by a valve stem 21 and selectively sealingly fitted with the fixed valve seat 14, an independent annular seal 30, a micro-rotation drive structure, a one-way positioning component 50, a seat locking component, and an axial bearing structure. The main valve core 20 is restricted from circumferential rotation relative to the valve body 10 by a guide anti-rotation structure 23, and can reciprocate along its own axis.

[0035] The valve body 10 includes a gas inlet 11, a gas supply chamber 12, and a gas outlet 13. A fixed valve seat 14 is arranged around the gas outlet 13. The main valve core 20 is driven by the actuator 25 and biased in the closing direction by the return spring 24.

[0036] A guide anti-rotation structure 23 is provided between the valve stem 21 and the valve stem guide sleeve 22. This guide anti-rotation structure 23 allows the valve stem 21 and the main valve core 20 to reciprocate at high speed along the axis, while restricting them from undergoing significant circumferential rotation relative to the valve body 10, so that the actuator 25, the valve stem 21 and the main valve core 20 maintain a defined circumferential installation relationship.

[0037] The main valve core 20 is provided with an annular mounting portion 31 on the side facing the fixed valve seat 14. An independent annular seal 30 is provided in the annular mounting portion 31. The independent annular seal 30 has an annular sealing strip 32 for cooperating with the fixed valve seat 14. The annular sealing strip 32 can be a flat surface, a conical surface, or a composite sealing surface that cooperates with each other. Its material and surface treatment are determined according to the gas fuel pressure, opening and closing frequency, temperature, and allowable leakage.

[0038] The annular mounting portion 31 is provided with an annular retainer 35, an axial elastic member 34, and an axial floating gap 36. The independent annular seal 30 is held within the annular mounting portion 31 by the annular retainer 35 and has the freedom to move axially with the main valve core 20, to float slightly axially relative to the main valve core 20, and to rotate circumferentially in the released state. The axial elastic member 34 allows the independent annular seal 30 to float slightly axially relative to the main valve core 20 between a first axial position when fully seated and a second axial position after being unseated; the axial elastic member 34 is a wave spring, disc spring, elastic washer ring, or an axial spring spaced circumferentially.

[0039] The auxiliary gas inlet 41 of the micro-rotation drive channel 40 is connected to the upstream high static pressure region in the gas supply chamber 12. The tangential micro-nozzle 42 opens upstream of the fixed valve seat 14 and adjacent to the local low static pressure region of the opening throttling gap formed after the main valve core 20 is removed from the seat. When the main valve core 20 is removed from the seat, the main gas is accelerated through the opening throttling gap, making the static pressure Ps of the upstream high static pressure region higher than the static pressure Pt of the local low static pressure region, thereby forming a driving pressure difference ΔP=Ps-Pt at both ends of the micro-rotation drive channel.

[0040] Under the driving pressure difference, the micro-rotation drive channel 40 draws out a small amount of gaseous fuel and acts on the flow receiving part 43 of the independent annular seal 30 through the tangential micro-nozzle 42. The flow receiving part 43 can be a micro-blade, a tangential groove, an oblique flow receiving groove, or a flow receiving cavity to convert the gas flow into the circumferential torque of the independent annular seal 30. The auxiliary gas inlet 41 or the micro-rotation drive channel 40 is equipped with a flow limiting orifice, a throttling section, or a filter. The micro-rotation airflow does not undertake the main gas supply function.

[0041] The tangential micro-nozzle 42 and its receiving area are both located on the upstream side of the fixed valve seat. After the auxiliary gas leaves the tangential micro-nozzle 42, it is still discharged into the upstream gas space controlled by the main valve core 20 and the fixed valve seat 14. When the main valve core 20 is completely closed, the flow velocity in the upstream space decreases, Ps and Pt tend to be consistent, the micro-rotation airflow decreases or stops accordingly, and at the same time, the annular sealing strip 32 cuts off the flow path between the upstream gas space and the gas outlet 13. The micro-rotation drive flow channel 40 does not constitute a bypass channel that bypasses the fixed valve seat 14.

[0042] The one-way positioning assembly 50 includes annular positioning teeth 51, elastic positioning element 52, single-step stop part 53, reset guide part 54, pivot 55, stop reset spring 56, and stop groove 57. The single-step stop part 53 may be a swingable stop pawl mounted on the main valve core 20 via pivot 55. The stop reset spring 56 biases the stop pawl toward the stop groove 57 of the annular positioning teeth. The elastic positioning element 52 allows the independent annular seal 30 to cross a positioning tooth pitch in a predetermined direction and restricts reverse retraction.

[0043] After the independent annular seal 30 passes one positioning tooth pitch, the stop pawl enters the stop groove 57 under the action of the stop return spring 56 and remains in a blocking state during this opening, preventing the independent annular seal 30 from passing the second positioning tooth pitch even if the tangential micro-nozzle 42 continues to supply air.

[0044] When the valve is closed again, the annular sealing strip 32 first makes initial contact with the fixed valve seat 14, thereby using contact friction to suppress free circumferential rotation; the first axial relative displacement generated by the main valve core 20 continuing to move in the closing direction causes the reset guide to lift the stop pawl and make it exit the stop groove 57, thus completing the single-step stop release.

[0045] Therefore, the tangential airflow does not rely on precise duration to determine the rotation angle, but only provides the energy required to cross adjacent positioning positions; the final rotation amount is mechanically determined by the positioning tooth pitch and the single-step stop 53, which structurally restricts continuous rotation.

[0046] When N positioning positions are set along the circumference, the rotation angle Δθ for each rotation can be expressed as 360° / N. In implementation, N can be selected according to the width of the sealing strip, the number of chip removal grooves, the allowable contact position repetition cycle, and the rotation resistance. The rotation angle can be 1° to 10°, preferably 2° to 5°.

[0047] The seating locking assembly includes a first locking structure 61 and a second locking structure 62. The two locking structures engage with each other or form frictional compression when the independent annular seal is fully seated to restrict circumferential movement under high closing load conditions; after the main valve core 20 opens and the independent annular seal 30 enters the release position, the two locking structures separate from each other.

[0048] The first locking structure 61 and the second locking structure 62 can employ axial teeth, shallow teeth engagement, conical friction locking, or a combination thereof. At least one of them can be provided with an inclined guide surface 63. After the reset guide 54 releases the single-step stop, the second segment of axial relative displacement generated by the main valve core 20 continuing to move in the closing direction is converted by the inclined guide surface into a circumferential micro-displacement of less than one full rotation angle; after this micro-wiping is completed, the two locking structures finally engage or press against each other.

[0049] Therefore, the reseating stage consists of the following steps: initial contact of the annular sealing strip 32, release of the single-step stop by the first axial relative displacement, optional low-load micro-wiping by the second axial relative displacement, final locking of the seat locking assembly, and establishment of high-load closing force by the axial bearing shoulder. The sequence of these actions is determined by the axial height difference between the reset guide and the inclined guide surface.

[0050] The main valve core 20 is provided with a continuous axial bearing shoulder, and the independent annular seal 30 is provided with a corresponding annular force-bearing surface. When fully closed, the closing load is transmitted along the main valve core, the axial bearing shoulder, the independent annular seal and the fixed valve seat, without passing through the tangential micro-nozzle 42, the flow receiving part 43, the positioning teeth or the single-step stop part.

[0051] The one-way positioning component 50 and the seating locking component are located outside the continuous annular bearing surface and have axial clearance or elastic relief structure. When the positioning component is stuck or the locking teeth are not fully aligned, they do not form a rigid wedge that blocks the axial downward pressure of the main valve core, and the gas intake valve can still be forcibly closed.

[0052] Example 1: Overall Structure of Gas Intake Valve like Figure 1 As shown, the gas intake valve 1 includes a valve body 10, a fixed valve seat 14, a main valve core 20, a valve stem 21, a valve stem guide sleeve 22, a return spring 24, and an actuator assembly 25. The valve body 10 can be mounted to the cylinder head or gas mounting passage 80 of the engine 8 via threads, flanges, or pressure plates.

[0053] The valve body 10 is provided with a gas inlet 11, and a gas supply chamber 12 is formed inside, surrounding the main valve core 20. The gas outlet 13 is located downstream of the fixed valve seat 14 and is connected to the air intake passage or the scavenging passage 86. When the main valve core 20 leaves the fixed valve seat 14, the gas flows from the gas supply chamber 12 through the opening gap to the gas outlet 13.

[0054] The actuator 25 can be electromagnetic, hydraulic, pneumatic, or pilot-operated. The actuator 25 applies an opening force to the valve stem 21, and the return spring 24 applies a closing bias force to the main valve core 20 when the driving force is removed or when the system is safely stopped.

[0055] The valve stem guide sleeve 22 and the valve stem 21 form an axial sliding fit. The guide anti-rotation structure 23 can be a guide key with an axial keyway, an axial spline, a flat round cross section, a D-shaped cross section, or a limit pin with an axial long groove. The fit retains the clearance required for high-speed axial movement, but inhibits the circumferential rotation of the main valve core 20.

[0056] The main valve core 20 can be a disc valve core, an annular valve core, or a lift valve core with a pressure balancing structure. The main body of the main valve core 20 is fixedly connected to the valve stem 21, while the independent annular seal 30 is assembled at its closed end as a separate part from the main valve core 20.

[0057] In one example, the opening stroke of the main valve core 20 is 0.3–3 mm, the specific value of which is determined based on the gas supply pressure and target flow rate. This invention does not rely on this value; the key is that the main valve core 20 performs axial opening and closing while the independent annular seal 30 performs limited circumferential rotation.

[0058] Example 2: Independent annular seal and axial floating installation: like Figure 2 and Figure 3 As shown, the closing end of the main valve core 20 forms an annular mounting portion 31 that opens toward the fixed valve seat 14. An independent annular seal 30 is disposed within the annular mounting portion 31, and its outer diameter and inner diameter form a controllable radial clearance with the annular mounting portion 31, respectively.

[0059] The annular retainer 35 is fixed to the main valve core 20 and axially retains the independent annular seal 30. The annular retainer 35 can be a threaded retaining ring, a split retaining ring, or a pressure ring connected by fasteners; after removing the annular retainer 35, the independent annular seal 30 can be replaced separately.

[0060] An axial elastic element 34 is provided between the independent annular seal 30 and the axial bearing shoulder 70. When fully closed, the independent annular seal 30 is blocked by the fixed valve seat 14, and the main valve core 20 continues to move in the closing direction and compress the axial elastic element 34 until the axial bearing shoulder 70 transmits the main closing load to the independent annular seal 30.

[0061] When the main valve core 20 begins to open, the axial elastic element 34 first releases its stored energy, causing the independent annular seal 30 to move slightly relative to the main valve core 20 toward the fixed valve seat 14. The seat locking assembly changes from an engaged state to a disengaged state. Subsequently, the annular retainer 35 drives the independent annular seal 30 to move away from the fixed valve seat 14 as a whole. When fully closed, the main valve core 20 moves relative to the independent annular seal 30 in the closing direction and compresses the axial elastic element 34.

[0062] In one example, the axial floating clearance 36 is 0.02–0.30 mm, preferably 0.05–0.15 mm. This clearance is greater than the axial displacement required for the seat locking structure to disengage, and less than the effective opening stroke of the main valve core 20.

[0063] The axial elastic element 34 can be a continuous wave spring, disc spring, elastic washer, or multiple small compression springs. Its preload is only required to ensure the transition between the release and locking states and does not replace the main closing force applied by the return spring 24.

[0064] The annular sealing strip 32 can be disposed on the lower end face of the independent annular seal 30. Chip removal grooves 33 are disposed on the radially inner side, radially outer side, or both sides of the annular sealing strip 32, and can be inclined radially or in a predetermined rotation direction; such as... Figure 3 As shown, the chip removal groove 33 terminates outside the effective continuous sealing area, or only extends partially into it without penetrating the entire radial width of the area, thus preserving a continuous annular sealing barrier. The tangential micro-nozzle 42 can also cover the sealing strip or the area adjacent to the chip removal groove 33, thereby creating a synergistic cleaning process of off-seat airflow purging, single-step rotation, initial low-load micro-wiping upon closure, and particle removal.

[0065] The independent annular seal 30 can be made of wear-resistant stainless steel, nickel-based alloy, cobalt-based alloy or ceramic matrix composite material; the annular sealing strip 32 can be made of nitriding, carbide coating, diamond-like coating or other surface strengthening methods suitable for gas fuel valves.

[0066] Example 3: Single-step micro-rotation driven by natural gas flow: like Figure 4 As shown, the auxiliary gas inlet 41 of the micro-rotation drive channel 40 is connected to the upstream high static pressure region in the gas supply chamber 12, and one or more tangential micro-nozzles 42 are formed at the end of the channel. The axis of the tangential micro-nozzle 42 is inclined relative to the radial direction of the independent annular seal 30, and opens on the upstream side of the fixed valve seat 14 and adjacent to the opening throttling gap formed after the main valve core 20 is dismounted.

[0067] Figure 4(b) shows the main valve core 20 in the open state. The main gas flows from the gas supply chamber 12 to the gas outlet 13 and is accelerated at the opening throttling gap, forming a local low static pressure region with a static pressure of Pt in the area where the tangential micro-nozzle 42 is located; the upstream region of the gas supply chamber 12 where the auxiliary gas inlet 41 is located maintains a relatively high static pressure Ps, thereby satisfying Ps>Pt, and forming a driving pressure difference of ΔP=Ps-Pt at both ends of the micro-rotation drive channel 40.

[0068] Under the driving pressure difference, the auxiliary gas flows in the direction of Ps → auxiliary gas inlet 41 → micro-rotation drive channel 40 → tangential micro-nozzle 42 → Pt. The flow receiving part 43 is arranged circumferentially around the independent annular seal 30. The jet generated by the tangential micro-nozzle 42 acts on the flow receiving part 43 to form a circumferential driving torque. The working radius of the flow receiving part 43 is preferably close to the outer periphery of the independent annular seal 30.

[0069] When the main valve core 20 is fully closed, the opening throttling gap disappears, the flow velocity in the upstream space decreases, Ps and Pt tend to be consistent, and the micro-rotation drive flow rate decreases accordingly until it can no longer push the independent annular seal 30 over the teeth, or stops. The tangential micro-nozzle 42 and the flow receiving part 43 are always located upstream of the fixed valve seat 14, and the gas outlet 13 is located downstream of the fixed valve seat 14. Therefore, there is no downstream opening at the outlet end of the micro-rotation drive flow channel 40 that is directly connected to the gas outlet 13.

[0070] The approximate driving torque generated by the micro-rotation airflow can be expressed as Tg= a·vt·rm estimation, where 'a' represents the auxiliary gas mass flow rate, 'vt' represents the tangential velocity component of the jet, and 'rm' represents the average radius from the jet's point of application to the axis. In the released state, Tg should be greater than the sum of the frictional torque generated by the residual clamping of the axial elastic element 34 and the over-tooth resistance torque of the elastic positioning element 52. The dimensions of the auxiliary gas inlet 41, the flow-limiting orifice, the tangential micro-nozzle 42, and the flow-receiving section 43 are calculated, simulated, or experimentally calibrated based on the available Ps-Pt, gas density, and the aforementioned resistance torque.

[0071] After the independent annular seal 30 rotates through one tooth pitch, the single-step stop 53 enters the blocking position. The circumferential blocking torque that the stop structure can withstand is greater than the torque generated by the tangential micro-nozzle 42 under the maximum design driving pressure difference. Therefore, even if the micro-airflow continues, the sealing ring cannot continue to rotate through a second tooth pitch. In one example, the total effective flow area of ​​the tangential micro-nozzle 42 is 0.05% to 1.0% of the main flow area of ​​the gas intake valve; the annular positioning teeth 51 are set with 72 or 90 positioning positions, corresponding to Δθ of 5° or 4° respectively. The actual values ​​are determined based on the gas supply pressure, sealing ring diameter, and friction resistance test.

[0072] like Figure 5As shown, the elastic positioning member 52 forms an inclined surface that allows forward tooth crossing and a steep surface that restricts reverse retraction. The single-step stop 53 adopts a swingable stop pawl mounted on the main valve core 20 via a pivot 55, and the stop return spring 56 applies a biasing force to the stop pawl toward the annular positioning tooth 51.

[0073] Figure 5 (a) indicates the ready state, where the stop pawl does not obstruct the first tooth pitch; Figure 5 (b) indicates that the annular positioning tooth 51 moves relative to the airflow torque and lifts the stop pawl; Figure 5 (c) indicates that after completing one tooth pitch, the stop pawl enters the stop groove 57 under the action of the stop return spring 56 and prevents the second tooth pitch; Figure 5 (d) indicates that during the repositioning process, the reset guide 54 uses the first segment of axial relative displacement s1 to lift the stop claw.

[0074] The reset guide 54 can be an axial boss, a beveled cam, or a guide ring that moves axially synchronously with the independent annular seal 30. The contact height between the reset guide 54 and the stop pawl is set such that the stop pawl only exits the stop groove 57 after the annular sealing strip 32 has initially contacted the fixed valve seat 14 and the independent annular seal 30 has undergone the first stage of axial relative displacement relative to the main valve core 20.

[0075] Example 4: Unlocking upon leaving the seat and locking upon sitting down: like Figure 2 and Figure 6 As shown, in the fully closed state, the annular sealing strip 32 is pressed against the fixed valve seat 14, and the first locking structure 61 and the second locking structure 62 are engaged or rubbed together, preventing the independent annular seal 30 from rotating circumferentially under high closing load.

[0076] When the actuator 25 moves the main valve core 20 in the opening direction, the axial elastic element 34 pushes the independent annular seal 30 into the release position relative to the main valve core 20, and the first locking structure 61 separates from the second locking structure 62; the annular retainer 35 then carries the independent annular seal 30 away from the fixed valve seat 14.

[0077] In the unseated state, the tangential micro-nozzle 42 acts on the flow receiving part 43, and the independent annular seal 30 rotates from the current positioning position to the adjacent positioning position. After reaching the adjacent positioning position, the single-step stop part 53 enters the stop groove 57, and the rotation stops.

[0078] like Figure 6 As shown in (a), when the main valve core 20 closes again, the annular sealing strip 32 first contacts the fixed valve seat 14. At this time, the single-step stop part 53 is still in the stop state, and the return spring 24 has not yet applied the full closing load to the sealing pair.

[0079] like Figure 6 As shown in (b), the main valve core 20 continues to move in the closing direction and compresses the axial elastic element 34, causing the independent annular seal 30 to undergo a first axial relative displacement s1 relative to the main valve core 20; the reset guide 54 first lifts the single-step stop 53, causing it to exit the stop groove 57. Since the annular sealing strip 32 has already contacted the fixed valve seat 14, releasing the stop will not allow the independent annular seal 30 to resume free and continuous rotation.

[0080] like Figure 6 As shown in (c), after the stop is released, the main valve core 20 continues to undergo a second axial relative displacement s2. The inclined guide surface 63 of the first locking structure 61 and the second locking structure 62 begins to cooperate, converting the second axial relative displacement into a circumferential micro-displacement δθ less than one tooth pitch, so that the annular sealing strip 32 completes short-distance micro-wiping under a contact load lower than the fully closed load.

[0081] like Figure 6 As shown in (d), after the micro-wiping is completed, the first locking structure 61 and the second locking structure 62 enter the final engagement or friction pressing state; after the main valve core 20 reaches the fully closed position, the inclined guide surface 63 no longer produces circumferential displacement, and the axial bearing shoulder 70 applies a high closing load to the independent annular seal 30 along the continuous axial bearing path.

[0082] To prevent the locking teeth from interfering with closure, the shallow teeth in the first locking structure 61 can be configured as an elastic, retractable structure, or a conical friction lock that does not require angular alignment can be used. Regardless of the structure used, the continuous axial bearing surface can pass over or bypass the locking structure to transmit the closing load.

[0083] Therefore, this embodiment forms a cycle of "fully seated locking - seated release - airflow driving one step - single-step stop - initial contact of the sealing strip - first stage axial displacement to release the stop - second stage axial displacement low-load micro-wiping - final locking and establishing high-load closing force".

[0084] Example 5: Lightweight micro-wiping and self-cleaning with chip removal: like Figures 3 to 6 As shown, the independent annular seal 30 changes its circumferential positioning position each time it is opened and closed, causing the relative positions of the local microscopic high point, the chip discharge groove 33 and the fixed valve seat 14 to change periodically.

[0085] When particles adhere to the edge of the annular sealing strip 32, the auxiliary airflow after disengagement first blows the area adjacent to the sealing strip; during the rotation process, the flow receiving part 43 and the chip discharge groove 33 change the flow direction near the particles; the micro-wiping at the initial stage of re-seating pushes the loosened particles into the chip discharge groove 33.

[0086] The chip removal groove 33 does not penetrate the entire radial width that forms the main sealing barrier in the fully closed state, or maintains sufficient leakage resistance through a labyrinthine bend to avoid the chip removal structure forming a direct leakage channel.

[0087] The micro-wiping angle is smaller than the single-step rotation angle and occurs during the initial contact of the annular seal strip 32 but before the axial bearing shoulder 70 has applied its full load. The angle of the inclined guide surface 63 and the positioning gap are used to limit the micro-wiping distance.

[0088] If the sealing material is sensitive to contact sliding, the circumferential guiding effect of the inclined guide surface 63 can be eliminated, so that the first locking structure 61 and the second locking structure 62 only perform axial compression; at this time, the single-step rotation of the seat, airflow purging and chip removal groove are still retained.

[0089] By comparing the amount of seal leakage, the surface roughness of the sealing strip, and the particle residue rate, the implementation method can be selected with or without micro-wiping.

[0090] Example 6: Fail-safe axial closure structure: like Figure 2 and Figure 6 As shown in (d), the continuous axial bearing path consists of the main valve core 20, the axial bearing shoulder 70, the independent annular seal 30, and the fixed valve seat 14. This path is arranged axially and does not pass through the micro-rotation drive flow channel 40, the flow receiving part 43, the annular positioning tooth 51, the single-step stop part 53, or the seat locking assembly.

[0091] When the tangential micro-nozzle 42 is blocked by particles, the independent annular seal 30 may remain in its current position; the return spring 24 can still drive the main valve core 20 to move in the closing direction, and the axial bearing shoulder 70 can still press the independent annular seal 30 against the fixed valve seat 14.

[0092] When the elastic positioning element 52 or the single-step stop 53 is circumferentially stuck, the sticking restricts the circumferential rotation of the independent annular seal 30. The area where the positioning assembly is located has an axial clearance clearance, so it does not prevent the independent annular seal 30 from axially settling within the annular mounting portion 31.

[0093] When the locking teeth are not aligned, the elastic relief structure allows the teeth to retract axially, or the conical friction locking structure directly forms a pressing contact. The continuous axial bearing surface still establishes the main closing force, avoiding making the precise engagement of the locking teeth a necessary condition for valve closure.

[0094] After the rotation function fails, the gas intake valve 1 can continue to function as a non-rotating ordinary axial opening and closing valve to complete the gas cut-off; during subsequent maintenance, the microchannel, positioning component or independent annular seal 30 can be replaced or cleaned.

[0095] With the above structure, what is lost upon failure is the additional effect of uniform wear, self-cleaning, or periodic rotation, rather than the basic closing function of the gas intake valve 1.

[0096] Example 7: Application of marine dual-fuel engines: like Figure 7 As shown, this embodiment provides a marine dual-fuel engine gas supply system employing the aforementioned gas intake valve 1. The system includes a gas fuel supply source 81, a safety shut-off valve 82, a gas conditioning and filtering assembly 83, a common gas rail or gas main 84, a gas branch pipe 85, and at least one gas intake valve 1 installed on the engine 8.

[0097] The gas fuel supply source 81, safety shut-off valve 82, gas conditioning and filtration assembly 83, common gas rail or main gas pipe 84, gas branch pipe 85, and gas inlet 11 are connected sequentially along the gas flow direction. The gas conditioning and filtration assembly 83 may include a pressure regulator, a pressure stabilizer, a temperature regulator, and a particulate filter.

[0098] The gas intake valve 1 is installed in the cylinder head or gas installation passage 80, and its gas outlet 13 is connected to the intake passage or scavenging passage 86. For a two-stroke low-speed dual-fuel engine, the gas intake valve 1 can be arranged in the branch from the scavenging receiver to the cylinder scavenging passage; for a four-stroke engine, it can be arranged in the intake branch pipe of each cylinder.

[0099] Safety shut-off valve 82 is used to cut off upstream gas when the engine stops, gas mode is discontinued, or gas supply is abnormal. The return spring 24 of the gas intake valve 1 itself and the independent axial force-bearing path constitute the end-cut-off structure near the engine intake passage.

[0100] When the engine is running, the actuator 25 opens and closes the main valve core 20 according to a predetermined gas supply sequence. After each opening, the independent annular seal 30 completes a limited rotation under the action of the gas supply pressure difference; during the operation phase where rotation is not required, rotation can be suppressed by closing the auxiliary gas inlet 41 or by using a bypass sleeve that is not aligned with the flow receiving part 43.

[0101] The gas conditioning and filtration component 83 uses the same filter for both the main gas and the micro-rotation airflow. Alternatively, a secondary micro-filter can be installed at the auxiliary gas inlet 41 to reduce the probability of clogging of the tangential micro-nozzle 42.

[0102] During maintenance, the annular retainer 35 can be removed to inspect the annular sealing strip 32, chip removal groove 33, annular positioning teeth 51, and flow receiving part 43; the main valve core 20, valve stem 21, and actuator 25 do not need to be replaced as a whole due to local wear of the sealing strip.

[0103] Example 8: An alternative to contactless micro-wiping: In this alternative embodiment, the first locking structure 61 and the second locking structure 62 adopt an axially pressed conical friction pair or a locking surface without circumferential guiding function, and do not provide an inclined guide surface 63 for generating circumferential micro-displacement.

[0104] The independent annular seal 30 is still driven to the adjacent positioning position by the tangential micro-nozzle 42 in the off-seat state and is held by the single-step stop 53; when closed again, the annular seal 32 sits vertically in the new circumferential position without being intentionally wiped relative to the fixed valve seat 14.

[0105] This alternative embodiment achieves cleaning and uniform wear through off-seat airflow, chip removal groove 33, and periodic changes in contact position. It is suitable for hard and brittle coatings, low lubrication conditions, or sealing pairs that have been shown by tests to be unfavorable for contact wiping.

[0106] Without departing from the core concept of this invention, the micro-rotation drive structure can also use a micro piston or diaphragm driven by the gas pressure difference, converting its one-time reciprocating displacement into one circumferential step of the independent annular seal 30; as long as the main valve core 20 remains circumferentially restricted, the independent annular seal 30 has limited rotation in the off-seat state, locks after being fully seated, and the main closing load has an independent axial path, it can all fall within the concept of this invention.

[0107] In this manual, "axial" refers to the direction parallel to the main opening and closing direction of the main valve core 20; "circumferential" refers to the direction around the axis; and "indexing" refers to the limited angular change of the independent annular seal 30 between adjacent predetermined positioning positions, rather than free and continuous rotation.

[0108] In this manual, "fully seated" means that the annular sealing strip 32 and the fixed valve seat 14 form a compressed state that meets the predetermined cut-off requirements; "released state" means that the annular sealing strip 32 has been released from high-load compression and the seated locking assembly allows the independent annular seal 30 to rotate circumferentially; "initial contact" means that the annular sealing strip 32 has contacted the fixed valve seat 14 but the axial bearing shoulder 70 has not yet established a full closing load.

[0109] In each embodiment, the fuel gas can be natural gas, methane fuel gas, or other gaseous fuels suitable for the engine. For low-pressure intake supply and higher-pressure supply, the flow area, the radius of the flow receiving part 43, and the positioning resistance of the micro-rotation drive flow channel 40 can be calibrated separately.

[0110] The embodiments of the present invention disclosed above are merely illustrative of the invention. These embodiments do not exhaustively describe all details, nor do they limit the invention to the specific implementations described. Many modifications and variations can be made based on the content of this specification. This specification selects and specifically describes these embodiments to better explain the principles and practical applications of the invention, thereby enabling those skilled in the art to better understand and utilize the invention.

Claims

1. A gas intake valve with an independent indexing sealing ring, characterized in that: The valve body includes a valve body (10), a fixed valve seat (14), a main valve core (20) driven by a valve stem (21) and selectively sealing with the fixed valve seat (14), an independent annular seal (30), a micro-rotation drive structure, a one-way positioning assembly (50), a seat locking assembly, and an axial bearing structure. The main valve core (20) is restricted from circumferential rotation relative to the valve body (10) by a guide anti-rotation structure (23) and can reciprocate along its own axis. An independent annular seal (30) is provided on the side of the main valve core (20) facing the fixed valve seat (14). The independent annular seal (30) moves axially with the main valve core (20) and can be rotated in a limited circumferential direction relative to the main valve core (20) in the rotated state separated from the fixed valve seat (14). The micro-rotation drive structure is used to apply circumferential driving force to the independent annular seal (30) in the rotated state; the one-way positioning component (50) is used to allow the independent annular seal (30) to rotate from the current positioning position to the adjacent positioning position and to maintain a single-step stop state after reaching the adjacent positioning position; the seating locking component is used to restrict the circumferential movement of the independent annular seal (30) when fully seated. The axial bearing structure includes an axial bearing shoulder (70) disposed on the main valve core (20). The axial bearing shoulder (70) can transmit axial closing load to the independent annular seal (30) without relying on the action of the micro-rotation drive structure, the one-way positioning component (50) and the seat locking component, so that when the rotation, stop or locking action cannot be completed, the independent annular seal (30) can still be pressed against the fixed valve seat (14).

2. The gas intake valve with an independent indexing sealing ring according to claim 1, characterized in that: The main valve core (20) has an annular mounting portion (31) on the side facing the fixed valve seat (14). An independent annular seal (30) is provided in the annular mounting portion (31). The independent annular seal (30) has an annular sealing strip (32) for cooperating with the fixed valve seat (14). The annular mounting portion (31) is provided with an annular retainer (35), an axial elastic member (34) and an axial floating gap (36). The annular retainer (35) restricts the independent annular seal (30) from disengaging from the main valve core (20). The axial elastic member (34) allows the independent annular seal (30) to axially float slightly relative to the main valve core (20) between a first axial position when fully seated and a second axial position after disengagement.

3. The gas intake valve with an independent indexing sealing ring according to claim 2, characterized in that: The micro-rotation drive structure includes a micro-rotation drive channel (40), an auxiliary gas inlet (41) communicating with the upstream high static pressure region of the gas supply chamber (12), and a tangential micro-nozzle (42) facing the independent annular seal (30); the tangential micro-nozzle (42) opens on the upstream side of the fixed valve seat (14) and is adjacent to the local low static pressure region of the opening throttling gap formed after the main valve core (20) is removed from the seat; the tangential micro-nozzle (42) generates a velocity component along the circumference of the independent annular seal (30) by the auxiliary gas driven by the driving pressure difference; When the main valve core (20) is off the seat, the main gas is accelerated through the opening throttling gap, making the static pressure Ps of the upstream high static pressure region higher than the static pressure Pt of the local low static pressure region, and forming a driving pressure difference at both ends of the micro-rotation drive channel (40); when the main valve core (20) is completely closed, the static pressure of the upstream high static pressure region and the local low static pressure region tend to be consistent, and the micro-rotation drive channel (40) cannot bypass the fixed valve seat (14) and directly connect to the gas outlet (13).

4. The gas intake valve with an independent indexing sealing ring according to claim 3, characterized in that: The independent annular seal (30) is provided with flow receiving parts (43) arranged at intervals along the circumference. The micro-rotation drive channel (40) draws out a small amount of gaseous fuel under the action of the driving pressure difference and acts on the flow receiving parts (43) of the independent annular seal (30) through the tangential micro-nozzle (42). The flow receiving parts (43) are at least one of micro flow receiving blades, tangential grooves, oblique flow receiving grooves and flow receiving cavities.

5. The gas intake valve with an independent indexing sealing ring according to claim 3, characterized in that: Chip removal grooves (33) are provided on the radial inner side, radial outer side, or both sides of the annular sealing strip (32), and the chip removal grooves (33) extend radially or inclined relative to the radial direction; the chip removal grooves (33) are located outside the effective continuous sealing area of ​​the annular sealing strip (32), or terminate within the effective continuous sealing area without penetrating its entire radial width; the jet of at least one of the tangential micro-nozzles (42) covers the adjacent area of ​​the annular sealing strip (32) or the chip removal grooves (33).

6. The gas intake valve with an independent indexing sealing ring according to claim 2, characterized in that: The one-way positioning assembly (50) includes an annular positioning tooth (51) disposed on the independent annular seal (30), an elastic positioning member (52) disposed on the main valve core (20), a single-step stop (53), a reset guide (54), a pivot (55), a stop reset spring (56), and a stop groove (57); the single-step stop (53) is a stop pawl that is pivotally mounted on the main valve core (20) via the pivot (55), and is biased by the stop reset spring (56) in a direction that engages with the stop groove (57) of the annular positioning tooth (51); The elastic positioning element (52) allows the independent annular seal (30) to pass through a positioning tooth pitch in a predetermined direction. After passing through the first positioning tooth pitch, the stop pawl enters the stop groove (57) and prevents it from passing through the second positioning tooth pitch. After the annular sealing strip (32) initially contacts the fixed valve seat (14), the reset guide (54) uses the first axial displacement of the independent annular seal (30) relative to the main valve core (20) to make the stop pawl exit the stop groove (57). The annular positioning teeth (51) are provided with N positioning positions along the circumference.

7. The gas intake valve with an independent indexing sealing ring according to claim 2, characterized in that: The seating locking assembly includes a first locking structure (61) disposed on the main valve core (20) and a second locking structure (62) disposed on the independent annular seal (30). The first locking structure (61) and the second locking structure (62) are engaged or rubbed together at the first axial position and separated from each other at the second axial position.

8. The gas intake valve with an independent indexing sealing ring according to any one of claims 2-7, characterized in that: The axial bearing shoulder (70) forms a continuous annular bearing surface, and the independent annular seal (30) forms an annular force-bearing surface corresponding to the continuous annular bearing surface. When fully closed, the axial closing load is transmitted sequentially along the main valve core (20), the continuous annular bearing surface, the annular force-bearing surface, the annular sealing strip (32), and the fixed valve seat (14). The one-way positioning component (50) and the seat locking component are located outside the continuous annular bearing surface and have axial clearance or elastic relief structure.

9. A marine dual-fuel engine gas supply system, characterized in that: It includes a gas fuel supply source (81), a safety shut-off valve (82), a gas conditioning and filtering assembly (83), a common gas rail or a gas main (84), a gas branch pipe (85), and at least one gas intake valve (1) as described in any one of claims 1 to 8; the gas intake valve (1) is installed on the cylinder head or gas installation channel (80) of the engine (8), its gas inlet (11) is connected to the common gas rail or the gas main (84) via the gas branch pipe (85), and its gas outlet (13) is connected to the intake channel or scavenging channel (86) of the engine (8).

10. The marine dual-fuel engine gas supply system according to claim 9, characterized in that: The engine (8) is a marine two-stroke or four-stroke natural gas / liquid fuel dual-fuel engine. The gas intake valve (1) is used to periodically supply natural gas to the intake passage or scavenging passage (86) in the gas fuel operation mode. The safety shut-off valve (82) cuts off the upstream gas fuel when the gas intake valve (1) is stopped or malfunctions.

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