Fuel gas injection valve for high-pressure-difference gas engine

Abstract

A gas injection valve for a high-pressure difference gas engine, comprising an electromagnetic valve (1), an armature (2), a limiting ring (3), a limiting disc (4), a valve shell (5), a valve plate (6

Description

TECHNICAL FIELD

[0001] The present disclosure relates to the technical field of gas engine components, in particular to a fuel gas injection valve for a high-pressure-difference gas engine. BACKGROUND

[0002] At present, gas engines are popular for domestic and foreign markets with lower pollution emissions, better fuel economy and higher cost performance. The fuel gas injection valve is one of the core components of a fuel injection system, so the independent research and development of gas injection valve is of great importance.

[0003] The patent CN106121867A discloses a fuel gas electric injection valve for a gas fuel engine. The fuel gas electric injection valve for a gas fuel engine includes a shell, an electromagnetic valve part and a valve core part. The valve core includes a valve core, a valve plate, a valve seat and an armature. The valve plate is installed in the valve core, and the valve plate is fixedly connected with the lower end of the armature. When the electromagnetic valve part is powered on, the armature pulls the valve plate to move upwards under the action of electromagnetic force, so that a fuel gas channel is formed between the lower surface of the valve plate and the upper surface of the valve seat. When the electromagnetic valve part is powered off, the lower surface of the valve plate is laminated with the upper surface of the valve seat to form a sealing surface, so that the fuel gas channel is blocked. The fuel gas electric injection valve can be applied to medium and high-speed gas engines and dual-fuel engines, but is not suitable for high-pressure-difference gas engines in an annular flow channel mode because of the problem of insufficient electromagnetic force in the high-pressure-difference environment to result in that the valve plate fails to open smoothly in the high-pressure-difference fuel gas environment. SUMMARY

[0004] The purpose of the present disclosure is to provide a fuel gas injection valve for a high-pressure-difference gas engine so as to solve the problems in the prior art, so that the valve plate is opened smoothly in the high-pressure-difference gas environment, and then the engine performance is optimized, and the response speed is increased.

[0005] In order to achieve the above-mentioned purpose, the present disclosure provides the following scheme.

[0006] Provided is a fuel gas injection valve for a high-pressure-difference gas engine in the embodiment. The fuel gas injection valve for a high-pressure-difference gas engine includes an electromagnetic valve, an armature, a limiting ring, a travel limiting disc, a valve housing, a valve plate, a valve seat and a reset spring. A stepped through hole is formed in the center of the valve housing in a penetrating mode, and a gas outlet is formed in the lower end of the valve housing. A waist-shaped gas inlet is formed in the side wall of the valve housing. The valve seat, the valve plate, the travel limiting disc and the limiting ring are sequentially installed in the stepped through hole from bottom to top. A stepped hole is formed in the center of the travel limiting disc. The electromagnetic valve is fixedly installed on the valve housing. The armature is located below the electromagnetic valve. The upper part of the armature is located in the central hole of the limiting ring, and the lower part of the armature is located in the stepped hole of the travel limiting disc. The valve plate is fixedly connected to the lower end of the armature and gets close to the waistshaped gas inlet. The reset spring sleeves the lower part of the armature. The upper end of the reset spring abuts against the end face of the stepped hole of the travel limiting disc, and the lower end of the reset spring abuts against the upper end face of the valve plate. The travel limiting disc can limit the up-shift travel of the valve plate. The lower end face of the valve plate is matched with the upper end face of the valve seat. A first gas guide circular groove, a first inner annular groove and a first outer annular groove are formed in the lower end face of the valve plate at intervals from inside to outside. The first gas guide circular groove is formed in the center of the lower end face of the valve plate. The first outer annular groove is formed in the edge of the lower end face of the valve plate. A plurality of first radial through grooves are uniformly formed in the lower end face of the valve plate along the circumferential direction. The first radial through grooves communicate with the first gas guide circular groove, the first inner annular groove and the first outer annular groove in a penetrating mode to form a fuel gas flow channel and a plurality of discrete protruding valve plate sealing blocks separated by the flow channel. The plurality of discrete sealing blocks define a reduced sealing contact area with the valve seat operable to reduce a force required to separate the valve plate from the valve seat under high pressure difference conditions. The upper end face of the valve seat is a plane. A plurality of valve seat spray holes which are in one-to-one correspondence with the valve plate sealing blocks and communicate with the gas outlet are formed in the valve seat. When the electromagnetic valve is energized, the armature drives the valve plate to move upwards, the valve plate is lifted, and the fuel gas injection valve is opened. When the electromagnetic valve is powered off, the armature drives the valve plate to quickly take a seat under the elastic force of the reset spring, and the fuel gas injection valve is closed.

[0007] A plurality of first radial connecting grooves are uniformly formed between the first inner annular groove and the first outer annular groove.

[0008] Preferably, the edge of the upper end of the valve seat is uniformly provided with a plurality of cylindrical pins along the circumferential direction, and a plurality of semi-cylindrical pin hole grooves which are matched with the cylindrical pins in a one-to-one correspondence mode are formed in the side wall of the valve plate.

[0009] Preferably, the number of the first radial through grooves is six, the number of the first radial connecting grooves is also six, the numbers of the valve plate sealing blocks and valve seat spray holes are both eighteen, and the numbers of the cylindrical pins and the semi-cylindrical pin hole grooves are both three.

[0010] Provided is another fuel gas injection valve for a high-pressure-difference gas engine. The fuel gas injection valve for a high-pressure-difference gas engine includes an electromagnetic valve, an armature, a limiting ring, a travel limiting disc, a valve housing, a valve plate, a valve seat and a reset spring. A stepped through hole is formed in the center of the valve housing in a penetrating mode, and a gas outlet is formed in the lower end of the valve housing. A waist-shaped gas inlet is formed in the side wall of the valve housing. The valve seat, the valve plate, the travel limiting disc and the limiting ring are sequentially installed in the stepped through hole from bottom to top. A stepped hole is formed in the center of the travel limiting disc. The electromagnetic valve is fixedly installed on the valve housing. The armature is located below the electromagnetic valve. The upper part of the armature is located in the central hole of the limiting ring, and the lower part of the armature is located in the stepped hole of the travel limiting disc. The valve plate is fixedly connected to the lower end of the armature and gets close to the waistshaped gas inlet. The reset spring sleeves the lower part of the armature. The upper end of the reset spring abuts against the end face of the stepped hole of the travel limiting disc, and the lower end of the reset spring abuts against the upper end face of the valve plate. The travel limiting disc can limit the up-shift travel of the valve plate. The lower end face of the valve plate is matched with the upper end face of the valve seat. The lower end face of the valve plate is a plane. A second gas guide circular groove, a second inner annular groove and a second outer annular groove are formed in the upper end face of the valve seat at intervals from inside to outside. The second gas guide circular groove is formed in the center of the upper end face of the valve seat. A plurality of second radial through grooves are uniformly formed in the upper end face of the valve seat along the circumferential direction. The second radial through grooves communicate with the second gas guide circular groove, the second inner annular groove and the second outer annular groove in a penetrating mode to form a fuel gas flow channel and a plurality of discrete protruding valve seat sealing blocks separated by the flow channel wherein the sealing blocks define a reduced sealing contact area with the valve plate operable to reduce a force required to separate the valve plate from the valve seat under high pressure difference conditions. One valve seat spray hole which communicates with the gas outlet is formed in each valve seat sealing block. When the electromagnetic valve is energized, the armature drives the valve plate to move upwards, the valve plate is lifted, and the fuel gas injection valve is opened. When the electromagnetic valve is powered off, the armature drives the valve plate to quickly take a seat under the elastic force of the reset spring, and the fuel gas injection valve is closed.

[0011] A plurality of second radial connecting grooves are uniformly formed between the second inner annular groove and the second outer annular groove.

[0012] Preferably, the number of the second radial through grooves is six, the number of the second radial connecting grooves is also six, and the numbers of the valve seat sealing blocks and valve seat spray holes are both eighteen.

[0013] Preferably, an annular spring assembly groove is formed in the upper end face of the valve plate, and the lower end of the reset spring is located in the spring assembly groove and abuts against the bottom surface of the spring assembly groove.

[0014] Compared with the prior art, the present disclosure has the following beneficial technical effects.

[0015] Firstly, the fuel gas flow channel or the fuel gas flow channel are used, so that gas is replenished more timely and effectively, and the gas inlet throttling effect is reduced to the minimum. Meanwhile, the sealing area of the valve seat and the valve plate can be reduced, the sealing specific pressure is increased, the sealing specific pressure is positively correlated with the working environment pressure, the problem that the electromagnetic force of the electromagnetic valve is insufficient in the high-pressure-difference environment is solved, the valve plate can be smoothly opened in the high-pressure-difference gas environment, then the engine performance is optimized, and the response speed is increased.

[0016] Secondly, the arrangement of the valve seat spray holes in the valve seat is similar to a honeycomb, so that the sprayed fuel gas can be mixed with air more thoroughly, and the uniformity of fuel gas can be improved.

[0017] Thirdly, a plurality of first radial connecting grooves or a plurality of second radial connecting grooves are formed, so that the sealing area between the valve plate and the valve seat is further reduced, and the timeliness of replenishing gas is further improved.

[0018] Fourthly, the cylindrical pins and the semi-cylindrical pin hole grooves are cooperatively used to guide the valve plate, and the clamping stagnation problem caused by the traditional cooperative guide of shafts and holes, so that the reliability of the fuel gas injection valve is improved. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] To more clearly illustrate the embodiment of the present disclosure or the technical scheme in the prior art, the following briefly introduces the attached figures to be used in the embodiment. Apparently, the attached figures in the following description show merely some embodiments of the present disclosure, and those skilled in the art may still derive other drawings from these attached figures without creative efforts.

[0020] FIG. 1 is a cross-section diagram of a fuel gas injection valve for a high-pressure-difference gas engine in the first embodiment;

[0021] FIG. 2 is a matched schematic diagram of a valve plate and a valve seat in the first embodiment;

[0022] FIG. 3 is a structural schematic diagram of a valve plate in the first embodiment;

[0023] FIG. 4 is a structural schematic diagram of a valve seat in the first embodiment;

[0024] FIG. 5 is a cross-section diagram of a fuel gas injection valve for a high-pressure- difference gas engine in the second embodiment;

[0025] FIG. 6 is a matched schematic diagram of a valve plate and a valve seat in the second embodiment;

[0026] FIG. 7 is a structural schematic diagram of a valve plate in the second embodiment; and

[0027] FIG. 8 is a structural schematic diagram of a valve seat in the second embodiment. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0028] The following clearly and completely describes the technical scheme in the embodiments of the present disclosure with reference to the attached figures in the embodiments of the present disclosure. Apparently, the described embodiments are merely a part rather than all of the embodiments of the present disclosure. Based on the embodiment in the present disclosure, all other embodiments obtained by the ordinary technical staff in the art under the premise of without contributing creative labor belong to the scope protected by the present disclosure.

[0029] The present disclosure aims to provide a fuel gas injection valve for a high-pressure-difference gas engine to solve the problems in the prior art.

[0030] To make the foregoing objective, features and advantages of the present disclosure clearer and more comprehensible, the present disclosure is further described in detail below with reference to the attached figures and specific embodiments.

[0031] Embodiment I

[0032] A fuel gas injection valve for a high-pressure-difference gas engine in the embodiment, as shown in FIG. 1 to FIG. 4, includes an electromagnetic valve 1, an armature 2, a limiting ring 3, a travel limiting disc 4, a valve housing 5, a valve plate 6, a valve seat 8 and a reset spring 13.

[0033] A stepped through hole is formed in the center of the valve housing 5 in a penetrating mode, and a gas outlet 52 is formed in the lower end of the valve housing 5. A waist-shaped gas inlet 51 is formed in the side wall of the valve housing 5. The valve seat 8, the valve plate 6, the travel limiting disc 4 and the limiting ring 3 are sequentially installed in the stepped through hole of the valve housing 5 from bottom to top. A first O-shaped sealing ring 9 for ensuring the installation tightness is further arranged between the valve seat 8 and the valve housing 5. A stepped hole is formed in the center of the travel limiting disc 4. The electromagnetic valve 1 is fixedly installed on the valve housing 5 by fastening screws 11, and a second O-shaped sealing ring 10 for ensuring the installation tightness is further arranged between the electromagnetic valve 1 and the valve housing 5. The armature 2 is located below the electromagnetic valve 1. A diversion groove is formed in the upper end face of the armature 2, and the diversion groove can reduce the resistance caused by the compression of a working medium when the armature 2 moves up. The upper part of the armature 2 is located in the central hole of the limiting ring 3, and the lower part of the armature 2 is located in the stepped hole of the travel limiting disc 4.

[0034] A screw hole 60 is formed in the center of the valve plate 6. A connecting screw 12 passes through the screw hole 60, and the valve plate 6 is fixedly connected to the lower end of the armature 2 and gets close to the waist-shaped gas inlet 51. The valve plate 6 moves along with the armature 2. The reset spring 13 sleeves the lower part of the armature 2. The upper end of the reset spring 13 abuts against the end face of the stepped hole of the travel limiting disc 4, and the lower end of the reset spring 13 abuts against the upper end face of the valve plate 6. The reset spring 13 can provide enough reset spring force to ensure that the armature 2 and the valve plate 6 are quickly reset after the electromagnetic valve 1 is powered off. The travel limiting disc 4 can limit the upshift travel of the valve plate 6, and the valve plate 6 is light in weight, so that the impact energy can be reduced, and the reliability is improved. A first gas guide circular groove 65, a first inner annular groove 62 and a first outer annular groove 63 are formed in the lower end face of the valve plate 6 at intervals from inside to outside. The first gas guide circular groove 65 is formed in the center of the lower end face of the valve plate 6. The first outer annular groove 63 is formed in the edge of the lower end face of the valve plate 6. Six first radial through grooves 64 and six first radial connecting grooves 66 are uniformly formed in the lower end face of the valve plate 6 along the circumferential direction. The first radial through grooves 64 and the six first radial connecting grooves 66 are arranged at intervals. The six first radial through grooves 64 communicate with the first gas guide circular groove 65, the first inner annular groove 62 and the first outer annular groove 63 in a penetrating mode. The six first radial connecting grooves 66 are located between the first inner annular groove 62 and the first outer annular groove 63, and communicate the first inner annular groove 62 with the first outer annular groove 63. The first gas guide circular groove 65, the first inner annular groove 62, the first outer annular groove 63, the six first radial through grooves 64 and the six first radial connecting grooves 66 jointly form a fuel gas flow channel. Because the fuel gas flow channel is formed in the lower end face of the valve plate 6, eighteen protruding valve plate sealing blocks 61 are formed. Three semi-cylindrical pin holes 67 are uniformly formed in the side wall of the valve plate 6 along the circumferential direction.

[0035] The upper end face of the valve seat 8 is a plane. Eighteen valve seat spray holes (81) which are in one-to-one correspondence with the eighteen valve plate sealing blocks 61 and communicate with the gas outlet 52 are formed in the valve seat 8. The arrangement of the eighteen valve seat spray holes 81 in the valve seat 8 is similar to a honeycomb. The edge of the upper end of the valve seat 8 is uniformly provided with three cylindrical pins 7 in one-to-one correspondence with the three semi-cylindrical pin holes 67 along the circumferential direction. The lower end face of the valve plate 6 is matched with the upper end face of the valve seat 8. The eighteen valve plate sealing blocks 61 can cover and seal the eighteen valve seat spray holes 81. The three cylindrical pins 7 are respectively located in three semi-cylindrical pin hole grooves 67.

[0036] When the electromagnetic valve 1 is energized, the armature 2 drives the valve plate 6 to move upwards, the valve plate 6 is lifted, and the fuel gas injection valve is opened. At this time, gas entering from the waist-shaped gas inlet 51 flows out of the outlet gas 52 through the fuel gas flow channel and the eighteen valve seat spray holes 81 to begin gas supply. When the electromagnetic valve 1 is powered off, the armature 2 drives the valve plate 6 to quickly take a seat under the elastic force of the reset spring 13. The eighteen valve plate sealing blocks 61 cover and seal the eighteen valve seat spray holes 81. The fuel gas injection valve is closed to stop gas supply. The fuel gas injection valve in the embodiment can be quickly opened when the fuel gas pressure is less than or equal to 10 bar.

[0037] Embodiment II

[0038] A fuel gas injection valve for a high-pressure-difference gas engine in the embodiment, as shown in FIG. 5 to FIG. 8, includes an electromagnetic valve 1, an armature 2, a limiting ring 3, a travel limiting disc 4, a valve housing 5, a valve plate 6, a valve seat 8 and a reset spring 13.

[0039] A stepped through hole is formed in the center of the valve housing 5 in a penetrating mode, and a gas outlet 52 is formed in the lower end of the valve housing 5. A waist-shaped gas inlet 51 is formed in the side wall of the valve housing 5. The valve seat 8, the valve plate 6, the travel limiting disc 4 and the limiting ring 3 are sequentially installed in the stepped through hole of the valve housing 5 from bottom to top. A first O-shaped sealing ring 9 for ensuring the installation tightness is further arranged between the valve seat 8 and the valve housing 5. A stepped hole is formed in the center of the travel limiting disc 4. The electromagnetic valve 1 is fixedly installed on the valve housing 5 by fastening screws 11, and a second O-shaped sealing ring 10 for ensuring the installation tightness is further arranged between the electromagnetic valve 1 and the valve housing 5. The armature 2 is located below the electromagnetic valve 1. A diversion groove is formed in the upper end face of the armature 2, and the diversion groove can reduce the resistance caused by the compression of a working medium when the armature 2 moves up. The upper part of the armature 2 is located in the central hole of the limiting ring 3, and the lower part of the armature 2 is located in the stepped hole of the travel limiting disc 4.

[0040] A screw hole 60 is formed in the center of the valve plate 6. A connecting screw 12 passes through the screw hole 60, and the valve plate 6 is fixedly connected to the lower end of the armature 2 and gets close to the waist-shaped gas inlet 51. An annular spring assembly groove 68 is formed in the upper end face of the valve plate 6, and the lower end face of the valve plate 6 is a plane. The valve plate 6 moves along with the armature 2. The reset spring 13 sleeves the lower part of the armature 2. The upper end of the reset spring 13 abuts against the end face of the stepped hole of the travel limiting disc 4, and the lower end of the reset spring 13 is located in the spring assembly groove 68 and abuts against the bottom surface of the spring assembly groove 68. The reset spring 13 can provide enough reset spring force to ensure that the armature 2 and the valve plate 6 are quickly reset after the electromagnetic valve 1 is powered off. The travel limiting disc 4 can limit the up-shift travel of the valve plate 6, and the valve plate 6 is light in weight, so that the impact energy can be reduced, and the reliability is improved.

[0041] A second gas guide circular groove 85, a second inner annular groove 82 and a second outer annular groove 83 are formed in the upper end face of the valve seat 8 at intervals from inside to outside. The second gas guide circular groove 85 is formed in the center of the upper end face of the valve seat 8. Six second radial through grooves 84 and six second radial connecting grooves 86 are uniformly formed in the upper end face of the valve seat 8 along the circumferential direction. The six second radial through grooves 84 and the six second radial connecting grooves 86 are arranged at intervals. The six second radial through grooves 64 communicate with the second gas guide circular groove 85, the second inner annular groove 82 and the second outer annular groove 83 in a penetrating mode. The six second radial connecting grooves 86 are located between the second inner annular groove 82 and the second outer annular groove 83, and communicate the second inner annular groove 82 with the second outer annular groove 83. The second gas guide circular groove 85, the second inner annular groove 82, the second outer annular groove 83, the six second radial through grooves 84 and the six second radial connecting grooves 86 jointly form a fuel gas flow channel. Because the fuel gas flow channel is formed in the upper end face of the valve seat 8, eighteen protruding valve seat sealing blocks 80 are formed. One valve seat spray hole 81 which communicates with the gas outlet 52 is formed in each valve seat sealing block 80. The arrangement of the eighteen valve seat spray holes 81 in the valve seat 8 is similar to a honeycomb. The lower end face of the valve plate 6 is matched with the upper end face of the valve seat 8, and the lower end face of the valve plate 6 can cover and seal the eighteen valve seat spray holes 81.

[0042] When the electromagnetic valve 1 is energized, the armature 2 drives the valve plate 6 to move upwards, the valve plate 6 is lifted, and the fuel gas injection valve is opened. At this time, gas entering from the waist-shaped gas inlet 51 flows out of the outlet gas 52 through the fuel gas flow channel and the valve seat spray holes 81 to begin gas supply. When the electromagnetic valve 1 is powered off, the armature 2 drives the valve plate 6 to quickly take a seat under the elastic force of the reset spring 13. The lower end face of the valve plate 6 covers and seals the eighteen valve seat spray holes 81. The fuel gas injection valve is closed to stop gas supply. The fuel gas injection valve in the embodiment can be quickly opened when the fuel gas pressure is less than or equal to 10 bar.

[0043] Several examples are used for illustration of the principles and implementation methods of the present disclosure. The description of the embodiments is used to help illustrate the method and its core principles of the present disclosure. In addition, those skilled in the art can make various modifications in terms of specific embodiments and scope of application in accordance with the teachings of the present disclosure. In conclusion, the content of this specification shall not be construed as a limitation to the present disclosure.

Claims

1. A fuel gas injection valve for a high-pressure-difference gas engine, comprising an electromagnetic valve (1), an armature (2), a limiting ring (3), a travel limiting disc (4), a valve housing (5), a valve plate (6), a valve seat (8) and a reset spring (13), wherein a stepped through hole is formed in the center of the valve housing (5) in a penetrating mode, and a gas outlet (52) is formed in the lower end of the valve housing (5); a waist-shaped gas inlet (51) is formed in the side wall of the valve housing (5); the valve seat (8), the valve plate (6), the travel limiting disc (4) and the limiting ring (3) are sequentially installed in the stepped through hole from bottom to top; a stepped hole is formed in the center of the travel limiting disc (4); the electromagnetic valve (1) is fixedly installed on the valve housing (5); the armature (2) is located below the electromagnetic valve (1); the upper part of the armature (2) is located in the central hole of the limiting ring (3), and the lower part of the armature (2) is located in the stepped hole of the travel limiting disc (4); the valve plate (6) is fixedly connected to the lower end of the armature (2) and gets close to the waist-shaped gas inlet (51); the reset spring (13) sleeves the lower part of the armature (2); the upper end of the reset spring (13) abuts against the end face of the stepped hole of the travel limiting disc (4), and the lower end of the reset spring (13) abuts against the upper end face of the valve plate (6); the travel limiting disc (4) can limit the up-shift travel of the valve plate (6); the lower end face of the valve plate (6) is matched with the upper end face of the valve seat (8); a first gas guide circular groove (65), a first inner annular groove (62) and a first outer annular groove (63) are formed in the lower end face of the valve plate (6) at intervals from inside to outside; the first gas guide circular groove (65) is formed in the center of the lower end face of the valve plate (6); the first outer annular groove (63) is formed in the edge of the lower end face of the valve plate (6); a plurality of first radial through grooves (64) are uniformly formed in the lower end face of the valve plate (6) along the circumferential direction; a plurality of first radial connecting grooves (66) are uniformly formed between the first inner annular groove (62) and the first outer annular groove (63); the first radial through grooves (64) communicate with the first gas guide circular groove (65), the first inner annular groove (62) and the first outer annular groove (63) in a penetrating mode to form a fuel gas flow channel and a plurality of discrete protruding valve plate sealing blocks (61) separated by the flow channel; wherein the plurality of discretesealing blocks (61) define a reduced sealing contact area with the valve seat (8); operable to reduce a force required to separate the valve plate (6) from the valve seat (8) under high-pressure-difference conditions; the upper end face of the valve seat (8) is a plane; and a plurality of valve seat spray holes (81) which are in one-to-one correspondence with the valve plate sealing blocks (61) and communicate with the gas outlet (52) are formed in the valve seat (8).

2. The fuel gas injection valve for a high-pressure-difference gas engine according to claim 1, wherein the edge of the upper end of the valve seat (8) is uniformly provided with a plurality of cylindrical pins (7) along the circumferential direction, and a plurality of semi-cylindrical pin hole grooves (67) which are matched with the cylindrical pins (7) in a one-to-one correspondence mode are formed in the side wall of the valve plate (6).

3. The fuel gas injection valve for a high-pressure-difference gas engine according to claim 2, wherein the number of the first radial through grooves (64) is six, the number of the first radial connecting grooves (66) is also six, the numbers of the valve plate sealing blocks (61) and valve seat spray holes (81) are both eighteen, and the numbers of the cylindrical pins (7) and the semi-cylindrical pin hole grooves (67) are both three.

4. A fuel gas injection valve for a high-pressure-difference gas engine, comprising an electromagnetic valve (1), an armature (2), a limiting ring (3), a travel limiting disc (4), a valve housing (5), a valve plate (6), a valve seat (8) and a reset spring (13), wherein a stepped through hole is formed in the center of the valve housing (5) in a penetrating mode, and a gas outlet (52) is formed in the lower end of the valve housing (5); a waist-shaped gas inlet (51) is formed in the side wall of the valve housing (5); the valve seat (8), the valve plate (6), the travel limiting disc (4) and the limiting ring (3) are sequentially installed in the stepped through hole from bottom to top; a stepped hole is formed in the center of the travel limiting disc (4); the electromagnetic valve (1) is fixedly installed on the valve housing (5); the armature (2) is located below the electromagnetic valve (1); the upper part of the armature (2) is located in the central hole of the limiting ring (3), and the lower part of the armature (2) is located in the stepped hole of the travel limiting disc (4); the valve plate (6) is fixedly connected to the lower end of the armature (2) and gets close to the waist-shaped gas inlet (51); the reset spring (13) sleeves the lower part of the armature (2); the upper end of the reset spring (13) abuts against the end face of the stepped hole of the travel limiting disc (4), and the lower end of the reset spring (13) abuts against the upper end face of thevalve plate (6); the travel limiting disc (4) can limit the up-shift travel of the valve plate (6); the lower end face of the valve plate (6) is matched with the upper end face of the valve seat (8); the lower end face of the valve plate (6) is a plane; a second gas guide circular groove (85), a second inner annular groove (82) and a second outer annular groove (83) are formed in the upper end face of the valve seat (8) at intervals from inside to outside; the second gas guide circular groove (85) is formed in the center of the upper end face of the valve seat (8); a plurality of second radial through grooves (84) are uniformly formed in the upper end face of the valve seat (8) along the circumferential direction; a plurality of second radial connecting grooves (86) are uniformly formed between the second inner annular groove (86) and the second outer annular groove (83); the second radial through grooves (84) communicate with the second gas guide circular groove (85), the second inner annular groove (82) and the second outer annular groove (83) in a penetrating mode to form a fuel gas flow channel and a plurality of discrete protruding valve seat sealing blocks (80) separated by the flow channel wherein the sealing blocks (80) define a reduced sealing contact area with the valve plate (6) operable to reduce a force required to separate the valve plate (6) from the valve seat (8) under high-pressure-difference conditions; and one valve seat spray hole (81) which communicates with the gas outlet (52) is formed in each valve seat sealing block (80).

5. The fuel gas injection valve for a high-pressure-difference gas engine according to claim 4, wherein the number of the second radial through grooves (84) is six, the number of the second radial connecting grooves (86) is also six, and the numbers of the valve seat sealing blocks (80) and valve seat spray holes (81) are both eighteen.

6. The fuel gas injection valve for a high-pressure-difference gas engine according to any one of claims 4 to 5, wherein an annular spring assembly groove (68) is formed in the upper end face of the valve plate (6), and the lower end of the reset spring (13) is located in the spring assembly groove (68) and abuts against the bottom surface of the spring assembly groove (68).

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