Patent Publication Number: US-2023160330-A1

Title: Liquid ammonia phase-change cooling type hybrid power thermal management system

Description:
CROSS REFERENCE TO RELATED APPLICATION(S) 
     This patent application claims the benefit and priority of Chinese Patent Application No. 202111374434.4, filed on Nov. 19, 2021, the disclosure of which is incorporated by reference herein in its entirety as part of the present application. 
     TECHNICAL FIELD 
     The present disclosure relates to an engine, and specifically relates to a hybrid power engine. 
     BACKGROUND 
     Under the large background of green and low-carbon ships, ship development enters a key transformation and upgrading period, the ships require high power flexibility in the future, and the power flexibility comprises flexible configuration of power devices, flexibility of fuel supply and injection systems and flexibility of fuel storage, lightering and filling. Power diversity and fuel diversity are inevitable trends of ship development, and therefore development and research of a low-carbon clean fuel supply and injection system for ships are key measures for meeting current and future technological development requirements and improving technological innovation, product competitiveness and enterprise influence Ammonia, as one of the typical low carbon fuels, is higher in energy storage and convenient to store and transport than hydrogen fuels, has a mature supply chain, and is one of main low-carbon alternative energy sources. 
     The ammonia fuel and other novel alternative fuels have the common characteristics of low viscosity, low flash point (liquid fuel), low carbon and low emission, so that existing equipment, especially a fuel supply and injection system, needs to be subjected to great technical upgrading and transformation to meet the use requirements of the novel fuels. Meanwhile, it is worth noting that although the novel alternative fuel has great emission reduction potential from the perspective of engine combustion emission, the existing alternative fuel needs to solve the problem of energy green regeneration from the whole life cycle of the fuel, so that the transformation of the whole energy industry chain is driven. At present, no mature ammonia fuel power device exists internationally, an ammonia fuel engine improved by a diesel engine has the problems of low volume efficiency, poor combustion effect, low heat efficiency and energy utilization rate and the like, and popularization and application are limited. 
     Thus, by adopting a diesel ignition combustion mode, an ammonia fuel injection system is designed, so that ammonia fuel is injected into a cylinder in a liquid state under high pressure, the operation compression ratio of the engine is improved, and the heat efficiency is effectively improved. Compared with existing patents, the double-acting heat pump module is innovatively designed based on the liquid ammonia phase-change cooling principle, firstly, the cold starting problem of the engine under the cold condition can be effectively solved, secondly, the power consumption of the compressor is reduced, waste heat utilization is achieved, and the energy utilization rate is improved. Meanwhile, a feasible ammonia fuel application path is provided, and ammonia can be used for three purposes: a fuel device fuel, a radiator system refrigerant and a discharge aftertreatment module reducing agent. The emission performance of the engine is improved, and the carbon emission is gradually reduced to the maximum extent while the dynamic property and the economical efficiency are guaranteed. 
     SUMMARY 
     The present disclosure aims to provide a liquid ammonia phase-change cooling type hybrid power thermal management system which can effectively solve the problem of cold start of an engine under a cold condition, reduce the power consumption of a compressor, realize waste heat utilization and improve the energy utilization rate. 
     The purpose of the present disclosure is realized as follows: 
     The liquid ammonia phase-change cooling type hybrid power thermal management system in the present disclosure comprises an injector, a liquid ammonia hydrogen supply system, a liquid ammonia common rail pipe, a fuel oil common rail pipe and an oil tank, wherein the liquid ammonia hydrogen supply system comprises a liquid ammonia storage tank, an ammonia pumping system, a flow dividing system and an ammonia inlet and outlet system, the fuel oil common rail pipe is respectively connected with the oil tank and a one-way oil inlet of the injector, the liquid ammonia common rail pipe is respectively connected with the ammonia inlet and outlet system and a one-way ammonia inlet of the injector, an ammonia inlet pipe and an ammonia return pipe are arranged in the ammonia inlet and outlet system, the ammonia pumping system comprises a liquid ammonia storage flow divider, a low-pressure pump and a high-pressure pump, the flow dividing system comprises a storage tank, an ammonia inlet control valve, a safety valve and an ammonia outlet control valve, an outlet of the liquid ammonia storage tank is sequentially connected with the low-pressure pump, the high-pressure pump, the liquid ammonia storage flow divider, the storage tank and the ammonia inlet control valve, the ammonia inlet control valve is connected with the liquid ammonia common rail pipe through the ammonia inlet pipe, an inlet of the liquid ammonia storage tank is sequentially connected with an ammonia return control valve and the safety valve, the safety valve is connected with the injector through the ammonia return pipe, and the liquid ammonia storage tank is respectively connected with a hydrogen storage tank and a nitrogen storage tank. 
     The present disclosure further has the following characteristics: 
     Firstly, the injector comprises an injector body, a liquid ammonia injection part and a diesel injection part, the liquid ammonia injection part and the diesel injection part are located in the injector body, the liquid ammonia injection part comprises a pressurizing module, a first pressure storage resonance flow-limiting module, a super-hysteresis electromagnetic control actuator and a phase-change controllable super-atomization nozzle module which are arranged from top to bottom, and the diesel injection part comprises a second pressure storage resonance flow-limiting module, an auxiliary pressurizing module, a pressure balance type electromagnetic control actuator and a needle valve eccentric self-adjusting nozzle which are arranged from top to bottom. 
     Secondly, the pressurizing module comprises a pressurizing magnet yoke, pressurizing main and auxiliary magnetic poles, a main pressurizing piston, a pressurizing armature, a pressurizing limited block, a pressurizing double-sealing valve rod, a pressurizing upper valve rod seat and a pressurizing lower valve rod seat, the pressurizing armature sleeves the top of the pressurizing double-sealing valve rod, a pressurizing reset spring is arranged between the pressurizing magnet yoke and the pressurizing armature, the pressurizing main and auxiliary magnetic poles are arranged on the outer side of the pressurizing reset spring, coils are wound around the pressurizing main and auxiliary magnetic poles, the middle of the pressurizing double-sealing valve rod is located in the pressurizing upper valve rod seat, the bottom of the pressurizing double-sealing valve rod is located in the pressurizing lower valve rod seat, the middle of the pressurizing double-sealing valve rod is sleeved with a pressurizing valve rod reset spring, a pressurizing double-sealing protrusion is arranged between the middle and the bottom of the pressurizing double-sealing valve rod, sealing surfaces are arranged on the surfaces, corresponding to the pressurizing double-sealing valve rod, of the pressurizing upper valve rod seat and the pressurizing lower valve rod seat, the main pressurizing piston is located below the pressurizing lower valve rod seat and externally sleeved with a main pressurizing piston reset spring, a connected ammonia return channel is arranged in the pressurizing upper valve rod seat, an ammonia inlet channel and a middle pipeline are arranged in the pressurizing lower valve rod seat, the space where the pressurizing double-sealing protrusion is located in the pressurizing lower valve rod seat is a connected space, and the connected space communicates with the middle pipeline. 
     Thirdly, the first pressure storage resonance flow-limiting module comprises a resonance block, a middle block, a prismatic sealing block, a flow-limiting piston and a pressure storage valve seat, a pressure storage cavity is formed in the injector body below the main pressurizing piston, the one-way ammonia inlet is formed in the side wall of the pressure storage cavity, a liquid cooling pipe inlet is formed in the injector body and communicates with the pressure storage cavity, the resonance block, the middle block, the prismatic sealing block and the pressure storage valve seat are sequentially arranged below the pressure storage cavity, the flow-limiting piston is arranged in the pressure storage valve seat, a middle block reset spring is arranged in the middle block, an ammonia inlet hole and a resonance block ammonia inlet path throttling hole are respectively formed in the bottom of the middle block, the prismatic sealing block is located above the flow-limiting piston, a middle hole is formed in the flow-limiting piston, a flow-limiting piston reset spring is arranged below the flow-limiting piston, and a storage cavity is formed below the flow-limiting piston reset spring. 
     Fourthly, a first ammonia inlet path, a second ammonia inlet path, a first ammonia inlet cavity, a second ammonia inlet cavity, a first ammonia outlet path and a second ammonia outlet path are respectively arranged in the resonance block, the first ammonia inlet cavity respectively communicates with the first ammonia inlet path and the first ammonia outlet path, the second ammonia inlet cavity respectively communicates with the second ammonia inlet path and the second ammonia outlet path, the first ammonia inlet cavity communicates with the second ammonia inlet cavity through a communicating hole, the first ammonia inlet cavity communicates with the first ammonia inlet path through a first ammonia inlet throttling hole, the first ammonia inlet cavity communicates with the pressure storage cavity through a second ammonia inlet throttling hole, and the first ammonia inlet path and the second ammonia inlet path communicate with the pressure storage cavity. 
     Fifthly, the super-hysteresis electromagnetic control actuator comprises super-hysteresis main and auxiliary magnetic poles, a hysteresis seat, a super-hysteresis upper valve rod, a super-hysteresis lower end cone valve and a super-hysteresis poppet valve, coils are wound in the super-hysteresis main and auxiliary magnetic poles, a super-hysteresis material is arranged in through holes of the super-hysteresis main and auxiliary magnetic poles, a hysteresis seat, a super-hysteresis upper valve rod, a super-hysteresis lower end cone valve and a super-hysteresis poppet valve are sequentially arranged below the super-hysteresis material, the super-hysteresis poppet valve is located in a super-hysteresis poppet valve cavity, a super-hysteresis poppet valve reset spring is arranged below the super-hysteresis poppet valve, an oil return oil channel and an oil inlet oil channel are arranged in the injector body where the super-hysteresis electromagnetic control actuator is located, the oil return oil channel communicates with the super-hysteresis poppet valve cavity, a super-hysteresis cone valve oil inlet hole is formed in a super-hysteresis lower end cone valve shell outside the super-hysteresis lower end cone valve, and the super-hysteresis cone valve oil inlet hole communicates with the oil inlet oil channel. 
     Sixthly, 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 rod, 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, a super-atomization needle valve body reset spring is arranged between the middle of the super-atomization needle valve body and the static leakage-free cylinder, an ammonia storage cavity is formed among the static leakage-free cylinder, the super-atomization needle valve body and the super-atomization valve seat, a liquid cooling working medium inlet pipeline and a liquid cooling working medium outlet pipeline are formed between the super-atomization valve seat and the super-atomization nozzle body, the bottom of the super-atomization needle valve body and the bottom of the super-atomization valve seat form a super-atomization injection flow channel, the ammonia storage cavity communicates with the storage cavity, and a super-atomization control cavity is formed between the top of the super-atomization needle valve body and the injector body above the super-atomization needle valve body. 
     Seventhly, the structure of the second pressure storage resonance flow-limiting module is the same as that of the first pressure storage resonance flow-limiting module, and the second pressure storage resonance flow-limiting module and the first pressure storage resonance flow-limiting module are arranged in the injector body in parallel. 
     Eighthly, the auxiliary pressurizing module comprises an auxiliary pressurizing magnet yoke, auxiliary pressurizing main and auxiliary magnetic poles, an auxiliary pressurizing piston, an auxiliary pressurizing armature, an auxiliary pressurizing limited block, an auxiliary pressurizing double-sealing valve rod, an auxiliary pressurizing upper valve rod seat and an auxiliary pressurizing lower valve rod seat, the auxiliary pressurizing armature sleeves the top of the auxiliary pressurizing double-sealing valve rod, an auxiliary pressurizing reset spring is arranged between the auxiliary pressurizing magnet yoke and the auxiliary pressurizing armature, auxiliary pressurizing main and auxiliary magnetic poles are arranged on the outer side of the auxiliary pressurizing reset spring, coils are wound around the auxiliary pressurizing main and auxiliary magnetic poles, the middle of the auxiliary pressurizing double-sealing valve rod is located in the auxiliary pressurizing upper valve rod seat, the bottom of the auxiliary pressurizing double-sealing valve rod is located in the auxiliary pressurizing lower valve rod seat, the middle of the auxiliary pressurizing double-sealing valve rod is sleeved with an auxiliary pressurizing valve rod reset spring, an auxiliary pressurizing double-sealing protrusion is arranged between the middle and the bottom of the auxiliary pressurizing double-sealing valve rod, sealing surfaces are arranged on the surfaces, corresponding to the auxiliary pressurizing double-sealing valve rod, of the auxiliary pressurizing upper valve rod seat and the auxiliary pressurizing lower valve rod seat, the auxiliary pressurizing piston is located below the auxiliary pressurizing lower valve rod seat and externally sleeved with an auxiliary pressurizing piston reset spring, an oil return pipeline is arranged in the auxiliary pressurizing upper valve rod seat, an auxiliary pressurizing oil channel and an auxiliary pressurizing communicating channel are arranged in the lower valve rod seat, the auxiliary pressurizing oil channel respectively communicates with an oil inlet channel and the lower portion of the auxiliary pressurizing double-sealing protrusion, the space where the auxiliary pressurizing double-sealing protrusion is located is a connected space, the auxiliary pressurizing communicating channel respectively communicates with the connected space and the upper portion of the auxiliary pressurizing piston, a sealing ball is arranged in the oil inlet channel, a sealing ball reset spring is arranged below the sealing ball, and a pressurizing oil pipeline is arranged below the auxiliary pressurizing piston and communicates with the oil inlet channel below the sealing ball reset spring. 
     Ninthly, the pressure balance type electromagnetic control actuator comprises pressure control type main and auxiliary magnetic poles, a pressure control type armature and a balance valve rod, the upper portion of the balance valve rod is arranged in the pressure control type main and auxiliary magnetic poles, the lower portion 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 poles, a pressure control type oil return hole upper section and a pressure control type oil return hole lower section are arranged below the pressure control type armature and the balance valve rod, the pressure control type oil return hole upper section and the pressure control type oil return hole lower section are connected through a pressure control type oil return throttling hole, and the pressure control type oil return hole lower section communicates with oil inlet pipelines through pressure control type oil inlet throttling holes. 
     Tenthly, the needle valve eccentric self-adjusting nozzle comprises an eccentric self-adjusting middle 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 control type oil return hole lower section is arranged in the eccentric self-adjusting middle block, the lower end of the eccentric self-adjusting middle 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, an eccentric self-adjusting control cavity is formed among the eccentric self-adjusting needle valve body, the eccentric self-adjusting valve block and the eccentric self-adjusting middle block, the eccentric self-adjusting control cavity communicates with the pressure control type 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 reset spring is sleeved above the eccentric self-adjusting needle valve body protrusion, the eccentric self-adjusting needle valve body is of an eccentric structure, and one part of the eccentric self-adjusting needle valve body is attached to the inner wall of the eccentric self-adjusting needle valve body shell outside the eccentric self-adjusting needle valve body. 
     Eleventhly, 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 a pile anode, a pile 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 converged and then supplied to the pile anode through a hydrogen filter, a first shut-off valve, a high-pressure gas injection valve, a jet pump and hydrogen circulating pump, and waste gas of the pile anode passes through a water separator and is discharged through a drain valve and an exhaust valve respectively; and air passes through an air filter, an air compressor, a first intercooler, a humidifier and a second shut-off valve and then is supplied to the pile cathode. 
     Twelfthly, the liquid ammonia phase-change cooling type hybrid power thermal management system further comprises a cooling system and a second cooling unit, the cooling system comprises a water tank, a first radiator, a first deionizer, a first heater, a second intercooler and a first cooling connector, the first radiator, the first deionizer, the first heater, the second intercooler and the first cooling connector are connected in parallel to form a first cooling unit, the water tank is connected with the first cooling unit, the cooling connector is connected with a cooling water outlet, and the first cooling unit is connected with the outlet through a discharge valve; and the 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 connector, and the arrangement mode of the second cooling unit is the same as and symmetrical with that of the first cooling unit. 
     Thirteenthly, 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 refrigerating 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 an outlet of the low-power compressor is introduced into the third radiator, and after being condensed, the high-pressure steam enters the refrigerating heat exchanger through a first electronic expansion valve and a second electronic expansion valve and returns to the low-power compressor; high-pressure steam at an outlet of the high-power compressor enters the heating heat exchanger for condensation and heat release, enters branch circuits where the expansion valves are located through a one-way check valve and the first electronic expansion valve, and a liquid working medium in the branch circuits where the expansion valves are located is evaporated into a gaseous working medium and returns to the high-power compressor. 
     Fourteenthly, the liquid ammonia phase-change cooling type hybrid power thermal management system further comprises a liquid ammonia-diesel oil dual-fuel cylinder, the liquid ammonia-diesel oil dual-fuel cylinder comprises a cylinder body, a piston, a crank, an air inlet pipe and an exhaust pipe, the air inlet pipe, the air outlet pipe and the injector are arranged above the cylinder body, the piston is arranged in the cylinder body, the crank is connected below the piston, an air inlet is formed in the joint of the air inlet pipe and the cylinder body, an air inlet valve rod is arranged at the air inlet and sleeved with an air inlet valve rod spring, an air outlet is formed in the joint of the air outlet pipe and the cylinder body, the air outlet is provided with an air outlet valve rod, the air outlet valve rod is sleeved with an air outlet valve rod spring, the air inlet pipe is provided with a hydrogen gas inlet, an air gas inlet is arranged between the hydrogen gas inlet and the air inlet, and a safety valve is arranged between the hydrogen gas inlet and the air gas inlet. 
     The liquid ammonia phase-change cooling type hybrid power thermal management system has the following advantages: 
     firstly, the liquid ammonia-diesel oil dual-fuel integrated design is adopted, the installation space is saved, injection of an ammonia fuel injector and a diesel oil injector is controlled while diesel oil is supplied, and fuel oil pressurization is provided for the diesel oil injector and a pressurizer; 
     secondly, accurate control of ammonia fuel injection is ensured by adopting the super-hysteresis electromagnetic control actuator structure; and the pressure balance type electromagnetic control actuator and the super-atomization nozzle module are matched to spray into the cylinder, so that ammonia fuel is sprayed into the cylinder in a high-flow high-pressure liquid state, and sufficient combustion is realized; 
     thirdly, the injection process is combined with thermal management design, and phase-change conversion of ammonia fuel is adjusted and controlled from two aspects of pressure and temperature; 
     fourthly, the liquid ammonia spraying process is circularly variable in a multi-valve cooperative control mode, so that the spraying amount and the spraying timing are more accurate and flexible; 
     fifthly, the pressure fluctuation in the system is adjusted by adopting the resonance block, and the controllability of the pressure wave coupling process is realized by changing the phase of pressure wave fluctuation, adjusting the fluctuation frequency and the corresponding relation between wave crests and wave troughs; and meanwhile, a flow limiter is designed to prevent abnormal injection; 
     sixthly, a balance valve control mode is adopted, and higher common rail pressure (250 MPa) can be achieved due to the fact that the whole valve is soaked in high-pressure fuel oil and is subjected to the effect of balance force, so that the mass of the whole valve is reduced, namely, the electromagnetic force requirement is reduced, and control response is increased; therefore, only a small-size electromagnetic valve is needed to be matched with the armature, and small spring pre-tightening force is needed; and meanwhile, the adopted balance valve rod is not directly subjected to high impact, the cavitation erosion phenomenon of a traditional ball valve is prevented, and the system reliability is improved; and 
     seventhly, through the combined design of the middle block and the self-adjusting valve block, on one hand, the problem of leakage caused by no static block in the prior art is solved, and on the other hand, through the design of the self-adjusting valve block, the problems of abrasion and leakage caused by needle valve eccentricity are prevented. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG.  1    is an integral structural schematic diagram of the present disclosure; 
         FIG.  2    is a liquid ammonia and hydrogen gas supply system; 
         FIG.  3    is a schematic diagram of a liquid ammonia-diesel oil dual-fuel cylinder; 
         FIG.  4    is a schematic diagram of a hydrogen fuel cell supply system; 
         FIG.  5    is a schematic diagram of a cooling system; 
         FIG.  6    is a schematic diagram of a double-acting heat pump and a waste heat utilization system; 
         FIG.  7    is an integral structural schematic diagram of a liquid ammonia-diesel oil dual-fuel integrated injector; 
         FIG.  8    is a structural schematic diagram of a pressurizing module; 
         FIG.  9    is a structural schematic diagram of a pressure storage resonance flow-limiting module; 
         FIG.  10    is a structural schematic diagram of a resonance block; 
         FIG.  11    is a structural schematic diagram of a super-hysteresis electromagnetic control actuator; 
         FIG.  12    is a structural schematic diagram of a phase-change controllable super-atomization nozzle module; 
         FIG.  13    is a structural schematic diagram of an auxiliary pressurizing module; 
         FIG.  14    is a structural schematic diagram of a pressure balance type electromagnetic control actuator; 
         FIG.  15    is a structural schematic diagram of a needle valve eccentric self-adjusting nozzle module; 
         FIG.  16    is a three-dimensional sectional structural schematic diagram of a phase-change controllable super-atomization nozzle module; and 
         FIG.  17    is a three-dimensional integral structural schematic diagram of a phase-change controllable super-atomization nozzle module. 
     
    
    
     DETAILED DESCRIPTION OF THE EMBODIMENTS 
     The present disclosure is described in more detail with reference to the attached figures. 
     In combination with  FIG.  1    to  FIG.  17   ,  FIG.  1    is an integral structural schematic diagram of the present disclosure. A liquid ammonia phase-change cooling type hybrid power thermal management system comprises a fuel oil supply system, a liquid ammonia and hydrogen supply system, a liquid ammonia-diesel oil dual-fuel cylinder  16 , a liquid ammonia-diesel oil dual-fuel injector  8 , a hydrogen fuel cell supply system  27 , a cooling system  28 , a double-acting heat pump  26  and a waste heat utilization system  29 . The fuel oil supply system comprises an oil tank  7 , a filter  6 , a high-pressure oil pump and motor  4 , a fuel oil common rail pipe  11 , a flow limiter  12 , high-pressure oil pipes  3  and  13  and an injector  8 , the right end of the common rail pipe  11  respectively communicates with the high-pressure oil pump  4 , the filter  6  and the oil tank  7 , and the flow limiter  12  communicates with the injector  14  through the high-pressure oil pipe  13 . 
       FIG.  2    is a schematic diagram of a liquid ammonia and hydrogen gas supply system. The liquid ammonia and hydrogen gas supply system comprises a liquid ammonia storage tank  24 , a hydrogen storage tank  25 , a nitrogen storage tank  23 , an ammonia pumping system  22 , a flow dividing 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 ammonia pumping system  22  is composed of a low-pressure pump and motor  30 , a high-pressure pump and motor  31 , an overflow valve  32 , a safety valve  33 , a temperature controller  34 , a liquid ammonia storage flow divider  35 , a storage tank  36 , a control valve  37 , an ammonia inlet  38 , an ammonia return port  39 , a regulation and control block  40 , a safety valve  41  and a control valve  42 . 
       FIG.  3    is a schematic diagram of a liquid ammonia-diesel oil dual-fuel cylinder. The schematic diagram of a liquid ammonia-diesel oil dual-fuel cylinder mainly comprises 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 gas inlet  51 , a safety valve  50  and an air gas inlet  49 . 
       FIG.  4    is a schematic diagram of a hydrogen fuel cell supply system. The hydrogen fuel cell supply system mainly comprises a hydrogen inlet  52 , a nitrogen purging inlet  53 , a hydrogen filter  54 , a pressure sensor  55 , a shut-off valve  56 , a high-pressure gas injection valve  57 , a jet pump and hydrogen circulating pump  58 , an overpressure valve  59 , introduced air tail gases  60  and  66 , a pile anode  61 , an outlet  62 , a water separator  63 , a drain valve  64 , an exhaust valve  65 , an air inlet  67 , an air filter  68 , a sensor  69 , an air compressor  70 , an intercooler  71 , a humidifier  72 , a shut-off valve  73 , a bypass valve  74 , a pile cathode  75 , a sensor  76 , a shut-off valve  77 , an outlet  78 , a water separator  79 , throttle valves  80  and  81 , anode excess hydrogen  82 , a muffler  83  and an outlet  84 . 
       FIG.  5    is a schematic diagram of a cooling system. The cooling system mainly comprises a water tank  85 , cooling water pumps  86  and  100 , temperature sensors  87  and  101 , cooling connectors  88  and  102 , temperature and pressure sensors  89  and  103 , intercoolers  90  and  104 , heaters  92  and  106 , three-way valves  93  and  107 , deionizers  94  and  108 , sensors  95  and  109 , radiators  96  and  110 , discharge valves  97  and  111 , outlets  91 ,  98 ,  105  and  112  and cooling water outlets  99  and  112 . 
       FIG.  6    is a schematic diagram of a double-acting heat pump and a waste heat utilization system, and the double-acting heat pump and the waste heat utilization system mainly comprise a liquid ammonia inlet  113 , a heater  114 , a three-way valve  115 , a radiator  116 , a sensor  117 , an electromagnetic reversing valve  118 , a gaseous working medium  119 , a filter  120 , a low-power compressor  121 , a sensor  122 , a refrigerating heat exchanger  123 , a sensor  124 , an electronic expansion valve  125 , a high-power compressor  126 , a sensor  127 , a heating heat exchanger  128 , a one-way check valve  129 , an electronic expansion valve  130 , a deionizer  131 , an ammonia discharge valve  132 , a waste working medium  133 , an expansion valve  134  and a liquid working medium  135 . 
       FIG.  7    is an integral structural schematic diagram of a liquid ammonia-diesel oil dual-fuel integrated injector, and the liquid ammonia-diesel oil dual-fuel integrated injector mainly comprises a one-way ammonia inlet  136 , a pressurizing module  137 , pressure storage resonance flow-limiting modules  138  and  142 , a super-hysteresis electromagnetic control actuator  139 , a phase-change controllable super-atomization nozzle module  140 , a one-way oil inlet  141 , an auxiliary pressurizing module  143 , a pressure balance type electromagnetic control actuator  144 , a needle valve eccentric self-adjusting nozzle  145  and liquid ammonia thermal management modules  146  and  147  Ammonia fuel is injected into the cylinder in a high-pressure liquid state, and sufficient combustion is achieved. Meanwhile, the injection process is combined with thermal management design, and phase-change conversion of ammonia fuel is adjusted and controlled from two aspects of pressure and temperature. The liquid ammonia spraying process is circularly variable in a double-valve control mode, so that the spraying amount and the spraying timing are more accurate and flexible. 
       FIG.  8    is a structural schematic diagram of an injector pressurizing module. The pressurizing module comprises a magnet yoke  148 , a reset spring  149 , main and auxiliary magnetic poles  150 , a coil  151 , an ammonia return channel  152 , a pressurizing piston upper surface  153 , a middle cavity  154 , a pressurizing piston reset spring  155 , an armature  156 , a limited block  157 , a valve rod reset spring  159 , a double-sealing valve rod  158 , an ammonia inlet channel  160 , a middle pipeline  161  and a pressurizing piston lower surface  162 . The module can adopt two control modes, one mode is a mode of pressurizing liquid ammonia by liquid ammonia, and the other mode is a mode of pressurizing liquid ammonia by diesel oil. 
       FIG.  9    is a structural schematic diagram of a pressure storage resonance flow-limiting module, and the pressure storage resonance flow-limiting module mainly comprises a pressure storage cavity  163 , a liquid cooling pipe inlet  164 , a resonance block  165 , a middle 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 channel  173 , a middle cavity  174 , a resonance block ammonia inlet channel throttling hole  175 , a valve seat  176 , a middle hole  177  and a reset spring  178 . The stability of ammonia fuel is ensured through the module, the pressure fluctuation in the system is adjusted by adopting the resonance block, and meanwhile, the flow limiter is designed to prevent abnormal injection. 
       FIG.  10    is a schematic diagram of a resonance block, and the resonance block mainly comprises a first ammonia inlet path  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 path  183 , a second ammonia inlet path  184 , a second ammonia inlet cavity  185 , a communicating hole  186  and a second ammonia outlet path  187 . 
       FIG.  11    is a schematic diagram of a super-hysteresis electromagnetic control actuator, and the super-hysteresis electromagnetic control actuator mainly comprises 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 middle cavity  193 , a buffer cavity  194 , an oil inlet and return hole  195 , a reset spring  196 , a super-hysteresis material  197 , a limited block  198 , an oil inlet oil channel  199 , an oil return oil channel  200 , a lower end cone valve  201 , a poppet valve  202  and an oil return oil channel  203 . 
       FIG.  12    is a schematic diagram of a phase-change controllable super-atomization nozzle module, and the phase-change controllable super-atomization nozzle module mainly comprises 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 surface  212 , a liquid cooling working medium outlet pipeline  213 , a needle valve body  214 , a needle valve sealing surface  215 , an injection flow channel  216  and a nozzle body  217 . 
       FIG.  13    is a schematic diagram of an auxiliary pressurizing module, and the auxiliary pressurizing module mainly comprises main and auxiliary magnetic poles  218 , a coil  219 , an oil inlet channel  220 , a middle pipeline  221 , a sealing ball  222 , a reset spring  223 , a pressurizing oil pipeline  224 , a pressurizing piston lower surface  225 , a valve rod reset spring  226 , an armature  227 , an oil return pipeline  228 , a double-sealing valve rod  229 , a pressurizing piston upper surface  230 , a middle cavity  231  and a pressurizing piston reset spring  232 . 
       FIG.  14    is a schematic diagram of a pressure balance type electromagnetic control actuator, and the pressure balance type electromagnetic control actuator mainly comprises an oil inlet pipe  233 , main and auxiliary magnetic poles  234 , a coil  235 , an armature  237 , oil inlet pipelines  233 ,  236  and  238 , reset springs  239  and  240 , a balance valve rod  241 , an oil inlet pipe  242 , an oil return throttling hole  243  and an oil inlet throttling hole  244 . 
       FIG.  15    is a schematic diagram of a needle valve eccentric self-adjusting nozzle module, and the needle valve eccentric self-adjusting nozzle module mainly comprises a middle block  245 , an oil accommodating groove  246 , a self-adjusting valve block  247 , a reset spring  248 , a needle valve lower end surface  249 , a nozzle hole  250 , a control cavity  251 , a control valve rod upper end surface  252 , a needle valve body  253 , a nozzle body  254 , a needle valve sealing surface  255  and a nozzle seat surface  256 . 
       FIG.  16    and  FIG.  17    show a super-atomization nozzle designed with an inner cone structure as a whole to achieve multi-layer sealing. Meanwhile, nearly hundreds of nozzle holes are used for spraying, and sufficient atomization of fuel is guaranteed from the structural angle. Fuel and air are fully fused and completely combusted. 
     Fuel of the system is stored in the liquid ammonia storage tank  24 , and the ammonia fuel is guaranteed to be in a stable liquid state in a high-pressure and low-temperature storage mode. Meanwhile, at the initial stage of fuel supply, a hydrogen and nitrogen preparation module is set up, stored liquid ammonia is converted into ammonia gas, and then purified ammonia gas is used for preparing hydrogen required by combustion and nitrogen required by system purging. The hydrogen and the nitrogen are respectively stored in the hydrogen storage tank  25  and the nitrogen storage tank  23 . Liquid ammonia stored in the liquid ammonia storage tank  24  firstly passes through the ammonia pumping system  22  and is pressurized by a low-pressure pump and a high-pressure pump, so that the requirements of supply and combustion are met. Wherein, the overflow valve  32  and the safety valve  33  are respectively arranged in a low-pressure loop and a high-pressure loop. The overflow valve  32  is arranged in the low pressure loop to control the delivery pressure, and when the pressure is too high, excess liquid ammonia is returned 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, the output pressure is adjusted through active control, and excess liquid ammonia returns to the liquid ammonia storage tank  24  through the safety valve  33 . For liquid ammonia, which is a phase-change-prone fuel, a thermal management module needs to be provided, and the temperature controller  34  is used for adjusting the temperature of the liquid ammonia output to control the phase state of the ammonia fuel by both pressure and temperature. Then, the fuel enters the liquid ammonia storage flow divider  35 , stable supply of the fuel is guaranteed through comprehensive control of double valves and double accommodating cavities, then the fuel is supplied into the ammonia inlet  38  through the storage tank  36  and the control valve  37 , and then the fuel is guided into the liquid ammonia common rail pipe  1 . The liquid ammonia common rail pipe  1  in the system is of a double-layer structure, and liquid ammonia is prevented from leaking into the atmosphere. Meanwhile, an ammonia leakage detection sensor is arranged at the port of the common rail pipe, and system feedback is carried out in time. 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 , is controlled by the electromagnetic valve in the injector and then is injected into the cylinder. 
     Diesel oil used for ignition in the system is stored in the oil tank  7 , the high-pressure oil pump  4  sucks fuel oil from the oil tank  7 , the filter  6  is arranged between the high-pressure oil pump  4  and the oil tank  7 , and the fuel oil is filtered through the filter  6 . And then the fuel oil is conveyed to the common rail pipe  11 , a plurality of hydraulic oil outlets are formed in the common rail pipe  11 , each hydraulic oil outlet communicates with the injector through the high-pressure oil pipe  13 , and the hydraulic oil is controlled by the electromagnetic valve in the injector and then is ejected into the cylinder. 
     Liquid ammonia fuel enters the pressure storage cavity  163  from the one-way ammonia inlet  136 , and the one-way ammonia inlet  136  plays a role of a one-way valve. When liquid ammonia supply pressure is larger than spring pre-tightening force of the one-way valve, the cone valve overcomes spring force to be opened, and liquid ammonia is supplied into the pressure storage cavity. And when the pressure of the one-way ammonia inlet  136  is small, the cone valve is closed again, and the liquid ammonia in the system is also sealed. After entering the pressure storage cavity  163 , the fuel is supplied downwards through the resonance block  165 . The resonance block  165  is composed of three pipelines  179 ,  181  and  184 . Fuel flows into the flow limiter from the three pipelines respectively, the first ammonia inlet pipeline  179  is a main flow channel, flows through the first ammonia inlet throttling hole  180  in the middle, plays a role in filtering liquid ammonia, and then flows into the first ammonia inlet cavity  182 . The second ammonia inlet path  184  is an auxiliary flow path, no throttling hole is formed in the middle, and the second ammonia inlet path  184  directly flows into the flow limiter after passing through the second ammonia inlet cavity  185  and the second ammonia outlet path  187 . The second ammonia inlet throttling hole  181  and the communicating hole  186  are main structures for realizing resonance, and the controllability of the pressure wave coupling process is realized by changing the phase of the pressure wave fluctuation, adjusting the fluctuation frequency and the corresponding relation between wave crests and wave troughs. Particularly, in a pressurizing mode, the stability of the system is ensured. The flow-limiting valve assembly is arranged inside the injector body through the pressure storage cavity  163 . The middle block  166  not only limits the overall flow-limiting valve assembly, but also cooperates with the reset spring  167  to serve as a spring seat of the reset spring  167  on one hand, and limits the maximum displacement of the flow-limiting piston on the other hand. Under the action of spring pre-tightening force of a damping spring and a ball valve reset spring, the lower end surfaces of the prismatic sealing block  169  and the flow-limiting piston  170  are matched with the upper end surface of a supporting control valve seat  176 . The valve seat  176  is pressed at the bottom under the action of spring force of the reset spring, and a seating surface of the prismatic sealing block is formed at the variable cross section of the upper portion of the valve seat  176 . Liquid ammonia flows into the middle cavity  174  from the resonance block and flows into the flow-limiting valve through the oil inlet hole  168  and the resonance block ammonia inlet path throttling hole  175  respectively. Under the action of hydraulic force, along with liquid ammonia supply, the prismatic sealing block  169  overcomes spring force to move downwards. When the fuel supply amount is higher than a limit value, the prismatic sealing block  169  is matched with the valve seat  176  to achieve sealing, fuel supply is disconnected, and cylinder pulling is avoided. When fuel supply is interrupted, the prismatic sealing block  169  rapidly resets under the action of the spring force. 
     Diesel enters the pressure storage resonance flow-limiting module  138  through the one-way oil inlet  141 , then is supplied downwards and enters the auxiliary pressurizing module  143 , and the pressurized fuel is supplied to the super-hysteresis electromagnetic control actuator  139 , the pressure balance type electromagnetic control actuator  144  and the needle valve eccentric self-adjusting nozzle  145  through the one-way valves  222  and  223  respectively for respectively controlling injection of the ammonia fuel injector and the diesel oil injector and providing fuel oil for the diesel oil injector. 
     Through the flow limiter, liquid ammonia is supplied into the ammonia storage cavity through the ammonia inlet channel, and is sprayed into the cylinder through the cooperation of the super-hysteresis electromagnetic control actuator and the super-atomization nozzle module. In the present disclosure, in order to ensure the control accuracy of the fuel injector, diesel oil is adopted as servo oil, and the upper and lower stress of the needle valve is changed by adjusting the pressure level in the control cavity, so that the injection timing is controlled. High-pressure diesel oil flows into the electromagnetic actuator from the oil inlet oil channel  199 , and when the electromagnetic actuator is not powered on, under the action of spring pre-tightening force  192  and  196 , the poppet valve  202  is in a sealed state, so that an electromagnetic actuator pipeline is disconnected from an oil return pipeline. When the lower end cone valve  201  is in an open state, diesel oil is supplied to the control cavity  211  from the oil inlet oil channel  199  through a flow channel of the lower end cone valve  201 . By means of the oil inlet and return hole  195  and the buffer cavity  194 , on one hand, fuel oil pressure fluctuation at the control valve is reduced through the buffer cavity, and on the other hand, leaked fuel oil is collected through the pressure difference of the high-pressure contact surface structure. Fuel oil flows downwards into the control cavity  211  and is sealed by the static leakage-free cylinder  206  and the needle valve sealing surface  215 , and accurate control over fuel injection is realized by regulating and controlling the pressure in a control chamber and changing the upper and lower stress difference of the needle valve. 
     The diesel injector adopts a balance valve control mode, and the balance valve rod is compressed by the armature. Higher common rail pressure (250 MPa) can be achieved due to the fact that the whole valve is soaked in high-pressure fuel oil and is subjected to the effect of balance force, so that the mass of the whole valve is reduced, namely, the electromagnetic force requirement is reduced, and control response is increased. Therefore, only a small-size electromagnetic valve is needed to be matched with the armature, and small spring pre-tightening force is needed. Meanwhile, the adopted balance valve rod is not directly subjected to high impact, the cavitation erosion phenomenon of a traditional ball valve is prevented, and the system reliability is improved. High-pressure diesel oil flows into the control cavity  251  through the oil inlet oil channel  242  and the oil inlet throttling hole  244 , and when the control cavity  251  is not powered on, under the action of the spring pre-tightening force  240 , the armature  237  and the balance valve rod  241  are in a sealed state, so that the electromagnetic actuator pipeline is disconnected from the oil return pipeline. Diesel oil is supplied to the control cavity  251  from the oil inlet oil channel  242  through the flow channel of the oil inlet throttling hole  244 . The fuel oil pressure fluctuation at the control valve is reduced due to the existence of the oil return cavity. Fuel oil flows downwards into the control cavity  251 , and the control cavity is formed by combining the middle block  245 , the self-adjusting valve block  247  and the control valve rod upper end surface  252  to achieve sealing. The pressure in the control chamber is regulated and controlled, the upper and lower stress difference of the needle valve is changed, and accurate control over fuel injection is achieved. Through the combined design of the middle block  245  and the self-adjusting valve block  247 , on one hand, the problem of leakage caused by no static block in the prior art is solved, and on the other hand, through the design of the self-adjusting valve block, the problems of abrasion and leakage caused by needle valve eccentricity are prevented. The working principles of the main and auxiliary pressurizing modules are similar, and by taking the main pressurizing module as an example, the working principles of the pressurizing modules in the specific injection process are as follows: 
     When a non-pressurizing mode is adopted for working, the pressurizing control valve part is not powered on, and due to the fact that the pressure of each acting surface of the pressurizing piston is balanced at the moment, the acting armature  156  and the double-sealing valve rod  158  which are subjected to spring pre-tightening force  149  and  155  are in a compressed state, and the ammonia inlet channel  160  is sealed. At the moment, no fuel is supplied to the pressurizing module, and the pressurizing piston is in a reset state under the action of spring pre-tightening force and is free of pressurizing function. Therefore, ammonia fuel in the system is stored in the pressure storage cavity  163  after passing through the one-way ammonia inlet  136 , and flows into the flow-limiting valve through a resonant cavity  165 . Due to the throttling effect of the resonance block  165  on the liquid ammonia, the fuel pressure in the middle hole  177  in the flow-limiting piston  170  and the pressure storage cavity  163  rises to form pressure difference with the pressure in a transition oil cavity, and therefore the flow-limiting piston  170  and the prismatic sealing block  169  integrally move downwards to compensate the injected pressure to a certain extent. The liquid ammonia passing through the flow-limiting valve is supplied into the oil accommodating groove  246  through the ammonia inlet pipe. When the pressure balance type electromagnetic control actuator is powered on, under the influence of a magnetic field, the armature  237  overcomes spring pre-tightening force  239  and  240  to move upwards, an oil return channel is opened, the control cavity  251  communicates with the low-pressure leakage hole, and fuel in the control cavity  251  flows back into the low-pressure cavity through the low-pressure oil leakage hole. When the resultant force formed by the pressure in the control cavity  251  and the elastic force of a needle valve spring  248  is smaller than the upward hydraulic force in the oil accommodating groove  246 , the needle valve body  253  is lifted upwards, the muzzle hole is opened, and the injector starts to spray oil. When the oil injection control valve part is powered off, the magnetic field influence is lost, the armature  237  moves downwards under the action of the pre-tightening force of the spring, and the oil return oil channel is sealed again. Meanwhile, the balance valve rod  241  is driven to move downwards, and sealing is achieved. The pressure of the control cavity  251  is re-built through the oil inlet throttling hole  244 , and when the resultant force formed by the pressure in the control cavity  251  and the elastic force of the needle valve spring  248  is larger than the upward hydraulic force in the oil accommodating groove  246 , the needle valve body  253  is re-seated, and the injector stops injecting. When the injector stops working, the pressure difference between the upper surface and the lower surface of the flow-limiting piston  170  is gradually reduced along with the liquid ammonia flowing through the middle hole  177 , and the flow-limiting piston  170  and the prismatic sealing block  169  integrally return to the initial position under the action of the reset spring. 
     When a pressurizing mode is adopted for working, the pressurizing control valve is partially powered on, the coil  151  is powered on, the main and auxiliary magnetic poles  150  form electromagnetic force, the armature  156  is attracted to move upwards, meanwhile, the double-sealing valve rod  158  is driven to move upwards, the ammonia inlet channel  160  is opened, and the ammonia return channel is closed. Liquid ammonia is collected on the pressurizing piston upper surface  153  to increase the stress on the upper surface, so that the upper and lower pressure difference overcomes the spring force to cause the pressurizing piston to move downwards. The volume in the lower pressure storage cavity is compressed, and the pressure is increased. The pressurizing module and the pressure balance type electromagnetic control actuator can both adopt two control modes, one mode is a mode of pressurizing liquid ammonia by liquid ammonia, and the other mode is a mode of pressurizing liquid ammonia by diesel oil. In the pressurizing module, the middle cavity  154  may serve as a pressurizing oil leakage collection cavity, and meanwhile, the fuel oil may play a sealing role in the liquid ammonia. The pressurized liquid ammonia flows into the flow-limiting valve through the resonant cavity  165 . Liquid ammonia passing through the flow-limiting valve is supplied into the ammonia storage cavity  205  through the ammonia inlet channel  171 . When the pressure balance type electromagnetic control actuator  144  is powered on, under the influence of the magnetic field, the armature  237  overcomes spring pre-tightening force  239  and  240  to move upwards, the oil return channel is opened, the control cavity  251  communicates with the low-pressure leakage hole, and fuel in the control cavity  251  flows back into the low-pressure cavity through the low-pressure oil leakage hole. When the resultant force formed by the pressure in the control cavity  251  and the elastic force of a needle valve spring  248  is smaller than the upward hydraulic force in the oil accommodating groove  246 , the needle valve body  253  is lifted upwards, the muzzle hole is opened, and the injector starts to spray oil. When the oil injection control valve part is powered off, the magnetic field influence is lost, the armature  237  moves downwards under the action of the pre-tightening force of the spring, and the oil return oil channel is sealed again. Meanwhile, the balance valve rod  241  is driven to move downwards, and sealing is achieved. The pressure of the control cavity  251  is re-built through the oil inlet throttling hole  244 , and when the resultant force formed by the pressure in the control cavity  251  and the elastic force of the needle valve spring  248  is larger than the upward hydraulic force in the oil accommodating groove  246 , the needle valve body  253  is re-seated, and the injector stops injecting. 
     Thermal management modules are designed at the pressure storage resonance flow-limiting module  138  and the super-atomization nozzle module  140 , including an inlet and an outlet for a refrigerant. The liquid ammonia phase state is comprehensively controlled in two aspects of temperature and pressure, so that the liquid ammonia phase state in the injection process is controllable. 
     Ammonia and hydrogen are supplied to the hydrogen fuel cell system, hydrogen is supplied to the hydrogen inlet  52 , purged through the nitrogen purging inlet  53 , filtered by the hydrogen filter  54 , and the circulation pressure is monitored by the pressure sensor  55 , when the pressure demand is met, the shut-off valve  56  is opened, and when the pressure is excessive, the shut-off valve  56  is closed. The pile anode  61  is then supplied by the high-pressure gas injection valve  57  and the jet pump and hydrogen circulating pump  58 . Exhaust gas of the pile anode  61  is discharged outwards through the water separator  63 , the drain valve  64  and the exhaust valve  65 . Air is filtered by the air filter  68  through the air inlet  67 , the circulation pressure is monitored by the pressure sensor  69 , and the air is pressurized and physically adjusted by the air compressor  70 , the intercooler  71  and the humidifier  72 , and is delivered to the shut-off valve  73  to be supplied to the pile cathode  75 . Excess air supply is discharged by the bypass valve  74  along with exhaust gas of the pile cathode  75  passing through the humidifier  72 , and through the throttle valves  80  and  81 , anode excess hydrogen is collected, flows through the muffler  83 , and is discharged through the outlet  84 . 
     Cooling requirements of a fuel cell and a dual-fuel injection system in the system are met by the cooling system  28 , in the system, cooling water in the water tank is an ethylene glycol solution, heat exchange fins are additionally arranged on the wall surface of the water tank, phase change is carried out by the branch circuit of ammonia  24  stored in the system, boiling heat exchange is achieved, and the solution in the water tank is primarily cooled. By utilizing the function of ammonia fuel as a refrigerant, the work done by the cooling water pumps  86  and  100  is greatly reduced. The cooled ethylene glycol solution is secondarily cooled by the cooling water pumps  86  and  100  to meet the cooling requirement of the system, the inlet air temperature is reduced by the intercoolers  90  and  104 , ions in the solution are removed by the deionizers  94  and  108 , and pure water is obtained. The temperature of the solution is adjusted by the heaters  92  and  106 , and the treated cooling water passes through the cooling water outlets  99 ,  112  respectively to meet the cooling requirements of the heat engine and the fuel cell. Meanwhile, the two loops are connected in parallel, power can be adjusted according to requirements of different parts, and the refrigerating capacity can be adjusted. 
     Liquid ammonia passes through the heater  114  from the liquid ammonia inlet  113  into the three-way valve  115 , and the three-way valve  115  plays a role of a diversion valve. When the low-power compressor  121  works, high-pressure steam discharged by the compressor enters the radiator through the filter  120  and the sensor  117 , after being condensed, the working medium enters the electronic expansion valves  130  and  125 , enters the refrigerating heat exchanger  123  through the sensor  124  and is evaporated to absorb heat in the refrigerating heat exchanger  123  to achieve the refrigeration effect, and then returns to the low-power compressor through the sensor  122 . 
     When switching to the heating mode, the system dissipates heat for the piston of the power system and related parts of the injector. High-pressure steam of the working medium is discharged from the high-power compressor  126 , enters the heating heat exchanger  128  through the sensor  127  for condensation and heat release, then enters the branch circuit where the expansion valve  134  is located through the one-way check valve  129  and the electromagnetic expansion valve  130  and communicates with the heat exchanger, and after the liquid working medium  135  evaporates and absorbs heat from the piston part, the gaseous working medium  119  returns to the high-power compressor  126  through the one-way check valve, heating circulation is achieved, and piston set components are cooled. 
     The system can also realize an air source heating mode, the high-pressure steam of the working medium is discharged from the high-power compressor  126 , enters the heating heat exchanger  128  through the sensor  127  for condensation and heat release, then enters the radiator  116  through the one-way check valve  129  and the electromagnetic expansion valve  130 , and returns to the high-power compressor through the sensor  117  and the electromagnetic reversing valve  118  after evaporation and heat absorption of the working medium at the radiator  116 , and air source heating circulation is realized. 
     According to the above description, the present disclosure realizes three purposes for ammonia: power device fuel supply, a heat dissipation system refrigerant and a hydrogen supply source of a fuel cell. The liquid ammonia-diesel oil dual-fuel integrated design is adopted, the installation space is saved, injection of the ammonia fuel injector and the diesel oil injector is controlled while diesel oil is supplied, and fuel oil is provided for the diesel oil injector. The double-acting heat pump module is innovatively designed based on the liquid ammonia phase-change cooling principle, firstly, the cold starting problem of the engine under the cold condition can be effectively solved, secondly, the power consumption of the compressor is reduced, waste heat utilization is achieved, and the energy utilization rate is improved. Meanwhile, the injection process is combined with thermal management design, and phase-change conversion of ammonia fuel is adjusted and controlled from two aspects of pressure and temperature. The liquid ammonia spraying process is circularly variable in a multi-valve cooperative control mode, so that the spraying amount and the spraying timing are more accurate and flexible. A main and auxiliary pressurizing mode can be adopted, under the pressurizing mode, the injection pressure and the injection rate of fuel injection are affected by the pressurizing mode, and controllable injection between cycles can be achieved. Accurate control of ammonia fuel injection is ensured by adopting the super-hysteresis electromagnetic control actuator structure. A balance valve control mode is adopted, and higher common rail pressure (250 MPa) can be achieved due to the fact that the whole valve is soaked in high-pressure fuel oil and is subjected to the effect of balance force, so that the mass of the whole valve is reduced, namely, the electromagnetic force requirement is reduced, and control response is increased. Therefore, only a small-size electromagnetic valve is needed to be matched with the armature, and small spring pre-tightening force is needed. Meanwhile, the adopted balance valve rod is not directly subjected to high impact, the cavitation erosion phenomenon of a traditional ball valve is prevented, and the system reliability is improved. Through the combined design of the middle block and the self-adjusting valve block, on one hand, the problem of leakage caused by no static block in the prior art is solved, and on the other hand, through the design of the self-adjusting valve block, the problems of abrasion and leakage caused by needle valve eccentricity are prevented.