Hybrid power thermal management system with liquid ammonia phase change cooling

Abstract

The application provides a liquid ammonia phase change cooling type hybrid power thermal management system and relates to the technical field of engines.The system comprises an injector, a liquid ammonia hydrogen supply system, a liquid ammonia common rail pipe, a fuel common rail pipe and an oil tank.The liquid ammonia hydrogen supply system comprises a liquid ammonia storage tank, a pump ammonia system, a shunt system and an ammonia inlet and outlet system.The fuel common rail pipe is connected with the one-way oil inlet of the injector, and the liquid ammonia common rail pipe is connected with the one-way ammonia inlet of the injector.The ammonia inlet pipe and the ammonia return pipe are arranged in the ammonia inlet and outlet system.The pump ammonia system comprises a liquid ammonia storage shunt, a low-pressure pump and a high-pressure pump.The shunt system comprises a storage tank, an ammonia inlet control valve, a safety valve and an ammonia return control valve.The application can effectively solve the cold start problem of the engine under cold conditions, reduce the power consumption of the compressor, realize waste heat utilization and improve the energy utilization rate.Meanwhile, the application provides a feasible ammonia fuel application path, which realizes one ammonia for three uses.

Description

[0001] The present application is a divisional application of the parent application entitled "Liquid Ammonia Phase Change Cooling Type Hybrid Power Management System". TECHNICAL FIELD

[0002] The present application relates to an engine, in particular a hybrid engine. BACKGROUND

[0003] Under the background of green and low-carbon ships, ship development has entered a critical period of transformation and upgrading. In the future, ships require high flexibility of power, which includes flexible configuration of power devices, fuel supply, injection system flexibility, and fuel storage, transfer, and injection flexibility. Power diversity and fuel diversity will be the inevitable trend of ship development. Therefore, developing research on low-carbon clean fuel supply and injection systems for ships is a key measure to meet current and future technological development needs, improve technological innovation, product competitiveness, and enterprise influence. Ammonia, as one of the typical low-carbon fuels, has higher energy storage than hydrogen fuel, is easy to store and transport, and has a mature supply chain, making it one of the main low-carbon alternative energy sources.

[0004] New alternative fuels such as ammonia fuel have common characteristics of low viscosity, low flash point (liquid fuel), low carbon, and low emission, which require a significant technical upgrade and modification of existing equipment, especially fuel supply and injection systems, to meet the use requirements of new fuels. At the same time, it is worth noting that although new alternative fuels have great potential for emission reduction from the perspective of engine combustion emissions, from the perspective of the entire life cycle of the fuel, existing alternative fuels need to address energy green regeneration, driving the transformation of the entire energy industry chain. Currently, there is no mature ammonia fuel power device internationally, and ammonia fuel engines modified from diesel engines have problems such as low volumetric efficiency, poor combustion effect, low thermal efficiency, and low energy utilization, limiting their widespread application.

[0005] To this end, the present application adopts a diesel pilot combustion mode and designs an ammonia fuel injection system to inject ammonia fuel into the cylinder in liquid form at high pressure, improving the engine's compression ratio and effectively improving thermal efficiency. Compared with existing invention patents, the present application innovatively designs a double-acting heat pump module based on the principle of liquid ammonia phase change, which effectively solves the problem of engine cold start under cold conditions and reduces the power consumption of the compressor, achieving waste heat utilization and improving energy utilization. At the same time, the present application proposes a practical ammonia fuel application path, realizing one ammonia for three uses: power device fuel, heat dissipation system refrigerant, and exhaust aftertreatment module reducing agent. This improves engine emission performance while ensuring power and economy, and gradually moves towards maximum carbon emission reduction. SUMMARY

[0006] The application aims to provide a liquid ammonia phase change cooling type hybrid power thermal management system which can effectively solve the engine cold start problem under cold conditions, reduce the power consumption of the compressor, realize waste heat utilization, and improve the energy utilization rate.

[0007] The application is achieved as follows:

[0008] The liquid ammonia phase change cooling type hybrid power thermal management system of the application is characterized in that it comprises an injector, a liquid ammonia hydrogen supply system, a liquid ammonia common rail pipe, a fuel common rail pipe, and an oil tank.

[0009] The application can further comprise:

[0010] 1. The injector comprises an injector body, a liquid ammonia injection part, and a diesel injection part.

[0011] 2、The booster module comprises a booster yoke, booster main and auxiliary poles, a main booster piston, a booster armature, a booster limit block, a booster double-sealed valve rod, a booster upper valve rod seat, a booster lower valve rod seat, the booster armature is sleeved on the top of the booster double-sealed valve rod, a booster reset spring is arranged between the booster yoke and the booster armature, the booster main and auxiliary poles are arranged outside the booster reset spring, the booster main and auxiliary poles are wound with coils, the middle part of the booster double-sealed valve rod is located in the booster upper valve rod seat, the bottom part of the booster double-sealed valve rod is located in the booster lower valve rod seat, the middle part of the booster double-sealed valve rod is sleeved with a booster valve rod reset spring, a booster double-sealed protrusion is arranged between the middle part and the bottom part of the booster double-sealed valve rod, a sealing surface is arranged on the corresponding face of the booster upper valve rod seat, the booster lower valve rod seat and the booster double-sealed valve rod, the main booster piston is located below the booster lower valve rod seat, the main booster piston is externally sleeved with a main booster piston reset spring, an ammonia return channel is arranged in the booster upper valve rod seat, an ammonia inlet channel and an intermediate pipeline are arranged in the booster lower valve rod seat, and a communication space is formed in the space where the booster double-sealed protrusion is located in the booster lower valve rod seat, and the communication space is in communication with the intermediate pipeline.

[0012] 3、The first pressure accumulation resonance flow limiting module comprises a resonance block, an intermediate block, a prismatic sealing block, a flow limiting piston and a pressure accumulation valve seat, a pressure accumulation cavity is arranged in the injector body below the main booster piston, a one-way ammonia inlet is mounted on the side wall of the pressure accumulation cavity, a liquid cooling pipe inlet is arranged on the injector body, the liquid cooling pipe inlet is in communication with the pressure accumulation cavity, the resonance block, the intermediate block, the prismatic sealing block and the pressure accumulation valve seat are sequentially arranged below the pressure accumulation cavity, the flow limiting piston is arranged in the pressure accumulation valve seat, an intermediate block reset spring is arranged in the intermediate block, an ammonia inlet hole and a resonance block ammonia inlet throttling hole are arranged in the bottom part of the intermediate block, the prismatic sealing block is located above the flow limiting piston, an intermediate hole is arranged in the flow limiting piston, a flow limiting piston reset spring is arranged below the flow limiting piston, and a storage cavity is arranged below the flow limiting piston reset spring.

[0013] 4、The resonance block is respectively provided with a first ammonia inlet, a second ammonia inlet, a first ammonia cavity, a second ammonia cavity, a first ammonia outlet and a second ammonia outlet, the first ammonia cavity is in communication with the first ammonia inlet and the first ammonia outlet, the second ammonia cavity is in communication with the second ammonia inlet and the second ammonia outlet, the first ammonia cavity and the second ammonia cavity are in communication through a communication hole, the first ammonia cavity is in communication with the first ammonia inlet through a first ammonia throttling hole, the first ammonia cavity is in communication with the pressure accumulation cavity through a second ammonia throttling hole, and the first ammonia inlet and the second ammonia inlet are in communication with the pressure accumulation cavity.

[0014] 5. The super-magnetic hysteresis electromagnetic control actuator comprises super-magnetic hysteresis main and auxiliary magnetic poles, a magnetic hysteresis seat, a super-magnetic hysteresis upper valve stem, a super-magnetic hysteresis lower end taper valve, a super-magnetic hysteresis bacterial-shaped valve, a coil wound in the super-magnetic hysteresis main and auxiliary magnetic poles, a super-magnetic hysteresis material arranged in the through hole of the super-magnetic hysteresis main and auxiliary magnetic poles, a magnetic hysteresis seat, a super-magnetic hysteresis upper valve stem, a super-magnetic hysteresis lower end taper valve, and a super-magnetic hysteresis bacterial-shaped valve arranged in sequence below the super-magnetic hysteresis material, the super-magnetic hysteresis bacterial-shaped valve is located in the super-magnetic hysteresis bacterial-shaped valve cavity, a super-magnetic hysteresis bacterial-shaped valve return spring is arranged below the super-magnetic hysteresis bacterial-shaped valve, an oil return oil path and an oil inlet oil path are arranged in the injector body where the super-magnetic hysteresis electromagnetic control actuator is located, the oil return oil path communicates with the super-magnetic hysteresis bacterial-shaped valve cavity, a super-magnetic hysteresis taper valve oil inlet hole is arranged in the super-magnetic hysteresis lower end taper valve shell outside the super-magnetic hysteresis lower end taper valve, and the super-magnetic hysteresis taper valve oil inlet hole communicates with the oil inlet oil path.

[0015] 6. The phase-change controllable super-atomization nozzle module comprises a super-atomization nozzle body, a super-atomization valve seat, a static leakage-free cylinder, a super-atomization needle valve body, and a super-atomization control valve stem, the super-atomization valve seat is located in the super-atomization nozzle body, the static leakage-free cylinder and the super-atomization needle valve body are located in the super-atomization valve seat, the head of the super-atomization needle valve body is located in the static leakage-free cylinder, the super-atomization needle valve body return spring is arranged between the middle part of the super-atomization needle valve body and the static leakage-free cylinder, the static leakage-free cylinder, the super-atomization needle valve body, and the super-atomization valve seat form an ammonia storage cavity, the super-atomization valve seat and the super-atomization nozzle body form a liquid cooling working medium inlet pipeline and a liquid cooling working medium outlet pipeline, the bottom of the super-atomization needle valve body and the bottom of the super-atomization valve seat form a super-atomization jet flow channel, the ammonia storage cavity communicates with the storage cavity, and the top end of the super-atomization needle valve body and the injector body above it form a super-atomization control cavity.

[0016] 7. The second pressure accumulation resonance flow limiting module has the same structure as the first pressure accumulation resonance flow limiting module and is arranged side by side in the injector body.

[0017] 8、The said sub-boost module includes sub-boost yoke, sub-boost main and auxiliary magnetic pole, sub-boost piston, sub-boost armature, sub-boost limit block, sub-boost double-sealed valve rod, sub-boost upper valve rod seat, sub-boost lower valve rod seat, sub-boost armature is sleeved on the top of sub-boost double-sealed valve rod, sub-boost reset spring is arranged between sub-boost yoke and sub-boost armature, sub-boost main and auxiliary magnetic pole is arranged outside sub-boost reset spring, sub-boost main and auxiliary magnetic pole is wound with coil, the middle part of sub-boost double-sealed valve rod is located in sub-boost upper valve rod seat, the bottom of sub-boost double-sealed valve rod is located in sub-boost lower valve rod seat, sub-boost valve rod reset spring is sleeved on the middle part of sub-boost double-sealed valve rod, sub-boost double-sealed protrusion is arranged between the middle part and the bottom of sub-boost double-sealed valve rod, sealing surface is arranged on the corresponding face of sub-boost upper valve rod seat, sub-boost lower valve rod seat and sub-boost double-sealed valve rod, sub-boost piston is located below sub-boost lower valve rod seat, sub-boost piston reset spring is sleeved on the outside of sub-boost piston, oil return pipeline is arranged in sub-boost upper valve rod seat, sub-boost oil channel and sub-boost communication passage are arranged in lower valve rod seat, sub-boost oil channel is respectively communicated with oil inlet channel and below sub-boost double-sealed protrusion, the space where sub-boost double-sealed protrusion is located is communication space, sub-boost communication passage is respectively communicated with communication space and above sub-boost piston, sealing ball is arranged in oil inlet channel, sealing ball reset spring is arranged below sealing ball, boost oil pipeline is below sub-boost piston, boost oil pipeline is communicated with oil inlet channel below sealing ball reset spring.

[0018] 9、The said pressure balance type electromagnetic control actuator includes pressure control type main and auxiliary magnetic pole, pressure control type armature and balance valve rod, the upper part of balance valve rod is arranged in pressure control type main and auxiliary magnetic pole, the lower part of balance valve rod is located in pressure control type armature, pressure control type armature is located below pressure control type main and auxiliary magnetic pole, pressure control type oil return hole upper section and pressure control type oil return hole lower section are arranged below pressure control type armature and balance valve rod, pressure control type oil return hole upper section and pressure control type oil return hole lower section are communicated through pressure control type oil return throttle hole, pressure control type oil return hole lower section is communicated with oil inlet pipeline through pressure control type oil inlet throttle hole.

[0019] 10. The needle valve eccentric self-adjusting nozzle comprises an eccentric self-adjusting intermediate block, an eccentric self-adjusting needle valve body, an eccentric self-adjusting needle valve body shell, an eccentric self-adjusting valve block, and an eccentric self-adjusting nozzle body. The eccentric self-adjusting needle valve body is located in the eccentric self-adjusting needle valve body shell, and the eccentric self-adjusting needle valve body is located in the eccentric self-adjusting nozzle body. A pressure-controlled oil return hole lower section is arranged in the eccentric self-adjusting intermediate block. The lower end of the eccentric self-adjusting intermediate block is connected to the eccentric self-adjusting valve block. The top of the eccentric self-adjusting needle valve body is located in the eccentric self-adjusting valve block. An eccentric self-adjusting control cavity is formed between the eccentric self-adjusting needle valve body, the eccentric self-adjusting valve block, and the eccentric self-adjusting intermediate block. The eccentric self-adjusting control cavity is connected to the pressure-controlled oil return hole lower section. An eccentric self-adjusting needle valve body protrusion is arranged in the middle of the eccentric self-adjusting needle valve body. An eccentric self-adjusting needle valve body return spring is sleeved on the eccentric self-adjusting needle valve body protrusion. The eccentric self-adjusting needle valve body is of an eccentric structure, and a part of it is attached to the inner wall of the eccentric self-adjusting needle valve body shell outside it.

[0020] 11. The hydrogen fuel cell system further comprises an anode of an electric pile, a cathode of the electric pile, a hydrogen inlet, a nitrogen inlet, and an air inlet. A hydrogen storage tank is connected to the hydrogen inlet, and a nitrogen storage tank is connected to the nitrogen inlet. The hydrogen inlet and the nitrogen inlet are combined and then supplied to the anode of the electric pile through a hydrogen filter, a first shut-off valve, a high-pressure gas injection valve, an eductor pump, and a hydrogen circulation pump. The exhaust gas of the anode of the electric pile passes through a water separator and is discharged through a drain valve and an exhaust valve, respectively. Air is supplied to the cathode of the electric pile through an air filter, an air compressor, a first intercooler, a humidifier, and a second shut-off valve.

[0021] 12. The cooling system further comprises a water tank, a first radiator, a first deionizer, a first heater, a second intercooler, and a first cooling connection port. The first radiator, the first deionizer, the first heater, the second intercooler, and the first cooling connection port are connected in parallel to form a first cooling unit. The water tank is connected to the first cooling unit. The cooling connection port is connected to a cooling water outlet. The first cooling unit is connected to an outlet through a drain valve. A second cooling unit is symmetrically arranged with the first cooling unit. The second cooling unit comprises a second radiator, a second deionizer, a second heater, a third intercooler, and a second cooling connection port. The second cooling unit is arranged in the same way and symmetrically with the first cooling unit.

[0022] 13. Further comprising a double-acting heat pump, the double-acting heat pump comprising a liquid ammonia inlet, a three-way valve, a low-power compressor, a high-power compressor, a refrigeration heat exchanger, a heating heat exchanger, a third heat sink, a liquid ammonia storage tank connected to the liquid ammonia inlet, the liquid ammonia inlet connected to the three-way valve, high-pressure steam from the low-power compressor outlet entering the third heat sink, the high-pressure steam condensed through a first electronic expansion valve and a second electronic expansion valve into the refrigeration heat exchanger, and returning to the low-power compressor; high-pressure steam from the high-power compressor outlet entering the heating heat exchanger to condense and release heat, entering the branch with the expansion valve through a single check valve and a first electronic expansion valve, the liquid working medium in the branch with the expansion valve evaporating into gaseous working medium, and returning to the high-power compressor.

[0023] 14. Further comprising a liquid ammonia-diesel dual-fuel cylinder, the liquid ammonia-diesel dual-fuel cylinder comprising a cylinder body, a piston, a crank, an air inlet pipe, and an exhaust pipe, the air inlet pipe and the exhaust pipe being arranged above the cylinder body respectively, and an injector being arranged on the cylinder body, the piston being arranged in the cylinder body, the crank being connected below the piston, the air inlet pipe being connected to the cylinder body at an air inlet, the air inlet being provided with an air inlet valve rod, the air inlet valve rod being sleeved with an air inlet valve rod spring, the exhaust pipe being connected to the cylinder body at an air outlet, the air outlet being provided with an air outlet valve rod, the air outlet valve rod being sleeved with an air outlet valve rod spring, the air inlet pipe being provided with a hydrogen inlet, the hydrogen inlet and the air inlet being provided with an air inlet, and the hydrogen inlet and the air inlet being provided with a safety valve.

[0024] The advantages of the present application are:

[0025] 1. The present application saves installation space through integrated design of liquid ammonia-diesel dual-fuel, simultaneously controls the injection of the ammonia fuel injector and the diesel injector, and provides fuel pressure for the diesel injector and the supercharger;

[0026] 2. The present application uses a super-magnetic electromagnetic control actuator structure to ensure accurate control of ammonia fuel injection. The pressure-balanced electromagnetic control actuator and the super-atomizing nozzle module are used to spray into the cylinder, realizing large-flow high-pressure liquid ammonia fuel injection into the cylinder and achieving sufficient combustion;

[0027] 3. The injection process combines thermal management design to adjust from pressure and temperature to control the phase change of ammonia fuel;

[0028] 4. The present application uses a multi-valve cooperative control form to realize variable cycle of liquid ammonia injection process, making the injection amount and injection timing more accurate and flexible;

[0029] 5. The present application uses a resonant block adjustment system to adjust the pressure fluctuation in the system, changes the phase of the pressure wave fluctuation, adjusts the fluctuation frequency, and adjusts the corresponding relationship between the wave crest and the wave trough, realizing controllable pressure wave coupling process. Meanwhile, a flow restrictor is designed to prevent abnormal injection;

[0030] 6. The balanced valve control mode is adopted, the whole bubble is in the high pressure fuel, and the higher common rail pressure (250MPa) can be realized by the action of the balance force, so as to reduce the mass of the whole valve, that is, to reduce the electromagnetic force demand, and to increase the control corresponding. Therefore, only the electromagnetic valve and armature with small size and small spring pre-tightening force are required. At the same time, the balanced valve rod is not directly subjected to high impact, the pitting phenomenon of the traditional ball valve is prevented, and the system reliability is increased;

[0031] 7. The combination design of the intermediate block and the self-adjusting valve block solves the leakage problem of the traditional static block, and prevents the wear and leakage problem caused by the eccentric needle valve. BRIEF DESCRIPTION OF DRAWINGS

[0032] Figure 1 It is a schematic diagram of the whole structure of the application;

[0033] Figure 2 It is a liquid ammonia hydrogen supply system;

[0034] Figure 3 It is a schematic diagram of a liquid ammonia-diesel dual fuel cylinder;

[0035] Figure 4 It is a schematic diagram of a hydrogen fuel cell supply system;

[0036] Figure 5 It is a schematic diagram of a cooling system;

[0037] Figure 6 It is a schematic diagram of a double-acting heat pump and waste heat utilization system;

[0038] Figure 7 It is a schematic diagram of the whole structure of the liquid ammonia-diesel dual fuel integrated injector;

[0039] Figure 8 It is a schematic diagram of a supercharging module structure;

[0040] Figure 9 It is a schematic diagram of a pressure accumulation cavity thermal management module structure;

[0041] Figure 10 It is a schematic diagram of a resonant block structure;

[0042] Figure 11 It is a schematic diagram of a super-magnetic electromagnetic control actuator structure;

[0043] Figure 12 It is a schematic diagram of a phase change controllable super-atomizing nozzle module structure;

[0044] Figure 13 It is a schematic diagram of a sub-supercharging module structure;

[0045] Figure 14Structure schematic diagram of pressure balance type electromagnetic control actuator;

[0046] Figure 15 Structure schematic diagram of needle valve eccentric self-adjusting nozzle module;

[0047] Figure 16 Three-dimensional overall structure schematic diagram of phase-change controllable super-atomization nozzle module;

[0048] Figure 17 Three-dimensional cross-sectional structure schematic diagram of phase-change controllable super-atomization nozzle module. DETAILED DESCRIPTION

[0049] The application will be described in more detail below with examples and with reference to the accompanying drawings:

[0050] In combination Figures 1-17 , Figure 1 The overall structure schematic diagram of the application, the liquid ammonia phase-change cooling type hybrid power thermal management system, comprises: a fuel supply system, a liquid ammonia and hydrogen supply system, a liquid ammonia-diesel dual fuel cylinder 16, a liquid ammonia-diesel dual fuel injector 8, a hydrogen fuel cell supply system 27, a cooling system 28, and a double-acting heat pump 26 and a waste heat utilization system 29. The fuel supply system comprises an oil tank 7, a filter 6, a high-pressure oil pump and a motor 4, a fuel common rail pipe 11, a flow restrictor 12, high-pressure oil pipes 3 and 13, and an injector 8, the right end of the common rail pipe 11 is in communication with the high-pressure oil pump 4, the filter 6 and the oil tank 7 respectively, and the flow restrictor 12 is in communication with the injector 14 through the high-pressure oil pipe 13.

[0051] Figure 2 The liquid ammonia and hydrogen supply system schematic diagram, comprising a liquid ammonia storage tank 24, a hydrogen storage tank 25, a nitrogen storage tank 23, a pump ammonia system 22, a shunt system 21, an ammonia inlet and outlet system 20, an ammonia inlet pipe 17, an ammonia return pipe 18, a liquid ammonia common rail pipe 1, a liquid ammonia leakage detection port 10, a high-pressure ammonia pipe 2, and a liquid ammonia injector 8. The pump ammonia system 22 comprises a low-pressure pump and a motor 30, a high-pressure pump and a motor 31, an overflow valve 32, a safety valve 33, a temperature controller 34, a liquid ammonia storage shunt 35, a storage tank 36, a control valve 37, an ammonia inlet 38, an ammonia return 39, a regulation block 40, a safety valve 41, and a control valve 42.

[0052] Figure 3 The liquid ammonia-diesel dual fuel cylinder schematic diagram, mainly comprising a crank 45, a piston 16, a cylinder 46, an air inlet 15, an air inlet valve rod 44, an air inlet valve rod spring 43, an air outlet 9, an air outlet valve rod 47, an air outlet valve rod spring 48, a hydrogen air inlet 51, a safety valve 50, and an air inlet 49.

[0053] Figure 4A schematic diagram of a hydrogen fuel cell supply system, mainly including: hydrogen inlet 52, nitrogen purge inlet 53, hydrogen filter 54, pressure sensor 55, shut-off valve 56, high-pressure gas injection valve 57, ejector pump and hydrogen circulation pump 58, overpressure valve 59, air exhaust 60, 66, anode 61, outlet 62, water separator 63, drain valve 64, exhaust valve 65, air inlet 67, air filter 68, sensor 69, air compressor 70, intercooler 71, humidifier 72, shut-off valve 73, bypass valve 74, cathode 75, sensor 76, shut-off valve 77, outlet 78, water separator 79, throttle valve 80, 81, excess hydrogen 82, muffler 83, outlet 84.

[0054] Figure 5 A schematic diagram of a cooling system, mainly including: water tank 85, cooling water pump 86, 100, temperature sensor 87, 101, cooling connection port 88, 102, temperature and pressure sensor 89, 103, intercooler 90, 104, heater 92, 106, three-way valve 93, 107, deionizer 94, 108, sensor 95, 109, radiator 96, 110, drain valve 97, 111, outlet 91, 98, 105, 112, cooling water outlet 99, 112.

[0055] Figure 6 A schematic diagram of a double-acting heat pump and waste heat utilization system, mainly including: liquid ammonia inlet 113, heater 114, three-way valve 115, radiator 116, sensor 117, electromagnetic reversing valve 118, gaseous working medium 119, filter 120, low-power compressor 121, sensor 122, refrigeration heat exchanger 123, sensor 124, electronic expansion valve 125, high-power compressor 126, sensor 127, heating heat exchanger 128, one-way check valve 129, electronic expansion valve 130, deionizer 131, ammonia drain valve 132, waste working medium 133, expansion valve 134, liquid working medium 135.

[0056] Figure 7 A schematic diagram of a liquid ammonia-diesel dual fuel integrated injector, mainly including: one-way ammonia inlet 136, booster module 137, pressure accumulation resonance flow limiting module 138, 142, super-magnetic electromagnetic control actuator 139, phase-change controllable super-atomization nozzle module 140, one-way oil inlet 141, auxiliary booster module 143, pressure balance type electromagnetic control actuator 144, needle valve eccentric self-adjusting nozzle 145, liquid ammonia thermal management module 146, 147. Realize high-pressure liquid ammonia injection into the cylinder, realize full combustion. At the same time, the injection process combines thermal management design, adjusts and controls the phase change conversion of ammonia fuel from two aspects of pressure and temperature. Adopting a double-valve control form, realize the cycle variability of liquid ammonia injection process, make the injection amount and injection timing more accurate and flexible.

[0057] Figure 8 The detailed schematic diagram of the ejector supercharging module includes: a magnetic yoke 148, a reset spring 149, main and auxiliary magnetic poles 150, a coil 151, a return ammonia passage 152, an upper surface of a supercharging piston 153, an intermediate cavity 154, a supercharging piston reset spring 155, an armature 156, a limit block 157, a valve rod reset spring 159, a double-sealed valve rod 158, an ammonia inlet passage 160, an intermediate pipeline 161, and a lower surface of the supercharging piston 162. The module can adopt two control modes, one of which is in the form of liquid ammonia supercharging liquid ammonia, and the other is in the form of diesel supercharging liquid ammonia.

[0058] Figure 9 The schematic diagram of the pressure storage resonance flow limiting module mainly includes: a pressure storage cavity 163, a liquid cooling pipe inlet 164, a resonance block 165, an intermediate block 166, a reset spring 167, an ammonia inlet hole 168, a prismatic sealing block 169, a flow limiting piston 170, an ammonia inlet channel 171, a storage cavity 172, a resonance block ammonia inlet passage 173, an intermediate cavity 174, a resonance block ammonia inlet passage throttling hole 175, a valve seat 176, an intermediate hole 177, and a reset spring 178. The module ensures the stability of ammonia fuel, adjusts the pressure fluctuation in the system by using a resonance block, and simultaneously designs a flow limiter to prevent abnormal injection.

[0059] Figure 10 The schematic diagram of the resonance block mainly includes: a first ammonia inlet passage 179, a first ammonia inlet throttling hole 180, a second ammonia inlet throttling hole 181, a first ammonia inlet cavity 182, a first ammonia outlet passage 183, a second ammonia inlet passage 184, a second ammonia inlet cavity 185, a communication hole 186, and a second ammonia outlet passage 187.

[0060] Figure 11 The schematic diagram of the super-magnetic electromagnetic control actuator mainly includes: main and auxiliary magnetic poles 188, a coil 189, a hysteresis seat 190, an upper valve rod 191, a reset spring 192, a valve rod intermediate cavity 193, a buffer cavity 194, an oil inlet and return hole 195, a reset spring 196, a super-hysteresis material 197, a limit block 198, an oil inlet passage 199, an oil return passage 200, a lower end spool valve 201, a fungus-shaped valve 202, and an oil return oil channel 203.

[0061] Figure 12 The schematic diagram of the phase-change controllable super-atomization nozzle module mainly includes: an ammonia inlet pipeline 204, an ammonia storage cavity 205, a static leakage-free cylinder 206, a reset spring 207, a gasket 208, a liquid cooling working medium inlet pipeline 209, a valve seat 210, a control cavity 211, a control valve rod upper end face 212, a liquid cooling working medium outlet pipeline 213, a needle valve body 214, a needle valve sealing surface 215, a jet flow channel 216, and a nozzle body 217.

[0062] Figure 13The schematic diagram of the sub-pressurization module mainly comprises: main and sub magnetic poles 218, coil 219, oil inlet channel 220, intermediate pipeline 221, sealing ball 222, reset spring 223, pressurized oil pipeline 224, pressurized piston lower surface 225, valve rod reset spring 226, armature 227, oil return pipeline 228, double-sealed valve rod 229, pressurized piston upper surface 230, intermediate cavity 231, pressurized piston reset spring 232.

[0063] Figure 14 The schematic diagram of the pressure balance type electromagnetic control actuator mainly comprises: oil inlet pipe 233, main and sub magnetic poles 234, coil 235, armature 237, oil inlet pipelines 233, 236, 238, reset springs 239, 240, balance valve rod 241, oil inlet pipe 242, oil return throttle hole 243, oil inlet throttle hole 244.

[0064] Figure 15 The schematic diagram of the needle valve eccentric self-adjusting nozzle mainly comprises: intermediate block 245, oil containing groove 246, self-adjusting valve block 247, reset spring 248, needle valve lower end surface 249, spray hole 250, control cavity 251, control valve rod upper end surface 252, needle valve body 253, nozzle body 254, needle valve sealing surface 255, and nozzle seat surface 256.

[0065] Figure 16 、 17 The designed super-atomizing nozzle adopts an inner cone structure as a whole, realizes multi-layer sealing, and at the same time, sprays nearly a hundred spray holes, which guarantees sufficient fuel atomization from the structural perspective. The fuel and air are fully mixed and completely combusted.

[0066] The liquid ammonia storage tank 24 stores the fuel of the system, adopts high-pressure low-temperature storage mode, and ensures that the ammonia fuel is in stable liquid state. At the same time, in the initial stage of fuel supply, a hydrogen and nitrogen preparation module is set up, the stored liquid ammonia is converted into ammonia gas, and then the purified ammonia gas is used to prepare hydrogen gas required for combustion and nitrogen gas required for system purging. And are respectively stored in the hydrogen storage tank 25 and the nitrogen storage tank 23. The liquid ammonia stored in the liquid ammonia storage tank 24 is first pumped by the pump ammonia system 22, and the low-pressure pump and the high-pressure pump are used to realize the pressurization of the liquid ammonia to meet the requirements of supply and combustion. Among them, the overflow valve 32 and the safety valve 33 are arranged in the low-pressure loop and the high-pressure loop respectively. The overflow valve 32 is arranged in the low-pressure loop to control the delivery pressure, and when the pressure is too high, the excess liquid ammonia returns to the liquid ammonia storage tank 24 through the overflow valve 32. The safety valve 33 is arranged in the high-pressure loop to control the high-pressure fuel delivery pressure, and the output pressure is adjusted by active control, and the excess liquid ammonia returns to the liquid ammonia storage tank 24 through the safety valve 33. For the fuel of liquid ammonia which is easy to phase change, a thermal management module needs to be set up, and the temperature controller 34 is used to adjust the temperature of the liquid ammonia output, and the phase state of the ammonia fuel is controlled through pressure and temperature. Then the fuel enters the liquid ammonia storage diverter 35, and through the comprehensive control of double valves and double cavities, the stable supply of the fuel is ensured, and then through the storage tank 36, the control valve 37 is supplied into the ammonia inlet 38, and then introduced into the liquid ammonia common rail pipe 1. The liquid ammonia common rail pipe 1 in the system adopts a double-layer structure to avoid liquid ammonia leakage to the atmosphere. At the same time, ammonia gas leakage detection sensors are arranged at the port of the common rail pipe to feedback the system in time. The liquid ammonia in the liquid ammonia common rail pipe 1 is supplied to the liquid ammonia injector 8 through the double-layer high-pressure ammonia pipe 2, and is injected into the cylinder through the electromagnetic valve control in the injector.

[0067] The oil tank 7 stores diesel oil as an ignition in the system, and the high-pressure oil pump 4 draws fuel from the oil tank 7. A filter 6 is arranged between the high-pressure oil pump 4 and the oil tank 7, and the fuel is filtered through the filter 6. Then the fuel is delivered to the common rail pipe 11, and a plurality of hydraulic oil outlets are opened on the common rail pipe 11. Each hydraulic oil outlet is connected with the injector through the high-pressure oil pipe 13, and is injected into the cylinder through the electromagnetic valve control in the injector.

[0068] Liquid ammonia fuel enters the pressure accumulation cavity 163 through the one-way ammonia inlet 136, which functions as a one-way valve. When the liquid ammonia supply pressure is greater than the spring pre-tightening force of the one-way valve, the cone valve opens against the spring force, and the liquid ammonia is supplied into the pressure accumulation cavity. When the pressure of the one-way ammonia inlet 136 is low, the cone valve closes again, also sealing the liquid ammonia in the system. After the fuel enters the pressure accumulation cavity 163, it is supplied downward through the resonance block 165. The resonance block 165 is composed of three pipelines 179, 181 and 184. The fuel flows into the flow restrictor from the three pipelines, respectively. The first ammonia inlet 179 is the main flow channel, and a first ammonia throttling hole 180 is arranged in the middle to filter the liquid ammonia flow, and then the liquid ammonia flows into the first ammonia cavity 182. The second ammonia inlet 184 is the auxiliary flow channel, and no throttling hole is arranged in the middle. After passing through the second ammonia cavity 185 and the second ammonia outlet 187, the liquid ammonia directly flows into the flow restrictor. The second ammonia throttling hole 181 and the communication hole 186 are the main structures for realizing resonance, which change the phase of pressure wave fluctuation, adjust the fluctuation frequency, and adjust the corresponding relationship between the wave crest and the wave trough, so as to realize the controllable pressure wave coupling process. Especially in the supercharging mode, the stability of the system is ensured. The flow restrictor assembly is arranged inside the injector body through the pressure accumulation cavity 163. The middle block 166 not only limits the overall flow restrictor assembly, but also cooperates with the return spring 167. On the one hand, it serves as a spring seat for the return spring 167, and on the other hand, it limits the maximum displacement of the flow restrictor piston. Under the action of the spring pre-tightening force of the damping spring and the ball valve return spring, the upper end surface of the prismatic sealing block 169 and the flow restrictor piston 170 cooperates with the upper end surface of the support control valve seat 176. The valve seat 176 is pressed at the bottom under the action of the spring force of the return spring, and the upper part forms the seat surface of the prismatic sealing block. The liquid ammonia flows into the middle cavity 174 from the resonance block, and then flows into the flow restrictor through the oil inlet hole 168 and the resonance block ammonia inlet throttling hole 175. Under the action of the liquid pressure, the prismatic sealing block 169 moves downward against the spring force as the liquid ammonia is supplied. When the fuel supply is higher than the limit value, the prismatic sealing block 169 cooperates with the valve seat 176 to realize sealing and cut off the fuel supply, thereby avoiding cylinder pulling. After the fuel supply is interrupted, the prismatic sealing block 169 is quickly reset under the action of the spring force.

[0069] The diesel fuel enters the pressure accumulation resonance flow restrictor module 138 through the one-way oil inlet 141, and then is supplied downward into the auxiliary supercharging module 143. The supercharged fuel is supplied to the diesel fuel injector through the one-way valves 222 and 223, respectively, and is supplied to the pressure balance type electromagnetic control actuator 144 and the needle valve eccentric self-adjusting nozzle 145, respectively, to control the injection of the ammonia fuel injector and the diesel fuel injector, respectively, and to provide fuel for the diesel fuel injector.

[0070] The liquid ammonia is supplied into the ammonia storage cavity through the ammonia inlet channel, and is sprayed into the cylinder by the super-magnetic electromagnetic control actuator and the super-atomizing nozzle module. In the present application, in order to ensure the accuracy of the fuel injector control, diesel oil is used as the servo oil, the pressure level in the control cavity is adjusted, the force acting on the needle valve is changed, and thus the injection timing is controlled. The high-pressure diesel oil flows into the electromagnetic actuator through the oil inlet channel 199, when not powered, is subjected to the pre-tightening force of the spring 192, 196, the mushroom valve 202 is in a sealed state, the electromagnetic actuator pipeline is disconnected with the oil return pipeline. The lower end valve 201 is in an open state, the diesel oil is supplied to the control cavity 211 through the oil inlet channel 199 and the flow channel of the lower end valve 201. The diesel oil flows into the control cavity 211 through the oil inlet and return hole 195 and the buffer cavity 194. The buffer cavity reduces the fuel pressure fluctuation at the control valve, and collects the leaked fuel through the pressure difference of the high-pressure contact surface structure. The fuel flows into the control cavity 211, is sealed by the no-static leakage cylinder 206 and the needle valve sealing surface 215, the pressure in the control chamber is adjusted, the force difference acting on the needle valve is changed, and thus the accurate control of the fuel injection is realized.

[0071] In the present application, the diesel oil injector adopts the balanced valve control mode, and the balanced valve rod is pressed by the armature. Since the whole is immersed in high-pressure fuel and is subjected to the balancing force, a higher common rail pressure (250 MPa) can be realized, thereby reducing the mass of the whole valve, i.e. reducing the electromagnetic force requirement and increasing the control response. Thus, only a smaller size electromagnetic valve and armature and a smaller spring pre-tightening force are required. Meanwhile, the balanced valve rod is not directly subjected to high impact, and the pitting phenomenon of the traditional ball valve is prevented, and the system reliability is increased. The high-pressure diesel oil flows into the control cavity 251 through the oil inlet channel 242 and the oil inlet throttling hole 244, when not powered, is subjected to the pre-tightening force of the spring 240, the armature 237 and the balanced valve rod 241 are in a sealed state, the electromagnetic actuator pipeline is disconnected with the oil return pipeline. The diesel oil is supplied to the control cavity 251 through the oil inlet channel 242 and the oil inlet throttling hole 244 flow channel. The existence of the oil return cavity reduces the fuel pressure fluctuation at the control valve. The fuel flows into the control cavity 251, and the control cavity is combined by the middle block 245, the self-adjusting valve block 247 and the upper end surface 252 of the control valve rod to realize sealing. The pressure in the control chamber is adjusted, the force difference acting on the needle valve is changed, and thus the accurate control of the fuel injection is realized. The combination of the middle block 245 and the self-adjusting valve block 247 solves the problem of leakage of the traditional no-static block, and prevents the wear and leakage problem caused by the eccentricity of the needle valve. The working principles of the main and auxiliary supercharging modules in the present application are similar, and the working principle of the main supercharging module in the specific injection process is as follows:

[0072] When working in the non-boost mode, the boost control valve part is not energized. Because the pressure of each action surface of the boost piston is balanced at this time, the armature 156 and the double-seal valve rod 158 are in a compressed state under the action of the spring pre-tightening force 149, 155, and the ammonia inlet channel 160 is sealed. At this time, there is no fuel supply in the boost module, and the boost piston is in a reset state under the action of the spring pre-tightening force, without the boost function. Therefore, the ammonia fuel in the system is stored in the pressure accumulation cavity 163 after passing through the one-way ammonia inlet 136, and flows into the flow limiting valve through the resonance cavity 165. During the injection process, due to the throttling effect of the resonance block 165 on the liquid ammonia, the pressure of the intermediate hole 177 in the flow limiting piston 170 and the fuel in the storage cavity 172 is lowered relative to the pressure above the resonance block 165, forming a pressure difference with the pressure in the pressure accumulation cavity 163. Therefore, the flow limiting piston 170 and the prismatic sealing block 169 as a whole are displaced downward, so that the chamber below the flow limiting piston 170 is compressed to a certain extent, and the pressure of the injection is compensated to a certain extent. The liquid ammonia passing through the flow limiting valve is supplied into the ammonia tank 246 through the ammonia inlet pipe. When the pressure balance type electromagnetic control actuator is energized, the armature 237 is affected by the magnetic field, moves upward to overcome the spring pre-tightening force 239, 240, opens the oil return channel, and connects the control cavity 251 with the low-pressure leakage hole. The fuel in the control cavity 251 flows back to the low-pressure cavity through the low-pressure oil leakage hole. When the resultant force of the pressure in the control cavity 251 and the elastic force of the needle valve spring 248 is smaller than the upward hydraulic pressure in the oil tank 246, the needle valve body 253 is lifted upward, the injection hole is opened, and the injector starts to inject. When the injection control valve part is de-energized, the armature 237 moves downward under the action of the spring pre-tightening force, re-seals the oil return channel. At the same time, the balance valve rod 241 is driven to move downward to realize sealing. The control cavity 251 re-pressurizes through the oil inlet throttling hole 244. When the resultant force of the pressure in the control cavity 251 and the elastic force of the needle valve spring 248 is greater than the upward hydraulic pressure in the oil tank 246, the needle valve body 253 re-seats, and the injector stops injecting. When the injector stops working, the pressure difference between the upper and lower surfaces of the flow limiting piston 170 gradually decreases as the liquid ammonia flows through the intermediate hole 177. Under the action of the reset spring, the flow limiting piston 170 and the prismatic sealing block 169 as a whole return to the initial position.

[0073] When working in the boost mode, the boost control valve is energized, the coil 151 is energized, the main and auxiliary magnetic poles 150 form an electromagnetic force, attracting the armature 156 to move upward, and at the same time driving the double-seal valve rod 158 to move upward, opening the ammonia inlet channel 160 and closing the ammonia return channel. Liquid ammonia accumulates on the upper surface 153 of the boost piston, increasing the force on the upper surface, and the pressure difference between the upper and lower surfaces overcomes the spring force, causing the boost piston to move downward. The volume of the lower pressure storage chamber is compressed, and the pressure is increased. Both the boost module and the pressure balanced electromagnetic control actuator can adopt two control modes, one of which is in the form of liquid ammonia boost liquid ammonia, and the other is in the form of diesel boost liquid ammonia. In the boost module, the intermediate chamber 154 can be used as a boost oil leakage collection chamber, and at the same time, fuel can seal the liquid ammonia. The boosted liquid ammonia flows into the flow limiting valve through the resonant chamber 165. The liquid ammonia passing through the flow limiting valve is supplied to the ammonia storage chamber 205 through the pipeline 171. When the pressure balanced electromagnetic control actuator 144 is energized, it is affected by the magnetic field, and the armature 237 overcomes the spring pre-tightening force 240 to move upward, opening the oil return channel, and the control chamber 251 is connected with the low pressure leakage hole, and the fuel in the control chamber 251 flows back to the low pressure chamber through the low pressure oil leakage hole. When the combined force of the pressure in the control chamber 251 and the spring force of the needle valve spring 248 is less than the upward hydraulic pressure in the oil tank 246, the needle valve body 253 is lifted upward, the injection hole is opened, and the injector starts to inject oil. When the oil injection control valve part is de-energized, it loses the influence of the magnetic field and is affected by the spring pre-tightening force, and the armature 237 moves downward to reseal the oil return oil way. At the same time, the balance valve rod 241 moves downward to achieve sealing. The control chamber 251 repressurizes through the oil inlet throttle hole 244, and when the combined force of the pressure in the control chamber 251 and the spring force of the needle valve spring 248 is greater than the upward hydraulic pressure in the oil tank 246, the needle valve body 253 reseats, and the injector stops injecting.

[0074] In the boost resonant flow limiting module 138 and the super-atomizing nozzle module 140, a heat management module is designed, including the inlet and outlet of the refrigerant. The phase state of the liquid ammonia is comprehensively controlled through temperature and pressure, and the phase state of the liquid ammonia in the injection process is controllable.

[0075] Ammonia and hydrogen are supplied to the hydrogen fuel cell system, hydrogen is supplied to hydrogen inlet 52, purged by nitrogen 53, filtered by hydrogen filter 54, flow pressure is monitored by pressure sensor 55, when the pressure requirement is met, the shut-off valve 56 is opened, when the pressure is too large, the shut-off valve 56 is closed. Then by high-pressure gas injection valve 57 and ejector pump and hydrogen circulating pump 58, the anode 61 of the stack is supplied. The exhaust gas of the anode 61 of the stack is discharged outwardly through the water separator 63, the drain valve 64 and the exhaust valve 65. Air is filtered by air inlet 67 through air filter 68, flow pressure is monitored by pressure sensor 69, is pressurized and physical property adjusted by air compressor 70, intercooler 71 and humidifier 72, is transmitted to shut-off valve 73 and then is supplied to the cathode 75 of the stack. Excess air supply is discharged outwardly by by-pass valve 74 together with the exhaust gas of the cathode 75 of the stack through humidifier 72, through throttle valves 80, 81, excess hydrogen 82 of the anode, flow through muffler 83, and is discharged through outlet 84.

[0076] The cooling requirements of the fuel cell and the dual fuel injection system in the system are realized by the cooling system 28. In the present application, the cooling water in the water tank is a glycol solution, heat exchange fins are added to the wall surface of the water tank, phase change is realized by the branch of ammonia 24 stored in the system, boiling heat exchange is realized, and the solution in the water tank is preliminarily cooled. This takes advantage of the function of ammonia fuel as a refrigerant, greatly reducing the work of the cooling water pump 86, 100. The cooled glycol solution is secondarily cooled by the cooling water pump 86, 100 to meet the cooling requirements of the system, the intercooler 90, 104 reduces the temperature of the inlet air, and ions in the solution are removed by the deionizer 94, 108 to obtain pure water. The solution temperature is adjusted by the heater 92, 106, and the treated cooling water is discharged through the cooling water outlet 99, 112 to realize the cooling requirements of the heat engine and the fuel cell. At the same time, the two-loop parallel form is adopted, and the power and refrigeration capacity can be adjusted according to the requirements of different components.

[0077] Liquid ammonia enters the three-way valve 115 through the heater 114 from the liquid ammonia inlet 113, and the three-way valve 115 functions as a diverter valve. When the low-power compressor 121 is working, the high-pressure steam discharged by the compressor passes through the filter 120 and the sensor 117 to enter the radiator, and the working medium is condensed to enter the electronic expansion valve 130, 125, passes through the sensor 124 to enter the refrigeration heat exchanger 123 and evaporates therein to absorb heat, thereby realizing the refrigeration function, and then returns to the low-power compressor through the sensor 122.

[0078] When switching to the heating mode, the system cools the power system piston and the injector related components. The working medium is discharged by the high-power compressor 126 to produce high-pressure steam, enters the heating heat exchanger 128 through the sensor 127 to condense and release heat, then enters the radiator 116 through the one-way check valve 129 and the electromagnetic expansion valve 130, and the working medium evaporates and absorbs heat at the radiator 116, then returns to the high-power compressor through the sensor 117 and the electromagnetic reversing valve 118 to realize the air source heating cycle.

[0079] The system can also realize the air source heating mode. The working medium is discharged by the high-power compressor 126 to produce high-pressure steam, enters the heating heat exchanger 128 through the sensor 127 to condense and release heat, then enters the radiator 116 through the one-way check valve 129 and the electromagnetic expansion valve 130, and the working medium evaporates and absorbs heat at the radiator 116, then returns to the high-power compressor through the sensor 117 and the electromagnetic reversing valve 118 to realize the air source heating cycle.

[0080] As can be seen from the above description, the present application realizes one ammonia three use: power device fuel supply, cooling system refrigerant and hydrogen supply source of fuel cell. Through the liquid ammonia-diesel fuel integrated design, the installation space is saved, the diesel fuel supply controls the injection of the ammonia fuel injector and the diesel fuel injector at the same time, and fuel is provided for the diesel fuel injector. Based on the phase change cooling principle of liquid ammonia, a double-acting heat pump module is innovatively designed, which can effectively solve the engine cold start problem under cold conditions, reduce the power consumption of the compressor, realize waste heat utilization, and improve the energy utilization rate. At the same time, the injection process is combined with the thermal management design to adjust and control the phase change conversion of the ammonia fuel from the aspects of pressure and temperature. A multi-valve cooperative control form is adopted to realize the variable cycle of the liquid ammonia injection process, so that the injection amount and injection timing are more accurate and flexible. The present application can adopt a main and auxiliary supercharging mode. In the supercharging mode, the injection pressure and injection rate of the fuel injection are affected by the supercharging mode, and the injection can be controlled between cycles. The structure of the super-magnetic electromagnetic control actuator is adopted to ensure the accurate control of the ammonia fuel injection. The balance valve control mode is adopted. Since the whole bubble is in the high-pressure fuel and is affected by the balance force, a higher common rail pressure (250 MPa) can be realized, so that the mass of the whole valve is reduced, that is, the electromagnetic force demand is reduced, and the control corresponding is increased. Therefore, only a smaller size electromagnetic valve and armature are needed to cooperate with a smaller spring pre-tightening force. At the same time, the balance valve rod is not directly affected by the high impact, which prevents the pitting phenomenon of the traditional ball valve and increases the system reliability. The combination design of the intermediate block and the self-adjusting valve block solves the leakage problem of the traditional static block, and prevents the wear and leakage problem caused by the eccentricity of the needle valve.

Claims

1. A liquid ammonia phase change cooling hybrid thermal management system characterized by: The application relates to a liquid ammonia and hydrogen supply system and a diesel injector. The injector comprises an injector body, a liquid ammonia injection part and a diesel injection part, and the liquid ammonia injection part and the diesel injection part are both located in the injector body; wherein the liquid ammonia injection part comprises, from top to bottom, a pressure boosting module, a first pressure accumulation and resonance flow limiting module, an ultra-magnetic hysteresis electromagnetic control actuator and a phase-change controllable super-atomization nozzle module; the diesel injection part comprises, from top to bottom, a second pressure accumulation and resonance flow limiting module, a sub-pressure boosting module, a pressure balance type electromagnetic control actuator and a needle valve eccentric self-adjusting nozzle. The pressure boosting module comprises a pressure boosting yoke, pressure boosting main and auxiliary magnetic poles, a main pressure boosting piston, a pressure boosting armature, a pressure boosting limiting block, a pressure boosting double-sealing valve rod, a pressure boosting upper valve rod seat and a pressure boosting lower valve rod seat; the pressure boosting armature is sleeved on the top of the pressure boosting double-sealing valve rod; a pressure boosting reset spring is arranged between the pressure boosting yoke and the pressure boosting armature; the pressure boosting main and auxiliary magnetic poles are arranged outside the pressure boosting reset spring; the pressure boosting main and auxiliary magnetic poles are wound with coils; the middle part of the pressure boosting double-sealing valve rod is located in the pressure boosting upper valve rod seat; the bottom part of the pressure boosting double-sealing valve rod is located in the pressure boosting lower valve rod seat; the middle part of the pressure boosting double-sealing valve rod is sleeved with a pressure boosting valve rod reset spring; a pressure boosting double-sealing protrusion is arranged between the middle part and the bottom part of the pressure boosting double-sealing valve rod; sealing surfaces are arranged on the corresponding surfaces of the pressure boosting upper valve rod seat, the pressure boosting lower valve rod seat and the pressure boosting double-sealing valve rod; the main pressure boosting piston is located below the pressure boosting lower valve rod seat; a main pressure boosting piston reset spring is sleeved outside the main pressure boosting piston; a back ammonia channel is arranged in the pressure boosting upper valve rod seat; an ammonia inlet channel and an intermediate pipeline are arranged in the pressure boosting lower valve rod seat; the space in which the pressure boosting double-sealing protrusion is located in the pressure boosting lower valve rod seat is a communication space; the communication space is communicated with the intermediate pipeline. The first pressure accumulation resonance current limiting module comprises a resonance block, an intermediate block, a prismatic sealing block, a current limiting piston and a pressure accumulation valve seat, a pressure accumulation cavity is arranged in the injector body below the main booster piston, a one-way ammonia inlet is mounted on the side wall of the pressure accumulation cavity, a liquid cooling pipe inlet is arranged on the injector body and communicates with the pressure accumulation cavity, the resonance block, the intermediate block, the prismatic sealing block and the pressure accumulation valve seat are sequentially arranged below the pressure accumulation cavity, the current limiting piston is arranged in the pressure accumulation valve seat, an intermediate block reset spring is arranged in the intermediate block, an ammonia inlet hole and a resonance block ammonia inlet throttling hole are arranged at the bottom of the intermediate block, the prismatic sealing block is located above the current limiting piston, an intermediate hole is arranged in the current limiting piston, a current limiting piston reset spring is arranged below the current limiting piston, and a storage cavity is arranged below the current limiting piston reset spring. The resonance block is respectively provided with a first ammonia inlet, a second ammonia inlet, a first ammonia cavity, a second ammonia cavity, a first ammonia outlet and a second ammonia outlet, the first ammonia cavity respectively communicates with the first ammonia inlet and the first ammonia outlet, the second ammonia cavity respectively communicates with the second ammonia inlet and the second ammonia outlet, the first ammonia cavity and the second ammonia cavity communicate through a communication hole, the first ammonia cavity communicates with the first ammonia inlet through a first ammonia throttling hole, the first ammonia cavity communicates with the pressure accumulation cavity through a second ammonia throttling hole, and the first ammonia inlet and the second ammonia inlet communicate with the pressure accumulation cavity. The second pressure accumulation resonance current limiting module has the same structure as the first pressure accumulation resonance current limiting module and is arranged in parallel in the injector body. The liquid ammonia phase change cooling type hybrid power thermal management system further comprises a hydrogen fuel cell system, the hydrogen fuel cell system comprises an anode, a cathode, a hydrogen inlet, a nitrogen inlet and an air inlet, the hydrogen storage tank is connected with the hydrogen inlet, the nitrogen storage tank is connected with the nitrogen inlet, the hydrogen inlet and the nitrogen inlet are combined and then supplied to the anode through a hydrogen filter, a first shut-off valve, a high-pressure gas injection valve, an eductor pump and a hydrogen circulating pump, waste gas of the anode passes through a water separator and is discharged through a drain valve and an exhaust valve respectively, and air is supplied to the cathode through an air filter, an air compressor, a first intercooler, a humidifier and a second shut-off valve.

2. The liquid-ammonia phase change cooling hybrid thermal management system of claim 1, wherein: The super-magnetic hysteresis electromagnetic control actuator comprises a super-magnetic hysteresis main and auxiliary magnetic pole, a magnetic hysteresis seat, a super-magnetic hysteresis upper valve rod, a super-magnetic hysteresis lower end taper valve and a super-magnetic hysteresis bacteria-shaped valve, a coil is wound in the super-magnetic hysteresis main and auxiliary magnetic pole, a super-magnetic hysteresis material is arranged in the through hole of the super-magnetic hysteresis main and auxiliary magnetic pole, the magnetic hysteresis seat, the super-magnetic hysteresis upper valve rod, the super-magnetic hysteresis lower end taper valve and the super-magnetic hysteresis bacteria-shaped valve are sequentially arranged below the super-magnetic hysteresis material, the super-magnetic hysteresis bacteria-shaped valve is located in a super-magnetic hysteresis bacteria-shaped valve cavity, a super-magnetic hysteresis bacteria-shaped valve reset spring is arranged below the super-magnetic hysteresis bacteria-shaped valve, an oil return oil way and an oil inlet oil way are arranged in the injector body of the super-magnetic hysteresis electromagnetic control actuator, a super-magnetic hysteresis taper valve oil inlet hole is arranged in the super-magnetic hysteresis lower end taper valve shell outside the super-magnetic hysteresis lower end taper valve, and the super-magnetic hysteresis taper valve oil inlet hole communicates with the oil inlet oil way.

3. The liquid-ammonia phase change cooling hybrid thermal management system of claim 1, wherein: The phase change controllable ultra-atomization nozzle module comprises an ultra-atomization nozzle body, an ultra-atomization valve seat, a static leakage-free cylinder, an ultra-atomization needle valve body and an ultra-atomization control valve rod, the ultra-atomization valve seat is located in the ultra-atomization nozzle body, the static leakage-free cylinder and the ultra-atomization needle valve body are located in the ultra-atomization valve seat, the head of the ultra-atomization needle valve body is located in the static leakage-free cylinder, the middle part of the ultra-atomization needle valve body is provided with an ultra-atomization needle valve body reset spring between the static leakage-free cylinder, the static leakage-free cylinder, the ultra-atomization needle valve body and the ultra-atomization valve seat form an ammonia storage cavity, the ultra-atomization valve seat and the ultra-atomization nozzle body form a liquid cooling working medium inlet pipeline and a liquid cooling working medium outlet pipeline, the bottom of the ultra-atomization needle valve body and the bottom of the ultra-atomization valve seat form an ultra-atomization injection flow channel, the ammonia storage cavity is communicated with the storage cavity, the top end of the ultra-atomization needle valve body and the injector body above it form an ultra-atomization control cavity.

4. The liquid-ammonia phase change cooling hybrid thermal management system of claim 1, wherein: The sub-boost module comprises a sub-boost yoke, a sub-boost main and auxiliary magnetic pole, a sub-boost piston, a sub-boost armature, a sub-boost limit block, a sub-boost double-sealing valve rod, a sub-boost upper valve rod seat and a sub-boost lower valve rod seat, the sub-boost armature is sleeved on the top of the sub-boost double-sealing valve rod, the sub-boost reset spring is arranged between the sub-boost yoke and the sub-boost armature, the outer side of the sub-boost reset spring is provided with the sub-boost main and auxiliary magnetic pole, the sub-boost main and auxiliary magnetic pole is wound with a coil, the middle part of the sub-boost double-sealing valve rod is located in the sub-boost upper valve rod seat, the bottom of the sub-boost double-sealing valve rod is located in the sub-boost lower valve rod seat, the middle part of the sub-boost double-sealing valve rod is sleeved with a sub-boost valve rod reset spring, the sub-boost double-sealing protrusion is arranged between the middle part and the bottom of the sub-boost double-sealing valve rod, the corresponding surfaces of the sub-boost upper valve rod seat, the sub-boost lower valve rod seat and the sub-boost double-sealing valve rod are all provided with sealing surfaces, the sub-boost piston is located below the sub-boost lower valve rod seat, the sub-boost piston is externally sleeved with a sub-boost piston reset spring, the sub-boost upper valve rod seat is provided with an oil return pipeline, the lower valve rod seat is provided with a sub-boost oil channel and a sub-boost communication passage, the sub-boost oil channel is respectively communicated with an oil inlet channel and below the sub-boost double-sealing protrusion, the space where the sub-boost double-sealing protrusion is located is a communication space, the sub-boost communication passage is respectively communicated with the communication space and above the sub-boost piston, the oil inlet channel is provided with a sealing ball, below the sealing ball is provided with a sealing ball reset spring, below the sub-boost piston is a boost oil pipeline, the boost oil pipeline is communicated with the oil inlet channel below the sealing ball reset spring.

5. The liquid-ammonia phase change cooling hybrid thermal management system of claim 1, wherein: The pressure balance type electromagnetic control actuator comprises a pressure control type main and auxiliary magnetic pole, a pressure control type armature and a balance valve rod, the upper part of the balance valve rod is arranged in the pressure control type main and auxiliary magnetic pole, the lower part of the balance valve rod is located in the pressure control type armature, the pressure control type armature is located below the pressure control type main and auxiliary magnetic pole, the pressure control type armature and below the balance valve rod are provided with a pressure control type oil return hole upper section and a pressure control type oil return hole lower section, the pressure control type oil return hole upper section and the pressure control type oil return hole lower section are communicated through a pressure control type oil return throttle hole, the pressure control type oil return hole lower section is communicated with an oil inlet pipeline through a pressure control type oil inlet throttle hole.

6. The liquid-ammonia phase change cooling hybrid thermal management system of claim 5, wherein: The needle valve eccentric self-adjusting nozzle comprises an eccentric self-adjusting intermediate block, an eccentric self-adjusting needle valve body, an eccentric self-adjusting needle valve body shell, an eccentric self-adjusting valve block and an eccentric self-adjusting nozzle body, the eccentric self-adjusting needle valve body is located in the eccentric self-adjusting needle valve body shell, the eccentric self-adjusting needle valve body is located in the eccentric self-adjusting nozzle body, the pressure-controlled oil return hole lower section is arranged in the eccentric self-adjusting intermediate block, the lower end of the eccentric self-adjusting intermediate block is connected with the eccentric self-adjusting valve block, the top of the eccentric self-adjusting needle valve body is located in the eccentric self-adjusting valve block, the eccentric self-adjusting needle valve body, the eccentric self-adjusting valve block and the eccentric self-adjusting intermediate block form an eccentric self-adjusting control cavity, the eccentric self-adjusting control cavity is communicated with the pressure-controlled oil return hole lower section, the eccentric self-adjusting needle valve body middle part is provided with an eccentric self-adjusting needle valve body protrusion, the eccentric self-adjusting needle valve body protrusion is sleeved with an eccentric self-adjusting needle valve body reset spring, the eccentric self-adjusting needle valve body is of an eccentric structure, and a part thereof is attached to the inner wall of the eccentric self-adjusting needle valve body shell outside the eccentric self-adjusting needle valve body.

7. The liquid-ammonia phase change cooling hybrid thermal management system of claim 1, wherein: The liquid ammonia phase change cooling type hybrid power thermal management system further comprises a cooling system, the cooling system comprises a water tank, a first radiator, a first deionizer, a first heater, a second intercooler and a first cooling connection port, the first radiator, the first deionizer, the first heater, the second intercooler and the first cooling connection port are connected in parallel to form a first cooling unit, the water tank is connected with the first cooling unit, the first cooling connection port is connected with a cooling water outlet, and the first cooling unit is connected with an outlet through a flow valve; a second cooling unit is symmetrically arranged with the first cooling unit, the second cooling unit comprises a second radiator, a second deionizer, a second heater, a third intercooler and a second cooling connection port, and the second cooling unit is arranged in the same manner and symmetrically with the first cooling unit.

8. The liquid-ammonia phase change cooling hybrid thermal management system of claim 1, wherein: The liquid ammonia phase change cooling type hybrid power thermal management system further comprises a double-acting heat pump, the double-acting heat pump comprises a liquid ammonia inlet, a three-way valve, a low-power compressor, a high-power compressor, a refrigeration heat exchanger, a heating heat exchanger and a third radiator, the liquid ammonia storage tank is connected with the liquid ammonia inlet, the liquid ammonia inlet is connected with the three-way valve, high-pressure steam at the low-power compressor outlet enters the third radiator, the high-pressure steam is condensed through a first electronic expansion valve and a second electronic expansion valve to enter the refrigeration heat exchanger, and returns to the low-power compressor; high-pressure steam at the high-power compressor outlet enters the heating heat exchanger to be condensed and release heat, enters a branch with an expansion valve through a single check valve and a first electronic expansion valve, liquid working medium in the branch with the expansion valve evaporates into gaseous working medium, and returns to the high-power compressor.

9. The liquid-ammonia phase change cooling hybrid thermal management system of claim 1, wherein: The liquid ammonia phase change cooling type hybrid thermal management system further comprises a liquid ammonia-diesel dual fuel cylinder, the liquid ammonia-diesel dual fuel cylinder comprising a cylinder body, a piston, a crank, an air inlet pipe and an air outlet pipe, the air inlet pipe, the air outlet pipe and an injector being arranged above the cylinder body respectively, the piston being arranged in the cylinder body, the crank being connected below the piston, the air inlet pipe being connected with the cylinder body as an air inlet, the air inlet being provided with an air inlet valve rod, the air inlet valve rod being sleeved with an air inlet valve rod spring, the air outlet pipe being connected with the cylinder body as an air outlet, the air outlet being provided with an air outlet valve rod, the air outlet valve rod being sleeved with an air outlet valve rod spring, the air inlet pipe being provided with a hydrogen air inlet, the hydrogen air inlet and the air inlet being provided with an air inlet, and the hydrogen air inlet and the air inlet being provided with a safety valve.

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