Injection valves, internal combustion engines, and fluid injection methods

Abstract

This application provides an injection valve, an internal combustion engine, and a fluid injection method. The injection valve includes an armature portion comprising a first armature and a second armature, the first armature and the second armature being detachably connected adjacent to each other in the axial direction. A first space and a second space are defined on opposite sides of the axial connection point of the first and second armatures. It also includes a first valve element and a second valve element disposed axially adjacent to it. The first valve element is connected to the armature portion, allowing it to move relative to the second valve element in the axial direction as the armature portion moves. An inlet region provides an inlet for fluid, and an outlet region provides an outlet for fluid. The inlet region and the outlet region are connected via the first valve element and the second valve element.

Description

Technical Field

[0001] This invention relates to injection valves, internal combustion engines, and fluid injection methods. Background Technology

[0002] Green fuel internal combustion engines, such as those using natural gas or ammonia, have lower energy density compared to traditional liquid fuels like diesel. Therefore, when higher engine power is required, high-flow-rate gas injection is demanded. The gas injection flow rate is directly related to the upstream and downstream pressure difference and also increases with the upstream pressure itself. When a large gas flow rate is required, the required upstream and downstream pressure difference is even greater, often leading to difficulty in valve opening. Generally, high-flow-rate injection is accompanied by a rapid increase in the valve's flow area, which in turn leads to an increase in the valve's characteristic dimensions. Therefore, the large structural dimensions of a high-flow-rate gas injection valve further amplify the difficulty of valve opening, affecting the rapid response time under high flow and pressure demands, and even leading to the risk of the valve failing to open.

[0003] To address this issue and mitigate the risk of valves failing to open under large pressure differentials, one technical approach is to employ a pressure-balanced injection valve. This valve utilizes an internal pressure balancing chamber to achieve overall pressure balance across the moving parts, offsetting the pressure difference. This allows the valve to maintain normal opening and closing even under large upstream and downstream pressure differences, significantly improving its response time. However, the inventors discovered that the main problems with current pressure-balanced valves are their complex internal structure, the high precision required for the mating surfaces of multiple parts, and the relatively cumbersome sealing methods. Furthermore, because pressure-balanced valves can continue operating even under larger pressure differentials, they pose a safety hazard: when the upstream and downstream pressure difference exceeds the designed safety range, or when the upstream pressure abnormally increases, the valve may fail to recognize the situation, leading to excessive air intake and potentially damaging the internal structure, thus creating a safety risk.

[0004] Another technical approach is to use a pressure-unbalanced injection valve. Compared to other types, pressure-unbalanced valves cannot open when the pressure difference between the upstream and downstream sides is too large, due to the pressure difference on the valve disc. Therefore, they effectively avoid the risk of excessive intake air and do not require additional engine automatic control strategies, thus offering advantages in safety and stability. However, the inventors discovered that if the gas injection valve is used in the diesel mode of a dual-fuel engine, it is also necessary to prevent excessive downstream pressure in the intake manifold during diesel operation, which could cause abnormal valve opening and lead to gas backflow. Furthermore, most existing pressure-unbalanced valves can only maintain pressure by providing a large pressure upstream, but this introduces other additional problems related to safety strategies. Summary of the Invention

[0005] In view of the problems existing in the background art, the purpose of this application is to provide an injection valve, an internal combustion engine and a fluid injection method that can easily switch between pressure-balanced and pressure-unbalanced valves.

[0006] In a first aspect, this application provides a jet valve, including an armature portion comprising a first armature and a second armature, the first armature and the second armature being detachably connected adjacent to each other in the axial direction; a first space and a second space defined on both sides of the axial connection point of the first armature and the second armature; a first valve element and a second valve element disposed axially adjacent to it; wherein the first valve element is connected to the armature portion, such that the first valve element can move with the armature portion, and the first valve element and the second valve element can move relative to each other in the axial direction; an inlet region providing an inlet for fluid; and an outlet region providing an outlet for fluid; the inlet region and the outlet region are connected by the first valve element and the second valve element, wherein... A first valve element is connected to the inlet region, and a second valve element is connected to the outlet region. The first armature has a first channel extending through its axial dimension, one end of which is connected to the second armature, and the other end is connected to the outlet region. The fluid injection valve has either a first structure or a second structure: in the first structure, the second armature has a second channel extending through its axial dimension, one end of which is connected to one end of the first channel, and the other end is connected to the second space, such that the second space is connected to the outlet region, and the first space and the second space are separated by an isolator; in the second structure, one end of the first channel is closed by the second armature, and the first space and the second space are connected.

[0007] In the technical solution of this application embodiment, the detachable connection between the first armature and the second armature, as well as the synergistic effect of the position and communication relationship of the armature part, the first valve element, the second valve element, and the inlet area and the outlet area, make it easy for the injection valve to switch between pressure balanced and pressure unbalanced valves.

[0008] In some embodiments, the fluid injection valve further includes a housing that provides receiving space to accommodate the armature portion, the second valve element, and the housing provides the inlet area and the outlet area.

[0009] In some embodiments, the housing has a first stepped structure that provides a limit on the stroke of the first valve element in axial movement.

[0010] In some embodiments, the first armature is detachably connected to the second armature at a first radial position, and the first armature has a mounting area at a second radial position for mounting a spacer, the second radial position being located radially peripheral to the first radial position.

[0011] In some embodiments, the second valve element has a third channel extending through its axial dimension; in the first configuration, the first channel, the second channel, and the third channel are connected such that the second space is connected to the outlet region.

[0012] In some embodiments, the fluid injection valve further includes a magnet that cooperates with the second armature to drive the armature portion to move axially.

[0013] In some embodiments, an elastic element is provided between the second armature and the magnet, with one end of the elastic element connected to the second armature and the other end connected to the magnet.

[0014] In some embodiments, the second channel and the elastic element are disposed at the center of the second armature.

[0015] In a second aspect, this application provides an internal combustion engine including a fluid injection valve as described in the first aspect.

[0016] Thirdly, this application provides a fluid injection method using a fluid injection valve as described in the first aspect, the injection method comprising: in a first injection mode, the fluid injection valve having a first structure; and in a second injection mode, the fluid injection valve having a second structure. Attached Figure Description

[0017] The above-described and other features, properties, and advantages of the present invention will become more apparent from the following description taken in conjunction with the accompanying drawings and embodiments, in which the same reference numerals always denote the same features. It should be noted that these drawings are merely illustrative and are not drawn to scale, and should not be construed as limiting the scope of protection actually claimed by the present invention, wherein:

[0018] Figure 1 This is a schematic diagram of the first structure of an embodiment of the injection valve.

[0019] Figure 2 This is a schematic diagram of the second structure of an embodiment of the injection valve.

[0020] Figure 3 This is a schematic diagram illustrating how to prevent the injection valve from opening when the backfire pressure difference is large, according to one embodiment.

[0021] Figure label:

[0022] 10 - Fluid ejection valve, 101 - First structure, 102 - Second structure;

[0023] 1-Armature section, 11-First armature, 111-First channel, 112-First radial position, 113-Second radial position, 12-Second armature, 121-Second channel, 110-First space, 120-Second space;

[0024] 21-First valve element, 22-Second valve element, 221-Third passage, 222-Seal;

[0025] 3-Imported areas;

[0026] 4-Export Area;

[0027] 5-Shell, 50-Accommodation space, 51-First step structure, 52-Second step structure;

[0028] 6-Isolator, 61-Diaphragm ring, 62-Compression washer;

[0029] 7-Magnet;

[0030] 8-Elastic element. Detailed Implementation

[0031] Reference will now be made in detail to various embodiments of the invention, examples of which are shown in the accompanying drawings and described below. Although the invention will be described in conjunction with exemplary embodiments, it should be understood that this specification is not intended to limit the invention to those exemplary embodiments. Rather, the invention is intended to cover not only these exemplary embodiments, but also various alternatives, modifications, equivalents, and other embodiments that may be included within the spirit and scope of the invention as defined by the appended claims.

[0032] Furthermore, this application uses specific terms to describe its embodiments. For example, "some embodiments" refers to a particular feature, structure, or characteristic associated with at least one embodiment of this application. Therefore, it should be emphasized and noted that "some embodiments" mentioned twice or more in different locations in this specification do not necessarily refer to the same embodiment. In addition, certain features, structures, or characteristics of some embodiments of this application can be appropriately combined.

[0033] Although the injection valve, internal combustion engine, and fluid injection method disclosed in the following embodiments are applicable to marine gas engines or diesel-gas dual-fuel engines, with the injection valve injecting gaseous fuels such as natural gas and ammonia, this application scenario is not limited. For example, it can be used in stationary generators, train internal combustion engines, etc. The solution in this invention can be applied wherever it is necessary to easily switch between pressure-balanced and pressure-unbalanced modes via the gas injection valve.

[0034] In existing green fuel internal combustion engines, or diesel-green fuel dual-fuel internal combustion engines, high-flow-rate injection of gaseous fuel is generally achieved using pressure-balanced injection valves. However, the inventors discovered that the main problems with current pressure-balanced injection valves are their complex internal structure, the high precision required for the mating surfaces of multiple parts, and their cumbersome sealing methods. Furthermore, because pressure-balanced valves can continue to operate even with larger pressure differences, this poses a safety hazard: when the upstream and downstream pressure difference exceeds the designed safety range, or when the upstream pressure abnormally increases, the valve cannot perform a safety identification, resulting in excessive air intake and even damage to the internal structure, creating a safety hazard. The main problem with pressure-unbalanced injection valves is that, if the gas injection valve is used in the diesel mode of a dual-fuel engine, it is also necessary to prevent excessive downstream pressure in the intake manifold during diesel operation, which could cause abnormal valve opening and lead to gas backflow. Moreover, most existing pressure-unbalanced valves can only maintain pressure by providing a larger pressure upstream, but this introduces other additional problems with safety strategies.

[0035] Based on the above findings, the inventors proposed an injection valve, an internal combustion engine, and a fluid injection method. Through the detachable connection between the first and second armatures, and the synergistic effect of the positions and connections of the armature, the first valve element, the second valve element, and the inlet and outlet regions, the injection valve can easily switch between pressure-balanced and pressure-unbalanced modes. This not only overcomes the shortcomings of pressure-balanced injection valves, such as complex internal structure, high machining precision requirements, and cumbersome sealing methods, but also facilitates the switching between pressure-balanced and unbalanced modes, enabling the injection valve to be applicable to various working scenarios.

[0036] refer to Figure 1 as well as Figure 2 As shown, in some embodiments, the injection valve 10 includes an armature portion 1, a valve element, an inlet region 3, and an outlet region 4.

[0037] The armature part 1 includes a first armature 11 and a second armature 12. The first armature 11 and the second armature 12 are detachably connected adjacent to each other in the axial direction. A first space 110 and a second space 120 are defined on both sides of the axial direction, with the connection point of the first armature 11 and the second armature 12 as the boundary.

[0038] The meaning of armature 1 is similar to that in the art, namely, a moving magnet that is attracted by a fixed electromagnet and forms a closed magnetic circuit with the electromagnet after movement.

[0039] The first armature 11 and the second armature 12 are detachably connected adjacently in the axial direction, wherein the axial direction Figure 1 , Figure 2The vertical direction is defined as "center" or "center" in the following description. While the vertical direction is synonymous with the axial direction, it is not a limitation. A detachable connection structure can be... Figure 1 as well as Figure 2 As shown, the first armature 11 is detachably connected to the second armature 12 at its first radial position 112. The detachable connection can be a threaded connection, that is, the first armature 11 provides an internal thread at its first radial position 112, and the second armature 12 provides a corresponding external thread. The two are detachably connected through a threaded connection structure.

[0040] The valve element includes a first valve element 21 and a second valve element 22 disposed axially adjacent to it. For example... Figure 1 as well as Figure 2 As shown, the connection structure between the first valve element 2 and the second valve element 22 can be a dynamic seal structure. The lower surface of the first valve element 21 is an annular perforation, which ensures a larger intake flow rate within a small lifting distance. The upper surface of the second valve element 22 is also an annular perforation, but its size and position differ from the annular perforation of the first valve element 21 and form an interlaced pattern, ensuring that the two annular perforations do not overlap geometrically. The center of the second valve element 22 is also a through hole. The specific structure of the first valve element 21 and the second valve element 22 can be a disc-shaped structure as shown in the figure, but is not limited to this.

[0041] The first valve element 21 is connected to the armature part 1, so that the first valve element 21 can move relative to the second valve element 22 in the axial direction as the armature part 1 moves. For example Figure 1 As shown, the first valve element 21 and the first armature 11 are connected by a threaded connection structure. The first valve element 21 provides an internal thread structure, and the first armature 11 provides an external thread. The two are connected by a threaded connection structure, so that the armature part 1 and the first valve element 21 form a structure that moves synchronously as a whole.

[0042] In some embodiments, the armature portion 1 can be moved by a magnet 7, such as an electromagnet. The magnet 7 cooperates with the second armature 12 to drive the armature portion 1 to move axially. For example, when the magnet 7 is energized, the second armature 7 moves upward, driving the first armature 11 connected to it, and driving the first valve element 21 connected to the first armature 11 to move upward. The second valve element 22 is generally fixed, such as... Figure 1 The first valve element 21 is fixed to the housing 5 and sealed to the inner wall of the housing 5 by a seal 222. Therefore, in some embodiments, the first valve element 21 may also be referred to as a movable valve element, and the second valve element 22 as a fixed valve element.

[0043] Inlet region 3 is used to provide the inlet for fluid, while outlet region 4 is used to provide the outlet for fluid. Inlet region 3 and outlet region 4 are connected by a first valve element 21 and a second valve element 22, wherein the first valve element 21 is connected to inlet region 3 and the second valve element 22 is connected to outlet region 4. The first armature 11 has a first channel 111 extending through its axial direction, one end of the first channel 111 is connected to the second armature 12, and the other end is connected to outlet region 4.

[0044] The fluid injection valve 10 has a first structure 101 or a second structure 102.

[0045] like Figure 1 As shown, when the fluid injection valve 10 is in the first structure 101, the second armature 12 has a second channel 121 that runs through its axial direction. One end of the second channel 121 is connected to one end of the first channel 111, and the other end is connected to the second space 120, so that the second space 120 is connected to the outlet region 4, and the first space 110 and the second space 120 are separated by the isolation member 6.

[0046] Preferably, in some embodiments, such as Figure 1 As shown, the isolation element 6 may include a diaphragm ring 61 and a compression washer 62. Specifically, the diaphragm ring 61 may be a central ring structure with an Ω-shaped cross-section, made of flexible material with good elastic deformation capability. The structure for mounting the isolation element 6 may involve a mounting area at a second radial position 113 of the first armature 11 for mounting the isolation element 6. The mounting area may be a groove structure, with the inner edge of the diaphragm ring 61 placed in the groove of the armature and the outer edge placed in the groove of the inner cavity surface of the housing 5, thereby forming two sealing surfaces that effectively isolate the gas in the upper and lower parts of the diaphragm ring 61, i.e., effectively isolate the first space 110 and the second space 120. The second radial position 113 may be located radially outside the first radial position 112, resulting in a compact arrangement.

[0047] like Figure 2 As shown, when the fluid injection valve 10 is in the second structure 102, one end of the first channel 111 is closed by the second armature 12, and the first space 110 and the second space 120 are connected. Specifically, when in the second structure 102, the isolator 6 is removed, and the second armature 12 is replaced with a structure that does not have the second channel 121.

[0048] It can be understood that the fluid injection valve 10 of the second structure 102 is different from that of the first structure 101 only in that the second armature 12 is replaced, the second armature 12 does not have the second channel 121, and the isolation member 6 is removed, while the rest of the structure is essentially the same.

[0049] It can be understood that when in the first structure 101, the injection valve is a pressure-balanced injection valve, while in the second structure 102, the injection valve is a pressure-unbalanced injection valve. The specific principle is as follows: When the coil is energized, the second armature 12 is subjected to an upward electromagnetic force by the magnet 7, which drives the entire first valve element 21 to move upward. At this time, the gaseous fuel enters from the inlet area 3 and passes through the annular gap generated by the relative movement of the first valve element 21 and the second valve element 22, providing the gas flow required by the outlet area 4, i.e., the downstream. When the power is off, the armature part 1 and the first valve element 21 will fall rapidly back due to the downward force of their own gravity, so that the lower surface of the first valve element 21 and the upper surface of the second valve element 22 are tightly attached together again. Since there is no overlap between the annular gaps, the air intake channel is isolated, and the injection valve is in the shut-off mode.

[0050] When in the first structure 101, the second armature 12, which has a second channel 121, is connected to the first armature 11. At this time, the air gap between the upper end face of the second armature 12 and the lower end face of the magnet 7 is connected to the downstream gas through a series of through-hole structures. Specifically, for example, it is connected through the second channel 121, the first channel 111, and the third channel 221 that penetrates the axial dimension of the second valve element 22, so that the second space 120 is connected to the outlet region 4. This causes the upper surface of the armature part 1 (i.e., the upper surface of the second armature 12) to be subjected to a downward pressure P2, while the lower surface of the armature (i.e., the lower surface of the first armature 11) is connected to the upstream air intake environment (i.e., the air intake region 3) and is subjected to an upward pressure P1. Due to the presence of the isolator 6, the pressure of the two parts is isolated from each other. At this time, the injection valve 10 can counteract the combined pressure difference between the upper and lower surfaces of the valve element (i.e., the pressure of the intake air on the upper surface of the first valve element 21 and the pressure of the downstream air on the lower surface of the second valve element 22, and the pressure difference between the two) through the combined pressure difference between the upper and lower surfaces of the armature part 1. Therefore, it can still work normally under a large pressure difference. The advantage of this mode is that it has a larger upper limit of injection capacity, and the valve can still maintain a fast response speed when the pressure difference is large.

[0051] When in the second structure 102, the second armature 12 (without the second channel 121) is connected to the first armature 11, and the isolator 6 is removed. At this time, the surface pressure on the upstream and downstream sides of the armature is the upstream pressure P1. This means the combined pressure difference force on the valve element can no longer be offset. Therefore, when the upstream and downstream pressure difference reaches a certain critical value, even with the electromagnetic coil energized, the injection valve 10 cannot open normally. The injection mode corresponding to the second structure 102 is mainly used when the diesel engine control system cannot incorporate a risk identification module for excessively high intake pressure, excessive pressure difference, and exceeding the safe range. In such cases, the balanced valve may cause flow exceeding limits or safety hazards. When the flow demand is not large and the requirement for upstream and downstream pressure difference is small, the pressure unbalanced mode offers greater safety and reliability.

[0052] Continue to refer to Figure 1 as well as Figure 2 As shown, in some embodiments, the fluid injection valve 10 may further include a housing 5, which provides a receiving space 50 to accommodate the armature portion 1, the second valve element 21, and the second valve element 22, and provides an inlet region 3 and an outlet region 4. Preferably, the housing 5 has a first stepped structure 51, which provides a limit to the stroke of the first valve element 21 in axial movement. Additionally, the housing 5 may also have a second stepped structure 52, which provides axial limitation for the installation of the second valve element 22. By using a stepped structure on the inner wall surface of the housing 5 to limit the displacement of corresponding components or provide an installation position, the arrangement of the injection valve becomes more compact and the structure simpler.

[0053] Continue to refer to Figure 1 As shown, in some embodiments, the fluid injection valve 10 structure may further include an elastic element 8 disposed between the second armature 12 and the magnet 7, with one end of the elastic element 8 connected to the second armature 12 and the other end connected to the magnet 7. The elastic element 8 is a spring. Specifically, a blind hole may be arranged in the center of the magnet 7, serving as the upper fixed end face of the elastic element 8 and strictly limiting the spring to move only in the vertical direction. The second armature 12 is correspondingly provided with a spring seat and a blind hole for the elastic element 8, serving as the lower fixed end face of the elastic element 8 to ensure that the axial position of the elastic element 8 coincides with the center position of the hole, thus ensuring the vertical movement path of the elastic element 8. Preferably, in addition to the blind hole arranged in the center of the magnet 7 and the blind hole arranged in the center of the second armature 12, the second channel 121 opened by the second armature 12, the first channel 111 opened by the first armature 11, and the third channel 221 opened by the second valve element 22 are all located in the center and extend along the axial direction, which can make the injection valve more responsive and the structure simple and compact.

[0054] refer to Figure 3As shown, the fluid injection valve 10 described in the above embodiments can also be equipped with the ability to prevent abnormal opening of the injection valve caused by backfire pressure differential. For example... Figure 3 As shown, when the downstream pressure can overcome the elastic force of the elastic element 8 and the weight of the valve element, since the second valve element 22 is not restricted in its up-and-down movement by the valve body shell and adopts a dynamic sealing form, the second valve element 22 will move closely to the first valve element 21 and remain closed until it reaches the limit position. When the upstream pressure rises again or the downstream pressure decreases, the second valve element 22 will return to its initial position under the action of the pressure difference, the weight of the first valve element 21, and the elastic force of the elastic element 8, without affecting the normal operation of the injection valve. This structure is particularly suitable for diesel mode in dual-fuel engines, where excessive air passage pressure can lead to an increased backfire pressure differential, resulting in abnormal valve opening. The solution described in the above embodiment effectively prevents this situation from occurring, avoiding the workload of judging and adjusting the valve operation from a safety strategy perspective, making the operation of the injection valve safer and more reliable.

[0055] In summary, the beneficial effects of the fluid injection valve 10 described in the above embodiments include, but are not limited to, the planar lift solenoid valve, which has a compact and simple structure, convenient replacement of pressure balanced and pressure unbalanced modes, and can effectively avoid the risk of abnormal valve opening caused by backfire pressure differential. Specifically, through the detachable connection between the first armature and the second armature, and the synergistic effect of the position and connection relationship of the armature part, the first valve element, the second valve element, and the inlet and outlet areas, the balanced / unbalanced modes share most of the components, and the mode conversion can be completed by simply installing and replacing some parts (changing the second armature with different structures and whether or not the isolator 6 is installed). In addition, the second valve element 22 adopts a dynamic sealing form, which ensures that the valve remains closed through its own movement adjustment under the condition of large backfire pressure differential, avoiding abnormal valve opening. Furthermore, the injection valve 10 can meet various experimental operating conditions of gas injection valves, and has the characteristics of large flow rate, simple structure, and high reliability, improving the adaptability of gas injection valves.

[0056] Another aspect of the present invention provides an internal combustion engine including the fluid injection valve 10 described in the above embodiments. As mentioned above, the beneficial effect is that, when the internal combustion engine is used in various modes, such as when a larger injection capacity is required and the valve can maintain a fast response speed even with a large pressure difference, the first structure 101 of the injection valve 10 can be used. When the diesel engine control system cannot incorporate a risk identification module for excessively high intake pressure, excessively large pressure difference exceeding the safe range, and the flow requirement is not large and the pressure difference requirement across the valve is small, the second structure 102 of the injection valve 10 can be used. Furthermore, switching between these two structures is relatively convenient. At the same time, the structure of the injection valve 10 itself is relatively simple and reliable, resulting in good operational reliability of the internal combustion engine.

[0057] Another aspect of the present invention provides a fluid injection method, such as a gaseous fuel injection valve method for an internal combustion engine, employing the fluid injection valve 10 described in the above embodiments. As mentioned above, in a first injection mode, the fluid injection valve 10 has a first structure 101; in a second injection mode, the fluid injection valve 10 has a second structure 102. This allows for convenient switching between modes to accommodate injection scenarios with different pressure requirements.

[0058] While the present invention has been disclosed above with reference to preferred embodiments, it is not intended to limit the invention. Any variations and modifications can be made by those skilled in the art without departing from the spirit and scope of the invention. Therefore, any modifications, equivalent changes, and alterations made to the above embodiments based on the technical essence of the present invention, without departing from the scope of the invention, fall within the protection scope defined by the claims of the present invention.

Claims

1. A fluid injection valve (10), characterized in that, include: The armature part (1) includes a first armature (11) and a second armature (12). The first armature (11) and the second armature (12) are detachably connected adjacent to each other in the axial direction. A first space (110) and a second space (120) are defined on both sides of the axial direction, with the connection point of the first armature (11) and the second armature (12) as the boundary. A first valve element (21) and a second valve element (22) disposed axially adjacent thereto; The first valve element (21) is connected to the armature part (1), so that the first valve element (21) can move with the armature part (1), and the first valve element (21) and the second valve element (22) can move relative to each other in the axial direction. Import area (3) provides the inlet for fluid; The outlet area (4) provides an outlet for the fluid; The inlet area (3) and the outlet area (4) are connected by the first valve element (21) and the second valve element (22), wherein the first valve element (21) is connected to the inlet area (3) and the second valve element (22) is connected to the outlet area (4). The first armature (11) has a first channel (111) extending through its axial dimension, one end of the first channel (111) is connected to the second armature (12), and the second valve element (22) has a third channel (221) extending through its axial dimension. The other end of the first channel (111) is connected to the outlet area (4) through the third channel (221). The fluid injection valve (10) has a first structure (101) or a second structure (102): In the first structure (101), the second armature (12) has a second channel (121) extending through its axial dimension, one end of the second channel (121) is connected to one end of the first channel (111), and the other end is connected to the second space (120), such that the second space (120) is connected to the outlet region (4), and the first space (110) and the second space (120) are separated by a separator (6); In the second structure (102), the second armature (12) is not provided with the second channel (121), one end of the first channel (111) is closed by the second armature (12), and the first space (110) and the second space (120) are directly connected without the isolation member (6); By replacing the second armature (12) with different structures and whether or not to install the isolator (6), the fluid jet valve (10) can switch between the corresponding modes of the first structure (101) and the second structure (102).

2. The fluid injection valve (10) as described in claim 1, characterized in that, The fluid injection valve (10) also includes a housing (5) that provides a receiving space (50) to receive the armature (1), the first valve element (21), the second valve element (22), and the housing (5) provides the inlet area (3) and the outlet area (4).

3. The fluid injection valve (10) as described in claim 2, characterized in that, The housing (5) has a first stepped structure (51) that provides a limit on the stroke of the first valve element (21) in the axial direction.

4. The fluid injection valve (10) as claimed in claim 1, characterized in that, The first armature (11) is detachably connected to the second armature (12) at its first radial position (112), and the first armature (11) has an installation area at its second radial position (113) for installing the separator (6), and the second radial position (113) is located on the radial periphery of the first radial position (112).

5. The fluid injection valve (10) as claimed in claim 1, characterized in that, In the first structure (101), the first channel (111), the second channel (121), and the third channel (221) are connected, so that the second space (120) is connected to the exit area (4).

6. The fluid injection valve (10) as claimed in claim 1, characterized in that, The fluid injection valve (10) also includes a magnet (7), which cooperates with the second armature (12) to drive the armature part (1) to move axially.

7. The fluid injection valve (10) as claimed in claim 6, characterized in that, An elastic element (8) is provided between the second armature (12) and the magnet (7), with one end of the elastic element (8) connected to the second armature (12) and the other end connected to the magnet (7).

8. The fluid injection valve (10) as claimed in claim 7, characterized in that, In the first structure (101), the second channel (121) and the elastic element (8) are located at the center of the second armature (12).

9. An internal combustion engine, characterized in that, Includes the fluid injection valve (10) as described in any one of claims 1-8.

10. A fluid jetting method, characterized in that, The injection method, employing the fluid injection valve (10) as described in any one of claims 1-8, comprises: In the first injection mode, the fluid injection valve (10) has a first structure (101). In the second injection mode, the fluid injection valve (10) has a second structure (102).

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