High-pressure oil tank isolating valve for hybrid power vehicle

Abstract

According to the high-pressure oil tank isolating valve for the hybrid power vehicle, a main pressure relief channel is formed between a second valve disc located in a second cavity and the inner wall of a center channel at the bottom of a first cavity, and an auxiliary pressure relief channel is formed in the second valve disc; a first sealing face and a second sealing face which are used for sealing a main pressure relief channel are formed by a first valve disc located in a first cavity, the bottom of the first cavity and a second valve disc respectively, and a third sealing face used for sealing an auxiliary pressure relief channel is further formed between the first valve disc and the second valve disc. A circulation hole communicated with the second valve disc is formed in the first valve disc, the circulation hole is located between the second sealing face and the third sealing face, and under the two working conditions that the isolation valve is powered on, the isolation valve is powered off and the port of the oil tank is in positive pressure, pressure relief can be conducted at the same time through the main pressure relief channel and the auxiliary pressure relief channel. The circulation section of pressure relief is greatly increased, the pressure relief speed is higher, and the pressure relief effect is effectively improved.

Description

Technical Field

[0001] The invention relates to a high-pressure oil tank isolation valve for a hybrid vehicle, belonging to the technical field of automobile isolation valves. Background Art

[0002] With the increasing severity of automobile exhaust pollution, the current automobile exhaust emission regulations have increasingly stringent restrictions on vehicles' allowed atmospheric emissions, but have also promoted the rapid development of automobile hybrid technology. At present, hybrid models (plug-in hybrid PHEV and extended-range hybrid REEV) have gradually become the most acceptable models for the general public after several years of technological accumulation. Hybrid models not only have good fuel economy, but can also switch between engine and battery working states, which can well solve the anxiety caused by pure electric mileage. In this process, the fuel tank isolation valve came into being.

[0003] However, the existing oil tank isolation valve has a pressure relief channel arranged on a partition in the valve housing. Due to the limited area of ​​the partition, the pressure relief capacity of the pressure relief channel is insufficient, and it is increasingly difficult to meet market demand. Summary of the invention

[0004] The object of the present invention is to provide a high-pressure fuel tank isolation valve for a hybrid vehicle to solve the above-mentioned problem.

[0005] To achieve the above object, the present invention provides the following technical solution: a high-pressure fuel tank isolation valve for a hybrid vehicle, the high-pressure fuel tank isolation valve for a hybrid vehicle comprising:

[0006] A valve housing, wherein chambers are formed inside the valve housing, wherein the chambers include a first chamber externally connected to a fuel tank port and a second chamber externally connected to a carbon canister port, wherein the second chamber is a columnar chamber having an inner diameter smaller than that of the first chamber and is connected through a central channel, wherein the inner diameter of the central channel is not larger than the inner diameter of the second chamber;

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

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

[0009] A main pressure relief channel is formed between the second valve disc and the inner wall of the central channel, and an auxiliary pressure relief channel is formed in the second valve disc. The first valve disc forms a first sealing surface and a second sealing surface with the bottom of the first chamber and the second valve disc respectively for blocking the main pressure relief channel. A third sealing surface for blocking the auxiliary pressure relief channel is also formed between the first valve disc and the second valve disc. A flow hole is formed on the first valve disc, which is connected to the second valve disc and is located between the second sealing surface and the third sealing surface.

[0010] Furthermore, the end of the second valve disc is inwardly concave to form a supporting groove, the second sealing surface is formed at the groove top of the supporting groove, and the third sealing surface is formed at the groove bottom of the supporting groove.

[0011] Further, the first valve disc includes a first sealing portion abutting in the abutting groove to block the auxiliary pressure relief channel, and a gap is formed between the first sealing portion and an inner wall of the abutting groove.

[0012] Furthermore, the first valve disc also includes a second sealing portion abutting against the bottom of the first chamber and the top of the abutting groove, and the second sealing portion is spaced apart with an outer sealing ring and an inner sealing ring abutting against the bottom of the first chamber and the top of the abutting groove respectively.

[0013] Further, a first step surface and a second step surface are formed at the bottom of the first chamber, the first step surface is away from the axis of the central channel and is arranged farther from the second chamber than the second step surface, and the first sealing surface is formed on the first step surface.

[0014] Furthermore, guide ribs are arranged at intervals on the inner wall of the central channel, and ends of the guide ribs are abutted against the outer wall of the second valve disc.

[0015] Furthermore, the second valve disc includes a sealing ring, a limiting ring and a plurality of connecting strips connected between the sealing ring and the limiting ring at circumferential intervals along the limiting ring, the sealing ring is inserted into the central channel and abuts against the guide rib, the auxiliary pressure relief channel is formed on the sealing ring, and the limiting ring abuts against the bottom of the guide rib.

[0016] Furthermore, a mounting hole is opened on the valve housing in the axial direction of the second chamber, a plug is installed 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] Furthermore, the guide rib forms an inclined surface at one end of the second chamber, and the inclined surface is arranged gradually approaching the axis of the central channel from the second chamber toward the first chamber.

[0018] Furthermore, the first chamber includes an upper chamber for accommodating the electromagnetic assembly and a lower chamber for communicating with the oil tank port, and the cavity diameters of the upper chamber, the lower chamber and the second chamber are arranged in a decreasing trend.

[0019] The beneficial effects of the present invention are as follows: the present application forms a main pressure relief channel between the second valve disc located in the second chamber and the inner wall of the central channel at the bottom of the first chamber, and an auxiliary pressure relief channel is arranged on the second valve disc, and a first sealing surface and a second sealing surface for sealing the main pressure relief channel are formed with the first valve disc located in the first chamber and the bottom of the first chamber and the second valve disc respectively, a third sealing surface for sealing the auxiliary pressure relief channel is also formed between the first valve disc and the second valve disc, and a flow hole communicating with the second valve disc is arranged on the first valve disc, and the flow hole is located between the second sealing surface and the third sealing surface. When the isolation valve is energized, 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 opened for pressure relief. When the isolation valve is de-energized and the tank port is under positive pressure, the gas at the tank port acts on the second valve disc through the flow port, and the second valve disc moves toward the second chamber to render the second sealing surface and the third sealing surface invalid. The main pressure relief channel and the auxiliary pressure relief channel are simultaneously opened for pressure relief. Under both working conditions, pressure relief can be simultaneously performed through the main pressure relief channel and the auxiliary pressure relief channel, which greatly increases the flow cross-section of pressure relief, makes the pressure relief speed faster, and effectively improves the pressure relief effect.

[0020] The above description is only an overview of the technical solution of the present invention. In order to more clearly understand the technical means of the present invention and implement it according to the contents of the specification, the following is a detailed description of the preferred embodiments of the present invention in conjunction with the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 It is a schematic cross-sectional structure diagram of a high-pressure fuel tank isolation valve for a hybrid vehicle shown in an embodiment of the present application;

[0022] Figure 2 for Figure 1 Schematic diagram of the enlarged structure of the middle A part

[0023] Figure 3 for Figure 1 A schematic diagram of the structure of the second valve disc;

[0024] Figure 4 for Figure 3 A schematic diagram of the cross-sectional structure of the second valve disc;

[0025] Figure 5 for Figure 1 A schematic diagram of the cross-sectional structure of the middle armature assembly;

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

[0027] Figure 7 for Figure 1 Schematic diagram of the cross-sectional structure of the middle valve housing;

[0028] Figure 8 for Figure 1 Schematic diagram of the cross-sectional structure of the mechanical valve assembly. DETAILED DESCRIPTION

[0029] The specific implementation of the present invention is further described in detail below in conjunction with the accompanying drawings and examples. The following examples are used to illustrate the present invention, but are not intended to limit the scope of the present invention.

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

[0031] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0032] Please refer to Figure 1 to Figure 2 , a hybrid vehicle high pressure tank isolation valve shown in an embodiment of the present application, the hybrid vehicle high pressure tank isolation valve 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 independently arranged 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 arranged as one body. The armature assembly 3 is driven by the coil assembly 2 to move up and down, so as to cooperate with the mechanical valve assembly 3 to achieve pressure relief.

[0033] The valve housing 1 forms a chamber inside, and the chamber includes a first chamber 14 connected to the external fuel tank port 11 and a second chamber 15 connected to the external carbon canister port 12. The second chamber 15 is a columnar chamber with an inner diameter smaller than that of the first chamber 14 and is connected through a central channel 13. The inner diameter of the central channel 13 is not larger than the inner diameter of the second chamber 15. In this embodiment, the fuel tank port 11 and the carbon canister port 12 are respectively connected to the side walls of the first chamber 14 and the second chamber 15. The coil assembly 2 and the armature assembly 3 are arranged in the first chamber 14, and the 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 disposed in the first chamber 14 , and the first valve disc 31 can move along the axial direction of the first chamber 14 to approach or move away from the second chamber 15 .

[0035] The coil assembly 2 includes a housing 21, a winding frame 23 disposed in the housing 21, a solenoid valve coil 22 wound on the winding frame 23, a fixed iron core 24 fixedly disposed in the winding frame 23, and a guide shaft 25 fixedly connected to the fixed iron core 24. When assembled, the housing 21 is sealed and connected to the valve housing. A connector 211 for an external power supply is disposed on the housing 21. The connector 211 is electrically connected to a diode 212 disposed in the housing 21 and the solenoid valve coil 22, respectively. To improve the sealing effect, a first sealing ring 231 is disposed between the winding frame 23 and the housing 21, and a second sealing ring 241 is disposed between the winding frame 23 and the fixed iron core 24.

[0036] The armature assembly 3 includes an armature 32 sleeved on the outside of the guide shaft 25. The first valve disc 31 is connected to the end of the armature 32 and abuts against the housing 21 of the coil assembly 2 through the electromagnetic spring 24. When the coil assembly 2 is powered on and provides electromagnetic force to the armature assembly 3, the first valve disc 31 is lifted and compressed to open the central channel 13 on the bottom of the first chamber 14. When the coil assembly 2 is powered off, the electromagnetic spring 34 is relaxed to hold the first valve disc 31 against the bottom of the first chamber 14 to block the central channel 13. This is a prior art and will not be described in detail here. In addition, a rubber pad 33 is designed on the top of the armature 32 for shock absorption when abutting against the fixed iron core 24 to avoid rigid abutment and improve service life.

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

[0038] Among them, a main pressure relief channel is formed between the second valve disc 41 and the inner wall of the central channel 13, and an auxiliary pressure relief channel 4111 is formed in the second valve disc 41. The first valve disc 31 forms a first sealing surface 16 and a second sealing surface 4113 with the bottom of the first chamber 14 and the second valve disc 41 to block the main pressure relief channel, respectively. A third sealing surface 4114 for blocking the auxiliary pressure relief channel 4111 is also formed between the first valve disc 31 and the second valve disc 41. A flow hole is formed on the first valve disc 31 that is connected to 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 here refers to the step surface formed between the first chamber 14 with different inner diameters and the central channel.

[0039] In this embodiment, the end of the second valve disc 41 is concavely formed with a supporting groove 4112, the second sealing surface 4113 is formed at the groove top of the supporting groove 4112, and the third sealing surface 4114 is formed at the groove bottom of the supporting groove 4112. By providing the second sealing surface 4113 and the third sealing surface 4114 with a height difference, it is convenient to set the sealing strength of the second sealing surface 4113 and the third sealing surface 4114 as needed.

[0040] Please refer to Figure 6 In this embodiment, the first valve disc 31 includes a first sealing portion 311 abutting against the abutting groove 4112 to block the auxiliary pressure relief channel 4111, and a gap is formed between the first sealing portion 311 and the inner wall of the abutting groove 4112. The first sealing portion 311 extends into the central channel 13 and abuts against the second valve disc to seal the auxiliary pressure relief channel. A rubber seal 3111 is provided at the end of the first sealing portion 311. The armature 3232 rubber seal 3111 has a circle of annular sealing lips abutting against the bottom of the abutting groove 4112 to form a third sealing surface 4114 surrounding the auxiliary pressure relief channel 4111. A gap is formed between the first sealing portion 311 and the inner wall of the abutting groove 4112, so that when the gas at the oil tank port is pressurized on the second valve disc 41, a larger force application surface can be formed, which is convenient for driving the second valve disc 41 to move toward the second chamber 15, thereby opening the main pressure relief channel and the auxiliary pressure relief channel 4111 for pressure relief.

[0041] In this embodiment, the first valve disc 31 further includes a second sealing portion 312 abutting against the bottom of the first chamber 14 and the top of the abutting groove 4112, and an outer sealing ring 3121 and an inner sealing ring 3122 are formed on the second sealing portion 312 to abut against the bottom of the first chamber 14 and the top of the abutting 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 at intervals, so that under the working condition of negative pressure at the fuel tank port, a larger force application area can be provided to the gas at the carbon canister port 12.

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

[0043] In this embodiment, a first step surface and a second step surface are formed at the bottom of the first chamber 14, the first step surface is away from the axis of the central channel 13 and is arranged farther from the second chamber 15 than 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 against the first step surface, a gap is formed between the first valve disc 31 and the second step surface, so that under the working condition of negative pressure at the fuel tank port, a larger force application area is further provided to the gas at the carbon canister port 12.

[0044] Please refer to Figure 7 , guide ribs 131 are arranged at intervals on the inner wall of the central channel 13, and the ends of the guide ribs 131 abut against the outer wall of the second valve disc 41. The guide ribs 131 are used to guide the movement of the second valve disc 41 to ensure that the second valve disc 41 accurately abuts against the first valve disc 31, thereby ensuring the sealing effect of the second sealing surface 4113 and the third sealing surface 4114. In this embodiment, the central channel 13 is a part of the second chamber 15, the guide ribs are 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 first chamber 14. In this way, the inner diameter of the central channel 13 is the same as that of the second chamber 15, so as to maximize the pressure relief capacity of the main pressure relief channel. Of course, in other embodiments, the central channel 13 can also be set as an independent channel with an inner diameter smaller than that of the second chamber 15. In this way, it is convenient to set the guide ribs on the second valve disc, thereby reducing the difficulty of manufacturing the valve housing.

[0045] In this embodiment, the second valve disc 41 includes a sealing ring 411, a limiting ring 412, and a plurality of connecting strips 413 connected between the sealing ring 411 and the limiting ring 412 at intervals along the circumference of the limiting ring 412. The sealing ring 411 is inserted into the central channel 13 and abuts against the guide rib 131. The auxiliary pressure relief channel 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 by connecting strips 413 arranged at intervals, and the gaps between adjacent connecting strips 413 can be used to connect the main pressure relief channel and the second chamber 15 to accelerate the pressure relief speed. The abutting groove 4112 is arranged on the sealing ring 411, and the auxiliary pressure relief channel 4111 is formed at the bottom of the abutting groove 4112.

[0046] Please refer to Figure 8 In this embodiment, the mechanical valve assembly 4 also includes a mechanical spring 42. A mounting hole is provided on the valve housing 1 in the axial direction of the second chamber 15. The plug 5 is installed 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 providing the mounting hole, it is convenient to install the second valve disc 41 into the second chamber 15. After the second valve disc 41 and the mechanical spring 42 are installed in the second valve body, the outer diameter of the plug 5 is assembled with the valve housing 1 by laser welding to achieve sealing. The second valve disc 41 and the plug 5 are both provided with positioning ribs for the mechanical spring 42 to ensure the stability of the seat of the mechanical spring 42.

[0047] In this embodiment, the guide rib 131 is formed with an inclined surface 1311 at one end of the second chamber 15, and the inclined surface 1311 is arranged from the second chamber 15 toward the first chamber 14 and gradually approaches the axis of the central channel 13. The inclined surface 1311 of the guide bar is surrounded to form a tapered channel opening, which facilitates the second valve disc 41 to enter the central channel 13.

[0048] In this embodiment, the first chamber 14 includes an upper chamber 141 for accommodating the electromagnetic assembly and a lower chamber 142 for communicating with the oil tank port 11, and the cavity diameters 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 cavity structures, 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 sealed with the armature assembly 3. 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 controlled.

[0049] The present application forms a main pressure relief channel between a second valve disc located in the second chamber and an inner wall of a central channel at the bottom of the first chamber, and an auxiliary pressure relief channel is arranged on the second valve disc, and a first sealing surface and a second sealing surface for sealing the main pressure relief channel are formed with the first valve disc located in the first chamber, the bottom of the first chamber and the second valve disc, respectively; a third sealing surface for sealing the auxiliary pressure relief channel is also formed between the first valve disc and the second valve disc, and a flow hole communicating with the second valve disc is arranged on the first valve disc, and the flow hole is located between the second sealing surface and the third sealing surface. When the isolation valve is energized Under the working condition of the first valve disc away from the bottom of the first chamber, the main pressure relief channel and the auxiliary pressure relief channel are simultaneously connected for pressure relief; when the isolation valve is powered off and the tank port is under positive pressure, the gas at the tank port acts on the second valve disc through the flow port, and the second valve disc moves toward the second chamber to render the second sealing surface and the third sealing surface invalid, and the main pressure relief channel and the auxiliary pressure relief channel are simultaneously connected for pressure relief. Under both working conditions, pressure relief can be simultaneously performed through the main pressure relief channel and the auxiliary pressure relief channel, which greatly increases the flow cross-section of pressure relief, makes the pressure relief speed faster, and effectively improves the pressure relief effect.

[0050] The technical features of the above-described embodiments may be arbitrarily combined. To make the description concise, not all possible combinations of the technical features in the above-described embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0051] The above-mentioned embodiments only express several implementation methods of the present invention, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the invention patent. It should be pointed out that, for ordinary technicians in this field, several variations and improvements can be made without departing from the concept of the present invention, and these all belong to the protection scope of the present invention. Therefore, the protection scope of the patent of the present invention shall be subject to the attached claims.

Claims

1. A high-pressure fuel tank isolation valve for a hybrid vehicle, characterized in that: The high-pressure fuel tank isolation valve for a hybrid vehicle comprises: A valve housing, wherein chambers are formed inside the valve housing, wherein the chambers include a first chamber externally connected to a fuel tank port and a second chamber externally connected to a carbon canister port, wherein the second chamber is a columnar chamber having an inner diameter smaller than that of the first chamber and is connected through a central channel, wherein the inner diameter of the central channel is not larger than the inner diameter of the second chamber; a first valve disc, movably disposed in the first chamber, the first valve disc being movable along the axis direction of the first chamber to approach or move away from the second chamber; a second valve disc, movably disposed in the second chamber, the second valve disc being movable along the axis direction of the second chamber to approach or move away from the first chamber; A main pressure relief channel is formed between the second valve disc and the inner wall of the central channel, and an auxiliary pressure relief channel is formed in the second valve disc. The first valve disc forms a first sealing surface and a second sealing surface with the bottom of the first chamber and the second valve disc respectively for blocking the main pressure relief channel. A third sealing surface for blocking the auxiliary pressure relief channel is also formed between the first valve disc and the second valve disc. A flow hole is formed on the first valve disc, which is connected to the second valve disc and is located between the second sealing surface and the third sealing surface.

2. The high-pressure fuel tank isolation valve for a hybrid vehicle according to claim 1, characterized in that: The end of the second valve disc is concavely formed with a supporting groove, the second sealing surface is formed at the groove top of the supporting groove, and the third sealing surface is formed at the groove bottom of the supporting groove.

3. The high-pressure fuel tank isolation valve for a hybrid vehicle according to claim 2, characterized in that: The first valve disc includes a first sealing portion abutting in the abutting groove to block the auxiliary pressure relief channel, and a gap is formed between the first sealing portion and the inner wall of the abutting groove.

4. The high-pressure fuel tank isolation valve for a hybrid vehicle according to claim 3, characterized in that: The first valve disc also includes a second sealing portion abutting against the bottom of the first chamber and the top of the abutting groove, and the second sealing portion is spaced apart with an outer sealing ring and an inner sealing ring abutting against the bottom of the first chamber and the top of the abutting groove respectively.

5. The high-pressure fuel tank isolation valve for a hybrid vehicle according to claim 1, characterized in that: A first step surface and a second step surface are formed at the bottom of the first chamber, the first step surface is away from the axis of the central channel and is arranged farther from the second chamber than the second step surface, and the first sealing surface is formed on the first step surface.

6. The high-pressure fuel tank isolation valve for a hybrid vehicle according to claim 2, characterized in that: Guide ribs are arranged at intervals on the inner wall of the central channel, and ends of the guide ribs are abutted against the outer wall of the second valve disc.

7. The high-pressure fuel tank isolation valve for a hybrid vehicle according to claim 6, characterized in that: The second valve disc includes a sealing ring, a limiting ring and a plurality of connecting strips connected between the sealing ring and the limiting ring at intervals along the circumference of the limiting ring. The sealing ring is inserted into the central channel and abuts against the guide rib. The auxiliary pressure relief channel is formed on the sealing ring, and the limiting ring abuts against the bottom of the guide rib.

8. The high-pressure fuel tank isolation valve for a hybrid vehicle according to claim 6, characterized in that: In the axial direction of the second chamber, a mounting hole is opened on the valve housing, a plug is installed 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.

9. The high-pressure fuel tank isolation valve for a hybrid vehicle according to claim 8, characterized in that: The guide rib forms an inclined surface at one end of the second cavity, and the inclined surface is arranged gradually approaching the axis of the central channel from the second cavity toward the first cavity.

10. The high pressure fuel tank isolation valve for a hybrid vehicle according to claim 9, characterized in that: The first chamber includes an upper chamber for accommodating the electromagnetic assembly and a lower chamber for communicating with the oil tank port, 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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