High-pressure oil tank isolation valve for hybrid power vehicle

Abstract

The application relates to a high-pressure oil tank isolation valve for a hybrid power vehicle, which forms a main pressure relief channel between a second valve disc located in a second chamber and the inner wall of a central passage at the bottom of a first chamber, sets an auxiliary pressure relief channel on the second valve disc, uses a first valve disc located in the first chamber to form a first sealing surface and a second sealing surface for sealing the main pressure relief channel with the bottom of the first chamber and the second valve disc respectively, forms a third sealing surface for sealing the auxiliary pressure relief channel between the first valve disc and the second valve disc, sets a flow-through hole communicating with the second valve disc on the first valve disc, and the flow-through hole is located between the second sealing surface and the third sealing surface. In two working conditions of the isolation valve being powered on and the isolation valve being powered off and the oil tank port being positive pressure, pressure relief can be simultaneously performed through the main pressure relief channel and the auxiliary pressure relief channel, the flow-through cross section of pressure relief is greatly increased, the pressure relief speed is faster, and the pressure relief effect is effectively improved.

Description

TECHNICAL FIELD

[0001] The application relates to a high-pressure oil tank isolation valve for a hybrid power vehicle and belongs to the technical field of automobile isolation valves. BACKGROUND

[0002] With the increasing seriousness of automobile exhaust pollution, the current automobile exhaust emission regulations are more and more strict to the constraints of vehicle emissions into the atmosphere, but also promote the rapid development of automobile oil-electric hybrid technology. At present, hybrid vehicles (plug-in hybrid PHEV and range-extended hybrid REEV) have gradually become the most acceptable vehicle type for the public after several years of technology accumulation. The hybrid vehicle not only has good fuel economy, but also can switch between engine operation and battery operation, which can well solve the anxiety caused by pure electric range. In this process, the oil tank isolation valve emerges as the times require.

[0003] However, the existing oil tank isolation valve sets the pressure relief channel on the partition plate in the valve shell. Since the area of the partition plate is limited, the pressure relief capacity of the pressure relief channel is insufficient, and it is more and more difficult to meet the market demand. SUMMARY

[0004] The application aims to provide a high-pressure oil tank isolation valve for a hybrid power vehicle to solve the above problems.

[0005] To achieve the above purpose, the application provides the following technical scheme: a high-pressure oil tank isolation valve for a hybrid power vehicle, comprising:

[0006] a valve shell, an inner cavity of which forms a cavity, the cavity comprising a first cavity connected with an oil tank port and a second cavity connected with a carbon canister port, the second cavity being a cylindrical cavity with a smaller inner diameter than the first cavity and being communicated through a central passage, the inner diameter of the central passage being not greater than the inner diameter of the second cavity;

[0007] a first valve disc movably arranged in the first cavity, the first valve disc being movable along the axial direction of the first cavity to approach or move away from the second cavity;

[0008] a second valve disc movably arranged in the second cavity, the second valve disc being movable along the axial direction of the second cavity to approach or move away from the first cavity;

[0009] The second valve disc and the inner wall of the central passage form a main pressure relief passage, and the second valve disc forms a secondary pressure relief passage; the first valve disc and the second valve disc form a first sealing surface and a second sealing surface for blocking the main pressure relief passage, and a third sealing surface for blocking the secondary pressure relief passage; the first valve disc forms a flow-through hole which is connected to the second valve disc and is located between the second sealing surface and the third sealing surface.

[0010] Further, the end of the second valve disc is concave and forms a bearing groove, the second sealing surface is formed on the top of the bearing groove, and the third sealing surface is formed on the bottom of the bearing groove.

[0011] Further, the first valve disc includes a first sealing part which abuts in the bearing groove to block the secondary pressure relief passage, and a gap is formed between the first sealing part and the inner wall of the bearing groove.

[0012] Further, the first valve disc further includes a second sealing part which abuts with the bottom of the first chamber and the top of the bearing groove, and the second sealing part is spaced apart to form an outer sealing ring and an inner sealing ring which abut with the bottom of the first chamber and the top of the bearing groove, respectively.

[0013] Further, the bottom of the first chamber forms a first step surface and a second step surface, the first step surface is arranged away from the axis of the central passage and is arranged further away from the second chamber than the second step surface, and the first sealing surface is formed on the first step surface.

[0014] Further, the inner wall of the central passage is spaced apart to form a guide rib, and the end of the guide rib abuts on the outer wall of the second valve disc.

[0015] Further, the second valve disc includes a sealing ring, a limiting ring, and a plurality of connecting strips which are connected between the sealing ring and the limiting ring along the circumference of the limiting ring, the sealing ring is inserted into the central passage and abuts with the guide rib, the secondary pressure relief passage is formed on the sealing ring, and the limiting ring abuts on the bottom of the guide rib.

[0016] Further, a mounting hole is formed on the valve housing in the axial direction of the second chamber, a plug is mounted in the mounting hole, the second valve disc is connected to the plug through a mechanical spring, and the mechanical spring is always in a compressed state.

[0017] Further, the guide rib forms an inclined surface at one end of the second chamber, and the inclined surface is arranged gradually close to the axis of the central passage from the second chamber to the first chamber.

[0018] Further, the first chamber comprises an upper chamber for accommodating the electromagnetic assembly and a lower chamber for communicating the oil tank port, which are in communication with each other, and the cavity diameters of the upper chamber, the lower chamber and the second chamber are arranged in a decreasing trend.

[0019] The application has the beneficial effect that: the application forms a main pressure relief channel between the second valve disc located in the second chamber and the inner wall of the central passage of the bottom of the first chamber, and sets an auxiliary pressure relief channel on the second valve disc, and the first valve disc located in the first chamber forms a first sealing surface and a second sealing surface for sealing the main pressure relief channel with the bottom of the first chamber and the second valve disc respectively, and a third sealing surface for sealing the auxiliary pressure relief channel is further formed between the first valve disc and the second valve disc, and a flow-through hole communicating the second valve disc is set on the first valve disc, which is located between the second sealing surface and the third sealing surface, in the working condition of energizing the isolation valve, the first valve disc is away from the bottom of the first chamber, and the main pressure relief channel and the auxiliary pressure relief channel are simultaneously conducted for pressure relief, when in the working condition of de-energizing the isolation valve and the positive pressure of the oil tank port, the gas of the oil tank port acts on the second valve disc through the flow-through hole, the second valve disc moves towards the second chamber, so that the second sealing surface and the third sealing surface are invalid, and the main pressure relief channel and the auxiliary pressure relief channel are simultaneously conducted for pressure relief, in both working conditions, the main pressure relief channel and the auxiliary pressure relief channel can simultaneously perform pressure relief, which greatly increases the flow cross section of pressure relief, the pressure relief speed is faster, and the pressure relief effect is effectively improved.

[0020] The above description is only a summary of the technical scheme of the application, in order to more clearly understand the technical means of the application, and can be implemented according to the content of the specification, the following will be described in detail with the preferred embodiments of the application and with the help of the drawings. BRIEF DESCRIPTION OF DRAWINGS

[0021] Figure 1 The cross-sectional structure schematic diagram of the high-pressure oil tank isolation valve for the hybrid power vehicle shown in an embodiment of the application;

[0022] Figure 2 The cross-sectional structure schematic diagram of the high-pressure oil tank isolation valve for the hybrid power vehicle shown in an embodiment of the application; Figure 1 The enlarged structure schematic diagram of the A part in the middle

[0023] Figure 3 The cross-sectional structure schematic diagram of the high-pressure oil tank isolation valve for the hybrid power vehicle shown in an embodiment of the application; Figure 1 The structure schematic diagram of the second valve disc

[0024] Figure 4 The cross-sectional structure schematic diagram of the high-pressure oil tank isolation valve for the hybrid power vehicle shown in an embodiment of the application; Figure 3 The cross-sectional structure schematic diagram of the high-pressure oil tank isolation valve for the hybrid power vehicle shown in an embodiment of the application;

[0025] Figure 5 The cross-sectional structure schematic diagram of the high-pressure oil tank isolation valve for the hybrid power vehicle shown in an embodiment of the application; Figure 1 The cross-sectional structure schematic diagram of the high-pressure oil tank isolation valve for the hybrid power vehicle shown in an embodiment of the application;

[0026] Figure 6For Figure 1 A cross-sectional structural schematic diagram of the middle coil assembly;

[0027] Figure 7 For Figure 1 A cross-sectional structural schematic diagram of the middle valve housing;

[0028] Figure 8 For Figure 1 A cross-sectional structural schematic diagram of the middle mechanical valve assembly. DETAILED DESCRIPTION

[0029] The specific embodiments of the present application will be further described in conjunction with the drawings and examples. The following examples are used to illustrate the present application, but are not used to limit the scope of the present application.

[0030] In the description of the present application, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer" and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation on the present application. In addition, the terms "first", "second", "third" are only for descriptive purposes and cannot be understood as indicating or implying relative importance.

[0031] In the description of the present application, it should be noted that unless otherwise explicitly specified and limited, the terms "mounting", "connecting", "connecting" should be understood in a broad sense, for example, it can be fixedly connected, or it can be detachably connected, or integrally connected; it can be mechanically connected, or it can be electrically connected; it can be directly connected, or it can be indirectly connected through an intermediate medium; it can be the communication inside two elements. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0032] Please refer to Figures 1-2 , an embodiment of the present application shows a high-pressure oil tank isolation valve for a hybrid power vehicle, which comprises a valve housing 1, a coil assembly 2, an armature assembly 3 and a mechanical valve assembly 4. In this embodiment, the coil assembly 2 and the armature assembly 3 are two independent individuals, which are assembled and used in combination. Of course, in other embodiments, the coil assembly 2 and the armature assembly 3 can also be provided as one body. The coil assembly 2 drives the armature assembly 3 to move up and down to cooperate with the mechanical valve assembly 3 to achieve pressure relief.

[0033] Valve housing 1 forms a chamber inside, the chamber includes a first chamber 14 outside the oil tank port 11 and a second chamber 15 outside the carbon tank port 12, the second chamber 15 is a cylindrical chamber with a smaller inner diameter than the first chamber 14 and is communicated by a central passage 13, the inner diameter of the central passage 13 is not greater than the inner diameter of the second chamber 15. In this embodiment, the oil tank port 11 and the carbon tank port 12 are connected to the side walls of the first chamber 14 and the second chamber 15 respectively. Coil assembly 2 and armature assembly 3 are arranged in the first chamber 14, and mechanical valve assembly 3 is arranged in the second chamber 1514.

[0034] Please refer to Figure 4 and Figure 5 , the first valve disc 31 is movably arranged in the first chamber 14, and the first valve disc 31 can move along the axis direction of the first chamber 14 to approach or away from the second chamber 15.

[0035] Wherein, the coil assembly 2 includes a shell 21, a winding frame 23 arranged in the shell 21, an electromagnetic valve coil 22 wound on the winding frame 23, a fixed iron core 24 fixedly arranged in the winding frame 23 and a guide shaft 25 fixedly connected to the fixed iron core 24. During assembly, the shell 21 is sealingly connected with the valve housing, and the shell 21 is provided with a connector 211 for external power supply, and the connector 211 is electrically connected with a diode 212 and the electromagnetic valve coil 22 arranged in the shell 21 respectively. In order to improve the sealing effect, a first sealing ring 231 is arranged between the winding frame 23 and the shell 21, and a second sealing ring 241 is arranged between the winding frame 23 and the fixed iron core 24.

[0036] The armature assembly 3 includes an armature 32 sleeved outside the guide shaft 25, the first valve disc 31 is connected to the end of the armature 32 and abuts against the shell 21 of the coil assembly 2 through the electromagnetic spring 24. Under the action of the electromagnetic force provided by the coil assembly 2 to the armature assembly 3, the first valve disc 31 is lifted to compress the electromagnetic spring 24 to open the central passage 13 on the bottom of the first chamber 14. When the coil assembly 2 is de-energized, the electromagnetic spring 34 relaxes to abut the first valve disc 31 on the bottom of the first chamber 14 to block the central passage 13. It is a prior art and will not be described here. In addition, a rubber pad 33 for damping when abutting against the fixed iron core 24 is designed on the top of the armature 32 to avoid rigid abutment and improve the service life.

[0037] Please refer to Figure 3 and Figure 4 , the mechanical valve assembly 3 includes a second valve disc 41 movably arranged in the second chamber 15, and the second valve disc 41 can move along the axis direction of the second chamber 15 to approach or away from the first chamber 14.

[0038] The second valve disc 41 and the inner wall of the center passage 13 form a main pressure relief passage, and the second valve disc 41 forms an auxiliary pressure relief passage 4111. The first valve disc 31 and the bottom of the first chamber 14 form a first sealing surface 16 and a second sealing surface 4113 that seal the main pressure relief passage. The first valve disc 31 and the second valve disc 41 form a third sealing surface 4114 that seals the auxiliary pressure relief passage 4111. The first valve disc 31 has a flow hole that communicates with the second valve disc 41 and is located between the second sealing surface 4113 and the third sealing surface 4114. It should be noted that the bottom of the first chamber 14 refers to the stepped surface formed between the first chamber 14 and the center passage 13.

[0039] In this embodiment, the end of the second valve disc 41 is concave and forms a bearing groove 4112. The second sealing surface 4113 is formed on the top of the bearing groove 4112, and the third sealing surface 4114 is formed on the bottom of the bearing groove 4112. By setting the second sealing surface 4113 and the third sealing surface 4114 with a height difference, the sealing strength of the second sealing surface 4113 and the third sealing surface 4114 can be adjusted as needed.

[0040] Please refer to Figure 6 In this embodiment, the first valve disc 31 includes a first sealing portion 311 that abuts in the bearing groove 4112 to seal the auxiliary pressure relief passage 4111. A gap is formed between the first sealing portion 311 and the inner wall of the bearing groove 4112. The first sealing portion 311 extends into the center passage 13 and abuts against the second valve disc to seal the auxiliary pressure relief passage. The end of the first sealing portion 311 is provided with a rubber sealing member 3111. The armature 3232 has a circular sealing lip that abuts against the bottom of the bearing groove 4112 to form a third sealing surface 4114 that surrounds the auxiliary pressure relief passage 4111. A gap is formed between the first sealing portion 311 and the inner wall of the bearing groove 4112, which allows the gas in the tank port to press against the second valve disc 41 to form a larger force application surface, facilitating the movement of the second valve disc 41 towards the second chamber 15 to open the main pressure relief passage and the auxiliary pressure relief passage 4111 for pressure relief.

[0041] In this embodiment, the first valve disc 31 also includes a second sealing portion 312 that abuts against the bottom of the first chamber 14 and the top of the bearing groove 4112. The second sealing portion 312 has an outer sealing ring 3121 and an inner sealing ring 3122 that abut against the bottom of the first chamber 14 and the top of the bearing groove 4112, respectively. The outer sealing ring 3121 abuts against the bottom of the first chamber 14 to form a first sealing surface 16, and the inner sealing ring 3122 abuts against the second valve disc 41 to form a third sealing surface 4114. The inner sealing ring 3122 and the outer sealing ring 3121 are arranged in a spaced manner, which allows the gas in the carbon canister port 12 to have a larger force application area under negative pressure conditions of the tank port.

[0042] In the embodiment, the first sealing part 311 is integrally formed with the armature 32 and arranged at the end of the armature 32, the second sealing part 312 is connected to the armature 32 through the connecting frame 313, and the flow-through hole is formed at the connection between the second sealing part 312 and the first sealing part 311, wherein the outer sealing lip 3121 and the inner sealing lip 3122 are the outer sealing lip and the inner sealing lip of the sealing ring arranged on the second sealing part 312. Of course, in other embodiments, the first sealing part 311 and the second sealing part 312 can be integrally formed with the armature 32, or the second sealing part 312 is integrally formed with the armature 32 and the first sealing part 311 is connected to the armature 32. The outer sealing lip 3121 and the inner sealing lip 3122 can also be two sealing rings arranged independently. They can be set according to the needs and are not specifically limited here.

[0043] In the embodiment, the bottom of the first chamber 14 is formed with a first step surface and a second step surface, the first step surface is away from the axis of the central passage 13 and arranged away from the second chamber 15 compared with the second step surface, and the first sealing surface 16 is formed on the first step surface. That is, when the first valve disc 31 abuts on the first step surface, a gap is formed between the first step surface and the second step surface, so as to further provide a larger force application area for the gas of the carbon canister port 12 under the working condition of negative pressure of the oil tank port.

[0044] Please refer to Figure 7 The inner wall of the central passage 13 is arranged with guide ribs 131 at intervals, and the end of the guide rib 131 abuts on the outer wall of the second valve disc 41. The guide rib 131 is used for guiding the movement of the second valve disc 41, so as to ensure that the second valve disc 41 abuts on the first valve disc 31 accurately, thereby guaranteeing the sealing effect of the second sealing surface 4113 and the third sealing surface 4114. In the embodiment, the central passage 13 is part of the second chamber 15, the guide rib is arranged at the end of the second chamber 15 close to the first chamber 14, the first step surface is formed at the bottom of the first chamber 14, and the second step surface is formed at the end of the guide rib on the side of the first chamber 14. In this way, the inner diameter of the central passage 13 is the same as that of the second chamber 15, so as to maximize the pressure relief capacity of the main pressure relief passage. Of course, in other embodiments, the central passage 13 can also be arranged as an independent passage with an inner diameter smaller than that of the second chamber 15. In this way, the guide rib can be arranged on the second valve disc, thereby reducing the manufacturing difficulty of the valve housing.

[0045] In the embodiment, the second valve disc 41 comprises a sealing ring 411, a limiting ring 412 and a plurality of connecting strips 413 which are connected between the sealing ring 411 and the limiting ring 412 along the circumference of the limiting ring 412, the sealing ring 411 is inserted into the central passage 13 and abuts against the guide rib 131, the auxiliary pressure relief passage 4111 is formed on the sealing ring 411, and the limiting ring 412 abuts against the bottom of the guide rib 131. The limiting ring 412 and the sealing ring 411 are connected through the connecting strips 413 which are arranged at intervals, the main pressure relief passage and the second chamber 15 are communicated through the gaps between the adjacent connecting strips 413, so as to accelerate the pressure relief speed. The abutting groove 4112 is arranged on the sealing ring 411, and the auxiliary pressure relief passage 4111 is formed at the bottom of the abutting groove 4112.

[0046] Please refer to Figure 8 In the embodiment, the mechanical valve assembly 4 further comprises a mechanical spring 42, a mounting hole is formed on the valve shell 1 in the axial direction of the second chamber 15, the plug 5 is mounted in the mounting hole, the second valve disc 41 is connected to the plug 5 through the mechanical spring 42, and the mechanical spring 42 is always in a compressed state. By arranging the mounting hole, the second valve disc 41 is facilitated to be mounted into the second chamber 15, after the second valve disc 41 and the mechanical spring 42 are mounted into the second valve body, the outer diameter of the plug 5 is sealed by laser welding with the valve shell 1. The mechanical spring 42 positioning ribs are arranged on the second valve disc 41 and the plug 5, so as to ensure the stability of the mechanical spring 42.

[0047] In the embodiment, the guide rib 131 is formed with a slope 1311 at one end of the second chamber 15, and the slope 1311 is arranged to gradually approach the axis of the central passage 13 from the second chamber 15 to the first chamber 14. The tapered passage opening is formed by surrounding the slope 1311 of the guide rib, so as to facilitate the second valve disc 41 to enter the central passage 13.

[0048] In the embodiment, the first chamber 14 comprises an upper chamber 141 for accommodating the electromagnetic assembly and a lower chamber 142 for communicating with the tank port 11, the upper chamber 141 and the lower chamber 142 are in communication with each other, and the diameters of the cavities of the upper chamber 141, the lower chamber 142 and the second chamber 15 are arranged in a decreasing trend. The upper chamber 141, the lower chamber 142 and the second chamber 15 are all cylindrical cavities, the coil assembly 2 is arranged in the upper chamber 141, the armature assembly 3 is arranged in the lower chamber 142 and connected to the coil assembly 2, and the mechanical valve assembly 3 is arranged in the second chamber 15 and sealedly abuts against the armature assembly 3. In this way, in order to adapt to the installation space requirements of the coil assembly 2, the armature assembly 3 and the mechanical valve assembly 3, the structure is compact, and the production cost is reduced.

[0049] The application forms a main pressure relief channel between the second valve disc and the inner wall of the central passage of the bottom of the first chamber, and sets an auxiliary pressure relief channel on the second valve disc, and the first valve disc in the first chamber forms a first sealing surface and a second sealing surface for sealing the main pressure relief channel with the bottom of the first chamber and the second valve disc respectively, and a third sealing surface for sealing the auxiliary pressure relief channel is formed between the first valve disc and the second valve disc, and a flow-through hole communicating with the second valve disc is set on the first valve disc, the flow-through hole is located between the second sealing surface and the third sealing surface, in the working condition of the isolation valve being powered on, the first valve disc is away from the bottom of the first chamber, the main pressure relief channel and the auxiliary pressure relief channel are simultaneously conducted to relieve pressure, when the isolation valve is powered off and the oil tank port is under positive pressure, the gas of the oil tank port acts on the second valve disc through the flow-through hole, the second valve disc moves towards the second chamber, so that the second sealing surface and the third sealing surface are invalid, the main pressure relief channel and the auxiliary pressure relief channel are simultaneously conducted to relieve pressure, in the two working conditions, the main pressure relief channel and the auxiliary pressure relief channel can simultaneously relieve pressure, greatly increasing the flow-through section of the pressure relief, the pressure relief speed is faster, and the pressure relief effect is effectively improved.

[0050] The technical features of the above-mentioned embodiments can be combined arbitrarily, and to make the description simple, all possible combinations of the technical features in the above-mentioned embodiments are not described, however, as long as the combination of the technical features does not exist contradictory, it should be considered as the scope of the present application.

[0051] The above-mentioned embodiments only express several embodiments of the present application, the description is more specific and detailed, but it should not be understood as the limitation of the scope of the patent. It should be pointed out that for ordinary skilled in the art, without departing from the concept of the present application, a number of modifications and improvements can be made, which all belong to the protection scope of the present application. Therefore, the protection scope of the patent of the present application should be subject to the appended claims.

Claims

1. A high-pressure fuel tank isolation valve for hybrid vehicles, characterized in that, The high-pressure oil tank isolation valve for the hybrid power vehicle comprises: a valve shell, an inner part of which forms a chamber, the chamber comprising a first chamber externally connecting an oil tank port and a second chamber externally connecting a carbon tank port, the second chamber being a cylindrical chamber with an inner diameter smaller than that of the first chamber and being communicated by a central passage with an inner diameter not greater than that of the second chamber; a first valve disc movably arranged in the first chamber, the first valve disc being movable along the axial direction of the first chamber to approach or move away from the second chamber; a second valve disc movably arranged in the second chamber, the second valve disc being movable along the axial direction of the second chamber to approach or move away from the first chamber; wherein a main pressure relief passage is formed between the second valve disc and the inner wall of the central passage, and an auxiliary pressure relief passage is formed in the second valve disc, the first valve disc and the second valve disc respectively form a first sealing surface and a second sealing surface for blocking the main pressure relief passage, and a third sealing surface is further formed between the first valve disc and the second valve disc for blocking the auxiliary pressure relief passage, and a flow-through hole is formed on the first valve disc for communicating the second valve disc and being located between the second sealing surface and the third sealing surface.

2. The hybrid vehicle high-pressure tank isolation valve according to claim 1, characterized by, The end of the second valve disc is concave and forms a bearing groove, the second sealing surface is formed on the groove top of the bearing groove, and the third sealing surface is formed on the groove bottom of the bearing groove.

3. The hybrid vehicle high-pressure tank isolation valve according to claim 2, characterized by The first valve disc comprises a first sealing part abutting in the bearing groove to block the auxiliary pressure relief passage, and a gap is formed between the first sealing part and the inner wall of the bearing groove.

4. The hybrid vehicle high-pressure tank isolation valve according to claim 3, characterized by The first valve disc further comprises a second sealing part abutting with the bottom of the first chamber and the top of the bearing groove, and an outer sealing ring and an inner sealing ring are formed on the second sealing part and abutting with the bottom of the first chamber and the top of the bearing groove, respectively.

5. The hybrid vehicle high-pressure tank isolation valve according to claim 1, characterized by, The bottom of the first chamber forms a first step surface and a second step surface, the first step surface is arranged away from the axis of the central passage and away from the second chamber compared with the second step surface, and the first sealing surface is formed on the first step surface.

6. The hybrid vehicle high-pressure tank isolation valve according to claim 2, characterized by The inner wall of the central passage is provided with a guide rib at intervals, and the end of the guide rib abuts on the outer wall of the second valve disc.

7. The hybrid vehicle high-pressure tank isolation valve according to claim 6, characterized by The second valve disc comprises a sealing ring, a limiting ring and a plurality of connecting strips connected between the sealing ring and the limiting ring along the circumferential direction of the limiting ring, the sealing ring is inserted into the central passage and abuts with the guide rib, the auxiliary pressure relief passage is formed on the sealing ring, and the limiting ring abuts on the bottom of the guide rib.

8. The hybrid vehicle high-pressure tank isolation valve according to claim 6, characterized by An installation hole is formed on the valve shell in the axial direction of the second chamber, a plug is installed in the installation hole, the second valve disc is connected to the plug by a mechanical spring, and the mechanical spring is always in a compressed state.

9. The hybrid vehicle high-pressure tank isolation valve according to claim 8, characterized by The guide rib forms an inclined surface at one end of the second chamber, and the inclined surface is arranged gradually close to the axis of the central passage from the second chamber to the first chamber.

10. The hybrid vehicle high-pressure tank isolation valve according to claim 9, characterized in that, The first chamber comprises an upper chamber for accommodating an electromagnetic assembly and a lower chamber for communicating the oil tank port, which are in communication with each other, and the cavity diameters of the upper chamber, the lower chamber and the second chamber are arranged in a decreasing trend.

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