Single electronic control high-pressure pump suitable for easy-to-vaporize clean fuel

Abstract

The invention relates to a single electronic control high-pressure pump suitable for easy-to-vaporize clean fuel. A pump cover is mounted at the upper part of a pump body; the discharging valve assembly is fixed to the upper portion of the pump cover. The bypass valve assembly is mounted in a horizontal mounting hole of the pump cover; the electromagnetic valve assembly is connected with the bypass valve, so that the electromagnetic valve assembly can drive the bypass valve to reciprocate left and right; the plunger and barrel assembly is mounted in a vertical mounting hole of the pump body; the feeding valve assembly is installed on the upper portion of the plunger and barrel assembly and integrated in the plunger cavity. The air inlet valve assembly is a one-way valve and is mounted on the pump body; the plunger spring, the spring seat and the guide piston assembly are sequentially mounted in a vertical mounting hole of the pump body; the guide piston assembly reciprocates up and down to drive the plunger to reciprocate up and down. The structure can adapt to the characteristics of methanol, ammonia, dimethyl ether and other clean fuels, overcomes the technical difficulties of vaporization, frictional wear, safety design and the like, and meets the development requirements of engines.

Description

Technical Field

[0001] This application relates to the field of engines, specifically a single-unit electronically controlled high-pressure pump adapted to easily vaporized clean fuels. Background Technology

[0002] The low-carbon / zero-carbon transformation of the fuel injection system, a core component of marine propulsion systems, has become a major focus of the global shipping industry. Methanol, ammonia, and dimethyl ether, with their excellent fuel properties and cost advantages from large-scale production, have become the most promising green and clean fuels at present. Some countries have already pioneered the engineering application of various green fuel injection systems, such as the G95ME-LGIM methanol engine and the W25A ammonia fuel engine.

[0003] The high-pressure pump is a key component of the engine fuel injection system, and its performance directly affects the engine's operating condition. The development of high-pressure pumps for clean fuels such as methanol, ammonia, and dimethyl ether faces numerous technical challenges, including: the fuel's easy vaporization, which can lead to cavitation and vapor lock in the high-pressure pump; the fuel's low viscosity, which can cause severe friction and wear on moving parts; the fuel's ability to contaminate lubricating oil, causing it to deteriorate and fail; the fuel's toxicity, requiring high safety protection for the high-pressure pump; and the fuel's corrosiveness, which can easily corrode and damage parts, especially solenoid valves.

[0004] Therefore, existing engine high-pressure pumps are not suitable for directly using fuels such as methanol, ammonia, and dimethyl ether. Technical research is needed to develop high-pressure pumps that are adapted to the characteristics of methanol, ammonia, and dimethyl ether fuels. Summary of the Invention

[0005] To adapt to the characteristics of fuels such as methanol, ammonia, and dimethyl ether, and to overcome technical challenges such as gas-liquid phase change conversion, friction and wear, safety design, and corrosion of solenoid valves, this invention provides a single-unit electronically controlled high-pressure pump suitable for easily vaporized clean fuels. It is well-suited for clean fuels such as methanol, ammonia, and dimethyl ether, and can be applied to both electronically controlled single-unit pump fuel injection systems and electronically controlled high-pressure common rail systems. The single-unit design facilitates maintenance or replacement, and offers good safety, reliability, and maintainability.

[0006] The technical solution of this invention is as follows: A single-unit electrically controlled high-pressure pump adapted to easily vaporized clean fuels includes a pump body 1, a pump cover 2 mounted on the upper part of the pump body 1, a plunger assembly 5 housed within the pump body 1, and a feed valve assembly 6. The plunger assembly 5 has a plunger cavity E1 formed within it. The single-unit electrically controlled high-pressure pump further includes: Bypass valve assembly 4, which is integrated on the pump cover 2; The discharge valve assembly 4, wherein the discharge valve assembly 3 is mounted on the pump cover 2 and is connected to the high-pressure fuel outlet of the bypass valve assembly 4; The feed valve assembly 6 is assembled between the plunger assembly 5 and the pump cover 2, and the inner hole of the feed valve assembly 6 is directly connected to the plunger cavity E1. The pump body 1, pump cover 2, plunger assembly 5 and feed valve assembly 6 together constitute a low-pressure fuel supply path for supplying low-pressure fuel into the plunger chamber E1. No regulating valve for adjusting the feed flow rate is provided between the low-pressure fuel inlet A2 of the pump body 1 and the feed valve assembly 6, so that the minimum fuel pressure in the plunger chamber E1 is greater than the saturated vapor pressure of the fuel. The feed valve assembly 6, the pump cover 2, and the bypass valve assembly 4 together constitute a low-pressure fuel circulation path that circulates the low-pressure fuel in the plunger chamber E1 to the fuel tank. The feed valve assembly 6, the pump cover 2, the bypass valve assembly 4, and the discharge valve assembly 4 together constitute a high-pressure fuel supply path that exports the high-pressure fuel obtained by pressurizing the plunger cavity E1 to the target device.

[0007] Preferably, the plunger assembly 5 includes: a plunger 51 and a plunger sleeve 52, wherein the plunger sleeve 52 is assembled inside the pump body 1, and the plunger 51 is slidably assembled inside the plunger sleeve 52. A chamber E2 is formed inside the plunger sleeve 52 on the side facing the pump cover 2. The feed valve assembly 6 is arranged inside the chamber E2. A portion of the pump cover 2 extends into the chamber E2 and may or may not contact the feed valve assembly 6. The plunger sleeve 52 is provided with a second low-pressure fuel ring groove E4, and the pump cover 2 is provided with a first fuel channel. The second low-pressure fuel ring groove E4 connects the low-pressure fuel inlet A2 of the pump body 1 and the first fuel channel through a channel. The feed valve assembly 6, the plunger sleeve 52 and the plunger 51 form the plunger cavity E1, and the feed valve assembly 6 is provided with a third fuel hole F1, which communicates with the plunger cavity E1. The low-pressure fuel supply path is formed by the fuel passage gap between the low-pressure fuel inlet A2, the second low-pressure fuel annular groove E4, the first fuel channel, the pump cover 2 and the feed valve assembly 6, and the third fuel hole F1.

[0008] Preferably, an air intake valve assembly 7 is installed on the pump body 1; The intake valve assembly 7, the plunger assembly 5, and the feed valve assembly 6 together constitute an inert gas purging path that blows inert gas into the plunger cavity E1. By adjusting the bypass valve assembly 4, the inert gas in the plunger chamber E1 is purged outward through the low-pressure fuel circulation path or the high-pressure fuel supply path.

[0009] Preferably, the bypass valve assembly 4 includes: a bypass valve sleeve 41, a bypass valve 42, a baffle 43, a bypass valve spring 44, and a solenoid valve assembly 45; The bypass valve sleeve 41, the bypass valve 42, the baffle 43 and the bypass valve spring 44 are all assembled inside the pump cover 2; The solenoid valve assembly 45 is driven to connect with the bypass valve 42 to control the reciprocating movement of the bypass valve 42 within the bypass valve sleeve central hole D1 of the bypass valve sleeve 41. The baffle 43 contacts the bypass valve sleeve 41 to limit the maximum stroke of the bypass valve 42; The bypass valve sleeve 41 and the bypass valve 42 define a high-pressure fuel chamber D11 and a return fuel chamber D12. The bypass valve 42 and the bypass valve sleeve 41 directly form a valve port through a pair of sealing cone surfaces. When the solenoid valve assembly 45 is energized, it drives the bypass valve 42 to move toward the opening valve port, and the fuel flow path between the high-pressure fuel chamber D11 and the return fuel chamber D12 is opened, so that the low-pressure fuel circulation path is formed. When the solenoid valve assembly 45 is de-energized, the bypass valve spring 44 drives the bypass valve 42 to move toward the closed valve port, and the fuel flow path between the high-pressure fuel chamber D11 and the return fuel chamber D12 is shut off, so that the high-pressure fuel supply path is formed.

[0010] Preferably, a fuel return annular groove D4 is formed on the outer end face of the bypass valve sleeve 41, and the fuel return annular groove D4 and the return fuel chamber D12 are connected through a plurality of fuel holes evenly distributed along the circumferential direction on the bypass valve sleeve 41; the fuel return annular groove D4 is also connected to the low-pressure fuel return outlet B2 provided on the pump cover 2; When the solenoid valve assembly 45 is energized, the plunger chamber E1, the third fuel port F1, the high-pressure fuel chamber D11, the return fuel chamber D12, and the low-pressure fuel return outlet B2 together form the low-pressure fuel circulation path.

[0011] Preferably, the discharge valve assembly 3 includes: a discharge valve head 31, a limit disc 32, and a discharge valve 33; The discharge valve head 31 is provided with a high-pressure fuel outlet C1 that runs through the axial direction and a limit disc mounting hole C4 located upstream of the high-pressure fuel outlet C1 and coaxially connected thereto. The limiting disc 32 is fixed in the limiting disc mounting hole C4. The disc body of the limiting disc 32 is provided with a second fuel hole C5 that is axially connected to the high-pressure fuel outlet C1. The large end face of the limiting disc 32 facing the discharge valve 33 constitutes the maximum stroke limiting surface of the discharge valve 33. The discharge valve 33 is slidably disposed in the pump cover mounting hole B9 of the pump cover 2 and located on the upstream side of the limit plate 32. A fuel tank C6 is provided on the outer peripheral wall of the discharge valve 33. When the discharge valve 33 is opened, the high-pressure fuel in the high-pressure fuel chamber D11 is introduced into the high-pressure fuel outlet C1 through the fuel tank C6 and the second fuel hole C5; When the pressure of the high-pressure fuel in the high-pressure fuel chamber D11 drops, the reverse thrust provided by the residual high-pressure fuel in the high-pressure fuel outlet C1 acts on the discharge valve 33 through the second fuel hole C5, realizing the self-sealing and self-resetting of the discharge valve 33, and completing the springless opening and closing of the discharge valve 33. When the solenoid valve assembly 45 is not energized, the plunger chamber E1, the third fuel hole F1, the high-pressure fuel chamber D11, the fuel tank C6, the second fuel hole C5, and the high-pressure fuel outlet C1 together form the high-pressure fuel supply path.

[0012] Preferably, the pump body 1 is provided with a pressure balance hole A5, which is connected to the chamber where the plunger spring is located.

[0013] Preferably, the pump body 1 is provided with a first sealing oil inlet A3; The plunger sleeve 52 of the plunger assembly 5 has a plunger assembly sealing oil passage K that communicates with the first sealing oil inlet A3, which is used to supply sealing oil to the mating gap between the plunger 51 and the plunger sleeve 52. The sealing oil pressure in the sealing oil passage K of the plunger assembly is higher than the leakage fuel pressure at the plunger assembly 5, so as to block the leakage fuel in the plunger assembly 5.

[0014] Preferably, the intake valve assembly 7 is a one-way valve that allows an external inert gas source to flow into the plunger chamber E1 and prevents fuel from flowing back into the inert gas source.

[0015] Preferably, the single-unit electrically controlled high-pressure pump adapted to easily vaporized clean fuels is suitable for any one of methanol, ammonia, and dimethyl ether.

[0016] The beneficial effects of this invention are as follows: 1. No bypass valve, proportional valve or other regulating valve is installed between the low-pressure fuel inlet and the plunger cavity, so that the low-pressure fuel can be directly injected into the plunger cavity, which greatly reduces the pressure loss caused by valve throttling; the feed valve assembly is directly integrated into the plunger cavity, and there is no need for the feed valve assembly and the plunger cavity to be connected through a channel, so that the clearance volume of the plunger cavity is smaller, which helps to reduce the pressure loss of low-pressure fuel, avoid fuel vaporization, and prevent problems such as cavitation and gas lock.

[0017] 2. A unique fuel path was designed for the high-pressure pump containing easily vaporizable clean fuel, including a low-pressure fuel circulation path and a high-pressure fuel supply path. During the high-pressure fuel supply interval, low-pressure fuel enters the plunger chamber of the high-pressure pump from the fuel tank through the low-pressure fuel supply path, then flows out of the high-pressure pump through the low-pressure fuel circulation path, and finally returns to the fuel tank. During the high-pressure fuel supply period, the low-pressure fuel is pressurized through the high-pressure fuel supply path and then flows out of the high-pressure pump. This low-pressure fuel circulation path design ensures that the low-pressure fuel circulates at a pressure greater than the fuel's saturated vapor pressure, allowing the fuel to fill the plunger chamber while carrying away heat from the plunger chamber, reducing the internal temperature of the high-pressure pump, ensuring that the fuel in the high-pressure pump remains in a liquid state, and avoiding problems such as cavitation and vapor lock.

[0018] 3. A sealing oil system was designed, consisting of a plunger assembly sealing oil passage, a first bypass valve sealing oil passage, and a second bypass valve sealing oil passage. This system lubricates the assembly and seals the gap between the assemblies. Under normal circumstances, fuel leaking from the high-pressure pump assembly gap will flow into the low-pressure fuel passage inside the high-pressure pump, thus achieving zero fuel leakage. The design of the first and second bypass valve sealing oil passages physically isolates the fuel from the solenoid valve using sealing oil, preventing fuel corrosion of the solenoid valve.

[0019] 4. A leakage sealing oil collection channel was designed, which can collect the sealing oil leaking from the bypass valve, balance the air pressure between the chamber where the bypass valve spring is located and the bypass valve orifice, and connect with the external atmosphere to avoid the formation of a closed space that would affect the movement of the bypass valve.

[0020] 5. An inert gas purging first flow channel and an inert gas purging second flow channel were designed, enabling the high-pressure pump to have an inert gas purging function. This function can remove residual fuel through purging, making the high-pressure pump easier to inspect and maintain, and greatly improving safety.

[0021] 6. The discharge valve assembly adopts a springless design, which solves the problem of possible spring breakage under high-frequency movement conditions, reduces the number of parts, simplifies the structure, and improves the reliability and service life of the discharge valve assembly.

[0022] 7. A multi-stage leak-proof structure consisting of a third low-pressure fuel ring groove, a sixth sealing oil ring groove, a ninth sealing ring groove, and a first sealing ring groove is designed to prevent fuel leakage to the bottom of the high-pressure pump. Because the bottom of the high-pressure pump is immersed in an oil chamber containing a large amount of lubricating oil after installation on the engine, this design prevents fuel from contaminating the lubricating oil.

[0023] 8. A pressure balance hole is designed to connect the chamber containing the plunger spring to the external space, balancing the internal and external air pressures and preventing it from becoming a sealed chamber that could affect the movement of the guide piston assembly. Furthermore, if the seal in the plunger assembly gap fails and an abnormal leak occurs, the leaked fuel and sealing oil can be collected and removed through the pressure balance hole, preventing accumulation in the chamber containing the plunger spring.

[0024] 9. This high-pressure pump can be used in both electronically controlled unit pump fuel injection systems and electronically controlled high-pressure common rail systems, offering a wide range of applications. This high-pressure pump can be connected to a mechanical injector via a high-pressure pipe to form an electronically controlled unit pump fuel injection system; it can also be connected to a common rail and electronically controlled injectors via a high-pressure pipe to form an electronically controlled high-pressure common rail system. Considering the easily vaporized, low-viscosity, and corrosive characteristics of clean fuels, this high-pressure pump adopts a unit pump design rather than a combined pump design. If one pump fails, the other pumps can still maintain engine operation, while also facilitating maintenance or replacement. Attached Figure Description

[0025] The present invention will be further described below with reference to the accompanying drawings and embodiments: Figure 1 This is a schematic diagram of the structure of the electrically controlled high-pressure pump in the embodiments of this application; Figure 2 This is a schematic diagram of the structure of the electrically controlled high-pressure pump in the embodiments of this application; Figure 3 This is a schematic diagram of the pump body in an embodiment of this application; Figure 4 This is a schematic diagram of the pump body in an embodiment of this application; Figure 5 This is a schematic diagram of the pump cover structure in an embodiment of this application; Figure 6 This is a schematic diagram of the pump cover structure in an embodiment of this application; Figure 7 This is a schematic diagram of the structure of the discharge valve assembly in the embodiments of this application; Figure 8 This is a schematic diagram of the bypass valve assembly in an embodiment of this application; Figure 9 This is a schematic diagram of the bypass valve sleeve in an embodiment of this application; Figure 10This is a schematic diagram of the bypass valve in an embodiment of this application; Figure 11 This is a schematic diagram of the baffle structure in an embodiment of this application; Figure 12 This is a schematic diagram of the plunger assembly in the embodiments of this application; Figure 13 This is a schematic diagram of the feed valve assembly in an embodiment of this application; Figure 14 This is a schematic diagram of the intake valve assembly in an embodiment of this application.

[0026] Explanation of key figure labels: 1-Pump body; 2-Pump cover; 3-Discharge valve assembly; 31-Discharge connector; 32-Stroke limit disc; 33-Discharge valve; 4-Bypass valve assembly; 41-Bypass valve sleeve; 42-Bypass valve; 43-Baffle; 44-Bypass valve spring; 45-Solenoid valve assembly; 5-Plunger assembly; 51-Plunger; 52-Plunger sleeve; 6-Infeed valve assembly; 61-Infeed valve; 62-Infeed valve spring; 63-Lower spring seat; 7-Intake valve assembly; 71-Intake valve sleeve; 72-Intake valve; 73-Intake valve spring; 8-Guide piston assembly; A1 - Vertical mounting hole for pump body; A2 - Low-pressure fuel inlet; A3 - First sealing oil inlet; A4 - Lubricating oil inlet; A5 - Pressure balance hole; A6 - First sealing ring groove; A7 - Pump body mounting hole; B1 - Horizontal mounting hole for pump cover; B2 - Low-pressure fuel return outlet; B3 - Second sealing oil inlet; B4 - Second sealing ring groove; B5 - First low-pressure fuel ring groove; B6 - First fuel hole; B7 - First sealing boss; B8 - Second sealing boss; B9 - Pump cover mounting hole; B10 - Abnormal leakage fuel collection ring groove. C1 - High-pressure fuel outlet; C2 - Abnormal leakage fuel collection hole; C3 - Third sealing ring groove; C4 - Throttle plate mounting hole; C5 - Second fuel hole; C6 - Fuel tank; D1 - Bypass valve sleeve bore; D2 - First sealing oil ring groove; D3 - Second sealing oil ring groove; D4 - Fuel return ring groove; D5 - First high-pressure fuel ring groove; D6 - First sealing cone surface; D7 - Bypass valve bore; D8 - Third sealing oil ring groove; D9 - Second high-pressure fuel ring groove; D10 - Second sealing cone surface; D11 - High-pressure fuel chamber; D12 - Return fuel chamber; D13 - Baffle bore; D14 - Fourth sealing oil ring groove; D15 - Leakage oil collection ring groove; D16 - Fourth sealing ring groove; D17 - Leakage oil outlet; D18 - Fifth sealing oil ring groove; E1 - Plunger cavity; E2 - Chamber; E3 - Fifth sealing ring groove; E4 - Second low-pressure fuel ring groove; E5 - Sixth sealing ring groove; E6 - Seventh sealing ring groove; E7 - Eighth sealing ring groove; E8 - Low-pressure fuel cavity; E9 - Sealing oil cavity; E10 - Ninth sealing ring groove; E11 - Sixth sealing oil ring groove; E12 - Third low-pressure fuel ring groove; F1 - Third fuel port; F2 - Middle hole of lower spring seat; G1 - Air inlet; G2 - Air inlet valve mounting hole; G3 - Air inlet valve spring mounting hole; H - Low-pressure fuel circulation path; I - High-pressure fuel supply path; J - Internal circulation channel for leaking fuel in the assembly; K - Piston assembly sealing oil passage; L - First sealing oil passage for bypass valve; M - Second sealing oil passage for bypass valve; N - Leaking sealing oil collection channel; O - First inert gas purging path; P - Second inert gas purging path. Detailed Implementation

[0027] The structure and operation of the present invention will be further described in detail below with reference to the accompanying drawings and embodiments.

[0028] It should be noted that, unless otherwise specified, the embodiments and features described in the present invention can be combined with each other. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout.

[0029] In the description of this invention, it should be understood that the terms "upper", "lower", "left", "right", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0030] like Figure 1 and Figure 2 As shown, a single-unit electrically controlled high-pressure pump adapted to easily vaporized clean fuels includes: pump body 1, pump cover 2, discharge valve assembly 3, bypass valve assembly 4, plunger assembly 5, feed valve assembly 6, intake valve assembly 7, plunger spring, spring disc, and guide piston assembly 8.

[0031] The pump body 1, pump cover 2, plunger assembly 5 and feed valve assembly 6 together constitute a low-pressure fuel supply path for supplying low-pressure fuel into the plunger chamber E1. No regulating valve for adjusting the feed flow rate is provided between the low-pressure fuel inlet A2 of the pump body 1 and the feed valve assembly 6, so that the minimum fuel pressure in the plunger chamber E1 is greater than the saturated vapor pressure of the fuel. The feed valve assembly 6, the pump cover 2, and the bypass valve assembly 4 together constitute a low-pressure fuel circulation path that circulates the low-pressure fuel in the plunger chamber E1 to the fuel tank. The feed valve assembly 6, the pump cover 2, the bypass valve assembly 4, and the discharge valve assembly 4 together constitute a high-pressure fuel supply path that exports the high-pressure fuel obtained by pressurizing the plunger cavity E1 to the target device.

[0032] Traditional fuel pumps involve complex flow paths and regulating valves before low-pressure fuel enters the plunger chamber, resulting in throttling losses and dead zones. This application eliminates the regulating valve between the low-pressure fuel inlet A2 and the plunger chamber E1, significantly reducing flow resistance and pressure loss. This allows fuel to enter the plunger chamber E1 at a higher pressure. Furthermore, continuous fuel circulation removes heat from critical areas like the plunger chamber E1, preventing localized high temperatures that could lead to increased saturated vapor pressure and further enhancing the anti-vaporization effect.

[0033] During the non-injection phase, the low-pressure fuel circulation path allows a large amount of low-temperature fuel to continuously flow through the pump body (including the plunger chamber E1), forming an active cooling system. This not only effectively suppresses the temperature rise of the pump body 1 caused by engine heat conduction and component friction, but also dissipates compression heat in a timely manner, maintaining the high-pressure pump at a low operating temperature, thereby reducing the risk of vaporization caused by temperature rise.

[0034] When injection is required, a high-pressure fuel supply path is established. Because the aforementioned measures ensure that the plunger chamber E1 is filled with pure liquid fuel, each pressurization stroke of the plunger 51 efficiently transfers energy to the fuel without being buffered by compressible air bubbles. This directly results in higher volumetric efficiency, more precise injection quantity control, and more stable outlet pressure, ensuring optimized engine combustion.

[0035] Reference Figure 1 and Figure 2 Pump cover 2 is installed on the upper part of pump body 1; discharge valve assembly 3 is fixed to the upper part of pump cover 2 by screws; bypass valve assembly 4 is integrated on pump cover 2; plunger assembly 5 is installed inside pump body 1; plunger assembly 5 is designed with plunger cavity E1, and plunger assembly 5 and pump body 1 cooperate to form low pressure fuel cavity E8 and sealing oil cavity E9.

[0036] The feed valve assembly 6 is installed on the upper part of the plunger assembly 5 and is directly integrated into the plunger cavity E1, so that the feed valve assembly 6 and the plunger cavity E1 do not need to be connected through a channel, reducing the clearance volume of the plunger cavity E1; the pump cover 2, the plunger assembly 5, the feed valve assembly 6 and the pump body 1 are connected as one piece by screws; the air intake valve assembly 7 installed on the pump body 1 is a one-way valve, so that the fluid can only flow into the high-pressure pump through the one-way valve and cannot flow out of the high-pressure pump in the opposite direction; the plunger spring, the spring seat and the guide piston assembly 8 are installed in the pump body 1 in sequence, and the plunger 51, the spring seat and the guide piston assembly 8 are connected as one piece by screws, so that when the guide piston assembly 8 moves up and down, it can drive the plunger 51 to move up and down.

[0037] like Figure 3 and 4 As shown, the pump body 1 is designed with a vertical mounting hole A1, a low-pressure fuel inlet A2, a first sealing oil inlet A3, a lubricating oil inlet A4, a pressure balance hole A5, a first sealing ring groove A6, and a pump body mounting hole A7 that can accommodate the intake valve assembly 7; the pressure balance hole A5 is connected to the chamber where the plunger spring is located to balance the internal and external air pressure and avoid becoming a closed chamber, which would affect the movement of the guide piston assembly 8.

[0038] Combination Figure 1 and Figure 3 The vertical mounting hole A1 is located inside the pump body 1 and is used to install the plunger assembly 5, the plunger spring, the spring disc and the guide piston assembly 8 from top to bottom.

[0039] Combination Figure 3 and Figure 4 The low-pressure fuel inlet A2 and the pump body mounting hole A7 are located on the radial side of the pump body 1, and are connected to the vertical mounting hole A1 through a channel on the pump body 1. The sealing oil inlet A3 is also located on the radial side of the pump body 1, and is connected to the vertical mounting hole A1 through a channel on the pump body 1. The lubricating oil inlet A4 is located on the radial side of the pump body 1, below the sealing oil inlet A3, and is connected to the vertical mounting hole A1 through a channel on the pump body 1 for introducing lubricating oil. The air pressure balance hole A5 is located on the radial side of the pump body 1, and is connected to the vertical mounting hole A1 through a channel on the pump body 1. The first sealing ring groove A6 is used to install the sealing ring.

[0040] like Figure 5 and Figure 6As shown, the pump cover 2 is designed with a horizontal mounting hole B1, a low-pressure fuel return outlet B2, a second sealing oil inlet B3, a second sealing ring groove B4, a first low-pressure fuel ring groove B5, several first fuel holes B6 that are connected to the first low-pressure fuel ring groove B5 and are evenly distributed along the circumference, a first sealing boss B7, a second sealing boss B8, and a pump cover mounting hole B9 that can accommodate the discharge valve assembly 3; an abnormal leakage fuel collection ring groove B10 is formed between the first sealing boss B7 and the second sealing boss B8.

[0041] The first low-pressure fuel annular groove B5 and the first fuel hole B6 together constitute the fuel passage.

[0042] like Figure 7 As shown in this embodiment, the discharge valve assembly 3 adopts a springless design. The discharge valve assembly 3 specifically includes: a discharge connector 31, a stroke limiting disc 32, and a discharge valve 33. The large end face of the stroke limiting disc 32 is used to limit the maximum stroke of the discharge valve 33. The discharge connector 31 is provided with a high-pressure fuel outlet C1, an abnormal leakage fuel collection hole C2 connected to the abnormal leakage fuel collection ring groove B10, a third sealing ring groove C3, and a stroke limiting disc mounting hole C4 capable of accommodating the stroke limiting disc 32. A second fuel hole C5 is designed on the stroke limiting disc 32. The discharge valve 33 is designed with several fuel grooves C6 evenly distributed along the circumference. These fuel grooves C6 are connected to the second fuel hole C5, which is connected to the high-pressure fuel outlet C1. The high-pressure fuel outlet C1 is connected to the second fuel hole C5 on the pump cover 2 through a channel.

[0043] Among them, the limit plate 32 is assembled in the limit plate mounting hole C4, and the discharge valve 33 is installed in the pump cover mounting hole B9; the discharge valve 33 and the pump cover mounting hole B9 form a conical surface fit.

[0044] like Figures 8-11 As shown, the bypass valve assembly 4 includes: a bypass valve sleeve 41, a bypass valve 42, a baffle 43, a bypass valve spring 44, and a solenoid valve assembly 45.

[0045] The bypass valve sleeve 41 is designed with a central hole D1 that can accommodate the bypass valve 42 and the baffle 43; the bypass valve sleeve 41 and the bypass valve 42 cooperate to form a precision pair. The solenoid valve assembly 45 is connected to the bypass valve 42 by screws, so that the solenoid valve assembly 45 can drive the bypass valve 42 to reciprocate left and right, and the small end face of the baffle 43 limits the maximum stroke of the bypass valve 42.

[0046] Reference Figures 8-11The outer surface of the bypass valve sleeve 41 is designed with a first sealing oil ring groove D2, a second sealing oil ring groove D3, and a fuel return ring groove D4; the first sealing oil ring groove D2 and the second sealing oil ring groove D3 are respectively connected to the second sealing oil inlet B3 through channels; the fuel return ring groove D4 is connected to the low-pressure fuel return outlet B2 on the pump cover 2 through channels; the inner surface of the bypass valve sleeve 41 is designed with a first high-pressure fuel ring groove D5 and a first sealing cone surface D6; the bypass valve 42 is designed with a bypass valve central hole D7, a third sealing oil ring groove D8, a second high-pressure fuel ring groove D9, and a second sealing cone surface D10; the bypass valve 42 is also designed with several holes evenly distributed along the circumference connecting the bypass valve central hole D7 and the chamber where the bypass valve spring 44 is located; the first sealing oil ring groove D2 and the third sealing oil ring groove D3 are connected to the second sealing oil inlet B3 through channels. 8. The system is connected by several oil holes evenly distributed along the circumference; the first high-pressure fuel ring groove D5 and the second high-pressure fuel ring groove D9 cooperate to form a high-pressure fuel chamber D11; the high-pressure fuel chamber D11 is connected to the discharge valve 33 through a channel; the high-pressure fuel chamber D11 is connected to the plunger chamber E1 through a channel on the pump cover 2; the first sealing cone surface D6 and the second sealing cone surface D10 cooperate to realize the connection and disconnection of the valve port; the bypass valve sleeve 41, the bypass valve 42 and the baffle 43 cooperate to form a return fuel chamber D12, and the first sealing cone surface D6 and the second sealing cone surface D10 cooperate to specifically realize the connection and disconnection of the high-pressure fuel chamber D11 and the return fuel chamber D12; the fuel return ring groove D4 and the return fuel chamber D12 are connected by several fuel holes evenly distributed along the circumference on the bypass valve sleeve 41.

[0047] Reference Figure 11 The baffle 43 is designed with a central hole D13 that can accommodate the bypass valve 42; the outer circular surface of the baffle 43 is designed with a fourth sealing oil ring groove D14, a leakage oil collection ring groove D15, a fourth sealing ring groove D16, and a leakage oil outlet D17; the surface of the central hole D13 of the baffle is designed with a fifth sealing oil ring groove D18; the second sealing oil ring groove D3 and the fourth sealing oil ring groove D14 are connected by a number of oil holes evenly distributed along the circumference; the fourth sealing oil ring groove D14 and the fifth sealing oil ring groove D18 are connected by a number of oil holes evenly distributed along the circumference; the leakage oil collection ring groove D15 is connected to the central hole D13 of the baffle by a number of oil holes evenly distributed along the circumference; the leakage oil outlet D17 is connected to the central hole D7 of the bypass valve and the central hole D13 of the baffle by oil holes.

[0048] The sealing oil at the second sealing oil inlet B3 is divided into two paths: one path passes through the first sealing oil ring groove D2 and the third sealing oil ring groove D8 to form the first sealing oil passage L of the bypass valve; the other path passes through the second sealing oil ring groove D3, the fourth sealing oil ring groove D14, and the fifth sealing oil ring groove D18 to form the second sealing oil passage M of the bypass valve. Leaked sealing oil is discharged through the leakage sealing oil collection channel N, which consists of the bypass valve central hole D7, the baffle central hole D13, and the leakage oil outlet D17.

[0049] like Figure 12 As shown, the plunger assembly 5 in this embodiment includes: a plunger 51 and a plunger sleeve 52. The plunger sleeve 52 is designed with a chamber E2 capable of accommodating the pump cover 2 and the feed valve assembly 6. The plunger cavity E1 is the cavity formed by the central hole of the plunger sleeve 52 and the plunger 51. The outer surface of the plunger sleeve 52 is designed with a fifth sealing ring groove E3, a second low-pressure fuel ring groove E4, a sixth sealing ring groove E5, a seventh sealing ring groove E6, and an eighth sealing ring groove E7. The second low-pressure fuel ring groove E4 is connected to the first fuel hole B6 through several channels. The second low-pressure fuel ring groove E4 is also connected to the first fuel hole B6 through several channels. The low-pressure fuel inlet A2 is connected; the surface of the plunger sleeve 52 is designed with a ninth sealing ring groove E10, a sixth sealing oil ring groove E11, and a third low-pressure fuel ring groove E12; the sixth sealing oil ring groove E11 is connected to the sealing oil chamber E9 through a channel; the sealing oil chamber E9 is connected to the first sealing oil inlet A3 through a channel; the third low-pressure fuel ring groove E12 is connected to the low-pressure fuel chamber E8 through a channel; the third low-pressure fuel ring groove E12 is connected to the second low-pressure fuel ring groove E4 through a channel.

[0050] like Figure 13 As shown, the feed valve assembly 6 includes: a feed valve 61, a feed valve spring 62, and a lower spring seat 63; the feed valve 61 is designed with a third fuel port F1; the lower spring seat 63 is designed with a lower spring seat central hole F2, the diameter of which is larger than the diameter of the plunger 51.

[0051] The second fuel port F1, the lower spring seat bore F2, and the plunger cavity E1 are connected. The lower spring seat 63 is placed on the step of the cavity E2, the feed valve 61 is arranged opposite to the lower spring seat 63, and the feed valve spring 62 is arranged between the feed valve 61 and the lower spring seat 63. Under the action of the spring force of the feed valve spring 62, the feed valve 61 and the lower spring seat 63 maintain a predetermined distance.

[0052] A fourth low-pressure fuel ring groove F3, opposite to the first low-pressure fuel ring groove B5, is provided on the upper end face of the feed valve 61. When no low-pressure fuel is introduced, the feed valve spring 62 pushes the upper end face of the feed valve 61 upward to fit tightly against the small end face of the pump cover 2. When low-pressure fuel is introduced, the low-pressure fuel pushes the feed valve 61 to move, so that a fuel passage gap is formed between the upper end face of the feed valve 61 and the small end face of the pump cover 2. At this time, the low-pressure fuel enters the plunger cavity E1 through the low-pressure fuel inlet A2, the second low-pressure fuel ring groove E4, the first fuel hole B6, the first low-pressure fuel ring groove B5, the fourth low-pressure fuel ring groove F3, the fuel passage gap, the second fuel hole F1, and the middle hole F2 of the lower spring seat. Thus, the pump body 1, the pump cover 2, the plunger assembly 5, and the feed valve assembly 6 together form a low-pressure fuel supply path that supplies low-pressure fuel into the plunger cavity E1.

[0053] like Figure 14 As shown, the intake valve assembly 7 includes: an intake valve sleeve 71, an intake valve 72, and an intake valve spring 73; the intake valve sleeve 71 is designed with an intake port G1; the intake valve sleeve 71 is designed with an intake valve mounting hole G2 that can accommodate the intake valve 72; the intake port G1 and the intake valve mounting hole G2 are connected through a vent; the intake valve 72 is designed with an intake valve spring mounting hole G3 that can accommodate the intake valve spring 73; the intake valve mounting hole G2 and the intake valve spring mounting hole G3 are connected through a channel; the intake valve spring mounting hole G3 and the low-pressure fuel chamber E8 are connected through a channel.

[0054] In an embodiment of the present invention, when the solenoid valve assembly 45 is energized, the bypass valve assembly 4 opens, and the plunger chamber E1, the lower spring seat bore F2, the second fuel port F1, the high-pressure fuel chamber D11, the return fuel chamber D12, and the low-pressure fuel return outlet B2 are connected to form a low-pressure fuel circulation path; when the solenoid valve assembly 45 is de-energized, the feed valve assembly 6, the plunger chamber E1, the lower spring seat bore F2, the second fuel port F1, the high-pressure fuel chamber D11, the fuel tank C6, the second fuel port C1, and the high-pressure fuel outlet C1 are connected to form a high-pressure fuel supply path. The working process of the electrically controlled high-pressure pump is as follows: During the high-pressure fuel supply interval, the feed valve assembly 6 is open and the bypass valve assembly 4 is open. The high-pressure pump is in the process of drawing in low-pressure fuel. The low-pressure fuel enters the high-pressure pump from the fuel tank, fills the plunger chamber E1, and then continues to flow out of the high-pressure pump through the low-pressure fuel circulation path, and finally returns to the fuel tank. This circulation continues, which cools and exhausts the pump body.

[0055] During high-pressure fuel supply, the feed valve assembly 6 is closed and the bypass valve assembly 4 is closed. The low-pressure fuel in the plunger chamber E1 is pressurized to the target high-pressure value through the plunger 51, and then flows out of the high-pressure pump through the discharge valve assembly 3 to output high-pressure fuel.

[0056] Because no bypass valve, proportional valve, or other regulating valve is installed between the low-pressure fuel inlet A2 and the plunger chamber E1, and the feed valve assembly 6 is directly integrated into the plunger chamber E1, the low-pressure fuel can be directly injected into the plunger chamber E1, which greatly reduces the pressure loss of the low-pressure fuel and prevents the low-pressure fuel from vaporizing due to the pressure being lower than the saturated vapor pressure after entering the plunger chamber E1. Furthermore, back pressure is applied to the low-pressure fuel return outlet B2, allowing the low-pressure fuel to circulate at a pressure greater than the saturated vapor pressure, keeping the fuel in a liquid state, carrying away the heat in the plunger chamber E1, reducing the internal temperature of the high-pressure pump, and preventing problems such as cavitation and gas lock.

[0057] In embodiments of the present invention, the second sealing oil inlet B3, the first sealing oil ring groove D2, and the third sealing oil ring groove D8 are connected to form the first sealing oil passage L of the bypass valve; the second sealing oil inlet B3, the second sealing oil ring groove D3, the fourth sealing oil ring groove D14, and the fifth sealing oil ring groove D18 are connected to form the second sealing oil passage M of the bypass valve; the sealing oil pressure in the third sealing oil ring groove D8 is higher than the fuel pressure in the high-pressure fuel chamber D11, and the sealing oil pressure in the fourth sealing oil ring groove D14 and the fifth sealing oil ring groove D18 is higher than the fuel pressure in the return fuel chamber D12; a fitting clearance is designed between the bypass valve sleeve 41 and the bypass valve 42, and a fitting clearance is also designed between the plunger 51 and the plunger sleeve 52, so that the sealing oil can enter the fitting clearance; this design can both lubricate the mating parts and seal the gap between the mating parts, and uses the sealing oil to physically isolate the fuel and the solenoid valve, avoiding fuel corrosion of the solenoid valve.

[0058] In embodiments of the present invention, the bypass valve bore D7, the baffle bore D13, and the leakage oil outlet D17 are connected to form a leakage sealing oil collection channel N, which can collect the sealing oil leaking from the bypass valve, balance the air pressure between the chamber where the bypass valve spring 44 is located and the bypass valve bore D7, and communicate with the external atmosphere to avoid forming a closed space that would affect the movement of the bypass valve 42.

[0059] In this embodiment of the invention, the intake valve assembly 7 is a one-way valve, allowing fluid to flow only into the high-pressure pump and preventing it from flowing outwards. When gas is introduced through the intake valve assembly 7, and the high-pressure fuel chamber D11 and the return fuel chamber D12 inside the bypass valve assembly 4 are connected, the intake port G1, intake valve assembly 7, low-pressure fuel chamber E8, third low-pressure fuel ring groove E12, second low-pressure fuel ring groove E4, feed valve assembly 6, plunger chamber E1, high-pressure fuel chamber D11, return fuel chamber D12, and low-pressure fuel return outlet B2 are connected to form an inert gas system. The first path O for inert gas purging is formed when the high-pressure fuel chamber D11 and the return fuel chamber D12 inside the bypass valve assembly 4 are not connected. The inlet G1, inlet valve assembly 7, low-pressure fuel chamber E8, third low-pressure fuel ring groove E12, second low-pressure fuel ring groove E4, feed valve assembly 6, plunger chamber E1, high-pressure fuel chamber D11, discharge valve assembly 3, and high-pressure fuel outlet C1 are connected to form the second path P for inert gas purging. This enables the high-pressure pump to have an inert gas purging function, which can remove residual fuel through purging, making the inspection and maintenance of the high-pressure pump easier and significantly improving safety.

[0060] In the embodiments of the present invention, the discharge valve assembly 3 adopts a springless design, which solves the problem that the discharge valve spring may break under high-frequency movement conditions, reduces the number of parts, simplifies the structure, and improves the reliability and service life of the discharge valve assembly 3.

[0061] In this embodiment of the invention, a multi-stage anti-leakage structure is adopted for the high-pressure fuel in the plunger cavity E1. First, the high-pressure fuel in the plunger cavity E1 leaks through the plunger assembly gap to the third low-pressure fuel ring groove E12, significantly reducing its pressure and turning it into low-pressure fuel. Then, the first sealing oil inlet A3, sealing oil cavity E9, and sixth sealing oil ring groove E11 are connected to form a plunger assembly sealing oil passage K. The sealing oil pressure in the sixth sealing oil ring groove E11 is greater than the fuel pressure in the third low-pressure fuel ring groove E12, thereby achieving the first stage of sealing for the fuel. Then, in the ninth sealing... A sealing ring is installed in the sealing groove E10 to achieve a second seal for the fuel; finally, a sealing ring is installed in the first sealing ring groove A6 to seal the gap between the pump body 1 and the guide piston assembly 8, and abnormal fuel leakage can be discharged from the pressure balance hole A5, forming a third seal for the fuel, preventing fuel leakage to the bottom of the high-pressure pump from contaminating the lubricating oil; because after the high-pressure pump is installed on the engine, the bottom of the high-pressure pump will be immersed in a lubricating oil chamber of the engine, which contains a large amount of lubricating oil, so the present invention can avoid fuel contamination of the lubricating oil.

[0062] In embodiments of the present invention, the high-pressure pump can be connected to a mechanical injector via a high-pressure pipe to form an electronically controlled unit pump fuel injection system; the high-pressure pump can also be connected to a common rail and an electronically controlled injector via a high-pressure pipe to form an electronically controlled high-pressure common rail system. Therefore, the present invention can be applied to both electronically controlled unit pump fuel injection systems and electronically controlled high-pressure common rail systems, thus having a wide range of applications. Considering the characteristics of clean fuels such as easy vaporization, low viscosity, and corrosiveness, the high-pressure pump adopts a unit pump design rather than a combined pump design. If one high-pressure pump fails, the other high-pressure pumps can still maintain engine operation, while also facilitating maintenance or replacement.

[0063] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit it. Although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, and all such modifications or substitutions should be covered within the scope of the claims of the present invention.

Claims

1. A single body electronically controlled high pressure pump suitable for clean fuel with easy vaporization, comprising a pump body (1), a pump cover (2) mounted on the upper part of the pump body (1), a plunger pair (5) accommodated in the pump body (1), and a feed valve assembly (6), a plunger cavity (E1) is formed in the plunger pair (5), characterized in that, The monolithic electronically controlled high-pressure pump further comprises: a bypass valve assembly (4) integrated on the pump cover (2); a delivery valve assembly (4) assembled on the pump cover (2) and in communication with the high-pressure fuel outlet of the bypass valve assembly (4); the feed valve assembly (6) is assembled between the plunger pair (5) and the pump cover (2), and the inner hole of the feed valve assembly (6) is directly in communication with the plunger cavity (E1); the pump body (1), the pump cover (2), the plunger pair (5) and the feed valve assembly (6) together constitute a low-pressure fuel supply path for supplying low-pressure fuel into the plunger cavity (E1), and no regulating valve for regulating the feed flow is arranged between the low-pressure fuel inlet (A2) of the pump body (1) and the feed valve assembly (6), so that the minimum fuel pressure in the plunger cavity (E1) is greater than the saturated vapor pressure of the fuel; the feed valve assembly (6), the pump cover (2) and the bypass valve assembly (4) together constitute a low-pressure fuel circulation path for circulating the low-pressure fuel in the plunger cavity (E1) to the fuel tank; the feed valve assembly (6), the pump cover (2), the bypass valve assembly (4) and the delivery valve assembly (4) together constitute a high-pressure fuel supply path for guiding the high-pressure fuel pressurized in the plunger cavity (E1) to the target device.

2. The single body electrically controlled high pressure pump adapted to clean fuel with easy vaporization according to claim 1, characterized in that, The plunger pair (5) comprises a plunger (51) and a plunger sleeve (52), the plunger sleeve (52) is assembled in the pump body (1), and the plunger (51) is slidingly assembled in the plunger sleeve (52); a cavity (E2) is formed on the side of the plunger sleeve (52) facing the pump cover (2), the feed valve assembly (6) is arranged inside the cavity (E2), and part of the pump cover (2) extends into the cavity (E2) and is in contact or not in contact with the feed valve assembly (6); a second low-pressure fuel ring groove (E4) is arranged on the plunger sleeve (52), a first fuel passage is arranged on the pump cover (2), and the second low-pressure fuel ring groove (E4) is in communication with the low-pressure fuel inlet (A2) of the pump body (1) and the first fuel passage through a channel; the plunger cavity (E1) is formed between the feed valve assembly (6), the plunger sleeve (52) and the plunger (51), a third fuel hole (F1) is arranged in the feed valve assembly (6), and the third fuel hole (F1) is in communication with the plunger cavity (E1); wherein the low-pressure fuel inlet (A2), the second low-pressure fuel ring groove (E4), the first fuel passage, the fuel passing gap formed between the pump cover (2) and the feed valve assembly (6), and the third fuel hole (F1) together constitute the low-pressure fuel supply path.

3. The single body electrically controlled high pressure pump adapted to clean fuel with easy vaporization according to claim 1, characterized in that, An air inlet valve assembly (7) is mounted on the pump body (1); the air inlet valve assembly (7), the plunger pair (5) and the feed valve assembly (6) together constitute an inert gas purging path for blowing inert gas into the plunger cavity (E1); By adjusting the bypass valve assembly (4), the inert gas in the plunger cavity (E1) is purged outward through the low-pressure fuel circulation path or the high-pressure fuel supply path.

4. The single body electrically controlled high pressure pump adapted to clean fuel with easy vaporization according to claim 2, characterized in that, The bypass valve assembly (4) comprises a bypass valve sleeve (41), a bypass valve (42), a baffle (43), a bypass valve spring (44) and an electromagnetic valve assembly (45). The bypass valve sleeve (41), the bypass valve (42), the baffle (43) and the bypass valve spring (44) are all assembled in the pump cover (2). The electromagnetic valve assembly (45) is in driving connection with the bypass valve (42) to control the reciprocating movement of the bypass valve (42) in the bypass valve sleeve hole (D1) of the bypass valve sleeve (41). The baffle (43) is in contact with the bypass valve sleeve (41) to limit the maximum stroke of the bypass valve (42). The bypass valve sleeve (41) and the bypass valve (42) define a high-pressure fuel cavity (D11) and a return fuel cavity (D12) therebetween, and the bypass valve (42) and the bypass valve sleeve (41) directly form a valve port through a pair of sealing cone surfaces. When the electromagnetic valve assembly (45) is energized, the bypass valve (42) is driven to move towards the opening of the valve port, the fuel flow path between the high-pressure fuel cavity (D11) and the return fuel cavity (D12) is conducted to form the low-pressure fuel circulation path. When the electromagnetic valve assembly (45) is de-energized, the bypass valve spring (44) drives the bypass valve (42) to move towards the closing of the valve port, the fuel flow path between the high-pressure fuel cavity (D11) and the return fuel cavity (D12) is shut off to form the high-pressure fuel supply path.

5. The single body electrically controlled high pressure pump adapted to clean fuel with a tendency to vaporize according to claim 4, characterized in that, An outer end surface of the bypass valve sleeve (41) is formed with a fuel return ring groove (D4), the fuel return ring groove (D4) and the return fuel cavity (D12) are communicated through a plurality of fuel holes uniformly distributed in the circumferential direction of the bypass valve sleeve (41), and the fuel return ring groove (D4) is also communicated with a low-pressure fuel return outlet (B2) provided on the pump cover (2). When the electromagnetic valve assembly (45) is energized, the plunger cavity (E1), the third fuel hole (F1), the high-pressure fuel cavity (D11), the return fuel cavity (D12) and the low-pressure fuel return outlet (B2) jointly form the low-pressure fuel circulation path.

6. The single body electrically controlled high pressure pump adapted to clean fuel with easy vaporization according to claim 4, characterized in that, The discharge valve assembly (3) comprises a discharge valve head (31), a stroke limiting disc (32) and a discharge valve (33). The discharge valve head (31) is provided with an axially penetrating high-pressure fuel outlet (C1) and a stroke limiting disc mounting hole (C4) coaxially communicated with the upstream end of the high-pressure fuel outlet (C1); The stroke limiting disc (32) is fixed in the stroke limiting disc mounting hole (C4), and the disc body of the stroke limiting disc (32) is provided with a second fuel hole (C5) axially butted with the high-pressure fuel outlet (C1), and the large end surface of the stroke limiting disc (32) towards the discharge valve (33) constitutes the maximum stroke limiting surface of the discharge valve (33). The discharge valve (33) is slidably arranged in a pump cover mounting hole (B9) of the pump cover (2) and located on an upstream side of the range limiting disc (32), and a fuel groove (C6) is arranged on an outer peripheral wall of the discharge valve (33); When the discharge valve (33) is opened, high-pressure fuel in the high-pressure fuel cavity (D11) is guided into the high-pressure fuel outlet (C1) through the fuel groove (C6) and the second fuel hole (C5); When the pressure of the high-pressure fuel in the high-pressure fuel cavity (D11) decreases, the reverse thrust provided by the residual high-pressure fuel in the high-pressure fuel outlet (C1) acts on the discharge valve (33) through the second fuel hole (C5), so that the discharge valve (33) is self-sealed and self-reset, and the springless opening and closing of the discharge valve (33) is completed. When the electromagnetic valve assembly (45) is not powered, the plunger cavity (E1), the third fuel hole (F1), the high-pressure fuel cavity (D11), the fuel groove (C6), the second fuel hole (C5) and the high-pressure fuel outlet (C1) together form the high-pressure fuel supply path.

7. The single body electrically controlled high pressure pump adapted to clean fuel with tendency to vaporize according to claim 1, characterized in that, The pump body (1) is provided with an air pressure balance hole (A5) which is in communication with a chamber where the plunger spring is located.

8. The single body electrically controlled high pressure pump adapted to clean fuel with easy vaporization according to claim 1, characterized in that, The pump body (1) is provided with a first sealing oil inlet (A3); The plunger sleeve (52) of the plunger pair (5) is formed with a plunger pair sealing oil channel (K) which is in communication with the first sealing oil inlet (A3) and is used for supplying sealing oil to the cooperation gap between the plunger (51) and the plunger sleeve (52); The sealing oil pressure in the plunger pair sealing oil channel (K) is higher than the leakage fuel pressure at the plunger pair (5), so as to block the leakage fuel in the plunger pair (5).

9. The single body electrically controlled high pressure pump adapted to clean fuel with tendency to vaporize according to claim 3, characterized in that, The intake valve assembly (7) is a one-way valve which allows the external inert gas source to flow to the plunger cavity (E1) and prevents the fuel from flowing reversely into the inert gas source.

10. The single body electrically controlled high pressure pump suitable for clean and easily vaporized fuel according to any one of claims 1 to 9, characterized in that, The single-body electronically-controlled high-pressure pump suitable for clean fuel with easy evaporation is suitable for any one of methanol, ammonia and dimethyl ether.

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