NL2032248B1 - Liquid ammonia phase-change cooling type hybrid power thermal management system - Google Patents

Liquid ammonia phase-change cooling type hybrid power thermal management system Download PDF

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Publication number
NL2032248B1
NL2032248B1 NL2032248A NL2032248A NL2032248B1 NL 2032248 B1 NL2032248 B1 NL 2032248B1 NL 2032248 A NL2032248 A NL 2032248A NL 2032248 A NL2032248 A NL 2032248A NL 2032248 B1 NL2032248 B1 NL 2032248B1
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Netherlands
Prior art keywords
ammonia
valve
pressurizing
pressure
inlet
Prior art date
Application number
NL2032248A
Other languages
Dutch (nl)
Inventor
Wei Yunpeng
Zhang Hanwen
Xu Jing
Mao Yuntao
Wu Yuelin
Fan Liyun
Original Assignee
Univ Harbin Eng
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Priority to NL2032248A priority Critical patent/NL2032248B1/en
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Publication of NL2032248B1 publication Critical patent/NL2032248B1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • F02M55/025—Common rails
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
    • F02D19/0639—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed characterised by the type of fuels
    • F02D19/0642—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed characterised by the type of fuels at least one fuel being gaseous, the other fuels being gaseous or liquid at standard conditions
    • F02D19/0644—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed characterised by the type of fuels at least one fuel being gaseous, the other fuels being gaseous or liquid at standard conditions the gaseous fuel being hydrogen, ammonia or carbon monoxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0203—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels characterised by the type of gaseous fuel
    • F02M21/0206—Non-hydrocarbon fuels, e.g. hydrogen, ammonia or carbon monoxide

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

A liquid ammonia phase—change cooling type hybrid power thermal management system. The system. 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 5 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 10 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— 15 pressure pump. (+ FIq. l)

Description

P1414 /NLpd
LIQUID AMMONIA PHASE-CHANGE COOLING TYPE HYBRID POWER THERMAL
MANAGEMENT SYSTEM
TECHNICAL FIELD
The present disclosure relates to an engine, and specifically relates to a hybrid power engine.
BACKGROUND ART
Under the large background of green and low-carbon ships, ship development enters a key transformation and upgrading period.
Fuel diversity is an inevitable trend of ship development, and therefore development and research of a low-carbon clean fuel sup- ply and injection system for ships are needed. Ammonia, as one of the typical low carbon fuels, is higher in energy storage and con- venient to store and transport than hydrogen fuels, has a mature supply chain, and is one of main low-carbon alternative energy sources.
At present, no mature ammonia fuel power device exists inter- nationally, 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 pop- ularization and application are limited.
SUMMARY
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 ammo- nia common rail pipe, a fuel oil comon rail pipe and an oil tank, wherein the liquid ammonia hydrogen supply system comprises a liq- uid ammonia storage tank, an ammonia pumping system, a flow divid- ing 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 in-
let 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 ammo- nia outlet control valve, an outlet of the liquid amonia 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 in- let control valve is connected with the liquid ammonia common rail pipe through the ammonia inlet pipe, an inlet of the liquid ammo- nia 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 characteris- tics:
Firstly, the injector comprises an injector body, a liquid ammonia injection part and a diesel injection part, the liquid am- monia 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 actua- tor and a phase-change controllable super-atomization nozzle mod- ule which are arranged from top to bottom, and the diesel injec- tion part comprises a second pressure storage resonance flow- limiting module, an auxiliary pressurizing module, a pressure bal- ance type electromagnetic control actuator and a needle valve ec- centric self-adjusting nozzle which are arranged from top to bot- tom.
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 pressur- izing upper valve rod seat and a pressurizing lower valve rod seat, the pressurizing armature sleeves the top of the pressuriz-
ing double-sealing valve rod, a pressurizing reset spring is ar- ranged 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 pres- surizing lower valve rod seat, the middle of the pressurizing dou- ble-sealing valve rod is sleeved with a pressurizing valve rod re- set 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 pres- surizing lower valve rod seat and externally sleeved with a main pressurizing piston reset spring, a connected ammonia return chan- nel is arranged in the pressurizing upper valve rod seat, an ammo- nia inlet channel and a middle pipeline are arranged in the pres- surizing 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 com- municates 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 be- low 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 mid- dle block, the prismatic sealing block is located above the flow- limiting piston, a middle hole is formed in the flow-limiting pis- ton, 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 in- let path and the first ammonia outlet path, the second ammonia in- let 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 throt- tling hole, and the first ammonia inlet path and the second ammo- nia inlet path communicate with the pressure storage cavity.
Fifthly, the super-hysteresis electromagnetic control actua- tor 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 materi- al, 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 ar- ranged in the injector body where the super-hysteresis electromag- netic control actuator is located, the oil return oil channel com-
municates 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 in- 5 let hole communicates with the oil inlet oil channel.
Sixthly, the phase-change controllable super-atomization noz- zle 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 su- per-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 su- per-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 nee- dle 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 su- per-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 injec- tor body above the super-atomization needle valve body.
Seventhly, the structure of the second pressure storage reso- nance flow-limiting module is the same as that of the first pres- sure storage resonance flow-limiting module, and the second pres- sure storage resonance flow-limiting module and the first pressure storage resonance flow-limiting module are arranged in the injec- tor body in parallel.
Eighthly, the auxiliary pressurizing module comprises an aux- iliary 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 aux- iliary pressurizing upper valve rod seat and an auxiliary pressur- izing 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 pressur- izing 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 auxil- iary pressurizing upper valve rod seat and the auxiliary pressur- izing 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 pres- surizing upper valve rod seat, an auxiliary pressurizing oil chan- nel and an auxiliary pressurizing communicating channel are ar- ranged 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 pres- surizing piston, a sealing ball is arranged in the oil inlet chan- nel, a sealing ball reset spring is arranged below the sealing ball, and a pressurizing oil pipeline is arranged below the auxil- iary pressurizing piston and comunicates with the oil inlet chan- nel below the sealing ball reset spring.
Ninthly, the pressure balance type electromagnetic control actuator comprises pressure control type main and auxiliary mag- netic 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 con- trol 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 pres- sure 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 pres- sure 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 communi- cates 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 nee- dle 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 noz- zle body, the pressure control type oil return hole lower section is arranged in the eccentric self-adjusting middle block, the low- er end of the eccentric self-adjusting middle block is connected with the eccentric self-adjusting valve block, the top of the ec- centric self-adjusting needle valve body is located in the eccen- tric self-adjusting valve block, an eccentric self-adjusting con- trol cavity is formed among the eccentric self-adjusting needle valve body, the eccentric self-adjusting valve block and the ec- centric self-adjusting middle block, the eccentric self-adjusting control cavity communicates with the pressure control type oil re- turn 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 hy- brid 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 hydro- gen inlet, the nitrogen storage tank is connected with the nitro- gen 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 an- ode 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 hy- brid 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 radia- tor, 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 en- ters the refrigerating heat exchanger through a first electronic expansion valve and a second electronic expansion valve and re- turns to the low-power compressor; high-pressure steam at an out- let 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 cylin- der 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.
Beneficial effects: firstly, the installation space is saved, injection of an am- monia 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 en- sured; and ammonia fuel is sprayed into the cylinder in a high- flow high-pressure liquid state, and sufficient combustion is re- alized; thirdly, the injection process is combined with thermal man- agement design, and phase-change conversion of ammonia fuel is ad- justed and controlled from two aspects of pressure and tempera- ture; 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 controllability of the pressure wave coupling process is realized; and meanwhile, a flow limiter is designed to prevent abnormal injection; sixthly, higher common rail pressure (250MPa) is achieved, so that the mass of the whole valve is reduced, namely, the electro- magnetic force requirement is reduced, and control response is in- creased; 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 lig- uid 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 stor- age 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 bal- ance 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
In combination with FIG. 1 to FIG. 17, in FIG. 1, 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 cyl- inder 16, a liquid ammonia-diesel oil dual-fuel injector 8, a hy- drogen 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 in- jJector 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 in- jJector 14 through the high-pressure oil pipe 13.
In FIG. 2, 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 am- monia 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 regu- lation and control block 40, a safety valve 41 and a control valve 42.
In FIG. 3, 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.
In FIG. 4, the hydrogen fuel cell supply system mainly com- prises a hydrogen inlet 52, a nitrogen purging inlet 53, a hydro- gen filter 54, a pressure sensor 55, a shut-off valve 56, a high- pressure gas injection valve 57, a jet pump and hydrogen circulat- ing 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 fil- ter 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 wa- ter separator 79, throttle valves 80 and 81, anode excess hydrogen 82, a muffler 83 and an outlet 84.
In FIG. 5, 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 sen- sors 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.
In FIG. 6, the double-acting heat pump and the waste heat utilization system mainly comprise a liquid amonia 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 re- frigerating heat exchanger 123, a sensor 124, an electronic expan- sion valve 125, a high-power compressor 126, a sensor 127, a heat- ing 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 liq- uid working medium 135.
In FIG. 7, the liquid ammonia-diesel oil dual-fuel integrated injector mainly comprises a one-way ammonia inlet 136, a pressur- izing 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 am- monia thermal management modules 146 and 147.
In FIG. 8, 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 up- per surface 153, a middle cavity 154, a pressurizing piston reset spring 155, an armature 156, a limited block 157, a valve rod re- set spring 159, a double-sealing valve rod 158, an ammonia inlet channel 160, a middle pipeline 161 and a pressurizing piston lower surface 162.
In FIG. 9, the pressure storage resonance flow-limiting mod- ule mainly comprises a pressure storage cavity 163, a liquid cool- ing 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 amnonia 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 re- set 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.
In FIG. 10, the resonance block mainly comprises a first am- monia 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 amonia outlet path 183, a second ammonia in- let path 184, a second ammonia inlet cavity 185, a communicating hole 186 and a second ammonia outlet path 187.
In FIG. 11, the super-hysteresis electromagnetic control ac- tuator 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.
In FIG. 12, 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 con- trol valve rod upper end surface 212, a liquid cooling working me- dium outlet pipeline 213, a needle valve body 214, a needle valve sealing surface 215, an injection flow channel 216 and a nozzle body 217.
In FIG. 13, the auxiliary pressurizing module mainly compris- es 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.
In FIG. 14, the pressure balance type electromagnetic control actuator mainly comprises an oil inlet pipe 233, main and auxilia- ry 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.
In FIG. 15, 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 lig-
uid state in a high-pressure and low-temperature storage mode.
Meanwhile, at the initial stage of fuel supply, a hydrogen and ni- trogen preparation module is set up, stored liquid ammonia is con- verted 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 ar- ranged in a low-pressure loop and a high-pressure loop. The over- flow valve 32 is arranged in the low pressure loop to control the delivery pressure, and when the pressure is too high, excess liq- uid 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 amonia, 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 ammo- nia leakage detection sensor is arranged at the port of the common rail pipe, and system feedback is carried out in time. Liquid am- monia 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 hy- draulic oil is controlled by the electromagnetic valve in the in-
Jector 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 amnonia inlet path 184 di- rectly flows into the flow limiter after passing through the sec- ond ammonia inlet cavity 185 and the second ammonia outlet path 187. The second ammonia inlet throttling hole 181 and the communi- cating hole 186 are main structures for realizing resonance, and the controllability of the pressure wave coupling process is real- ized by changing the phase of the pressure wave fluctuation, ad-
Justing the fluctuation frequency and the corresponding relation between wave crests and wave troughs. Particularly, in a pressur- izing 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 co- operates with the reset spring 167 to serve as a spring seat of the reset spring 167 on one hand, and limits the maximum displace- ment of the flow-limiting piston on the other hand. Under the ac- tion of spring pre-tightening force of a damping spring and a ball valve reset spring, the lower end surfaces of the prismatic seal- ing 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 mid- dle 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 val- ue, 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 electro- magnetic control actuator 139, the pressure balance type electro- magnetic control actuator 144 and the needle valve eccentric self- adjusting nozzle 145 through the one-way valves 222 and 223 re- spectively 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 re- turn 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 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 in- to the flow-limiting valve through a resonant cavity 165. Due to the throttling effect of the resonance block 165 on the liquid am-
monia, 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 pris- matic 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 communi- cates 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 inject- ing. When the injector stops working, the pressure difference be- tween 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 pressur- izing control valve is partially powered on, the coil 151 is pow- ered on, the main and auxiliary magnetic poles 150 form electro- magnetic force, the armature 156 is attracted to move upwards, meanwhile, the double-sealing valve rod 158 is driven to move up- wards, the ammonia inlet channel 160 is opened, and the ammonia return channel is closed. Liquid ammonia is collected on the pres- surizing 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 muz- zle hole is opened, and the injector starts to spray oil. When the 0il 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 in- let 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.
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 pres- sure 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 dis- charged 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 hu- midifier 72, and is delivered to the shut-off valve 73 to be sup- plied 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.
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 com- pressor enters the radiator through the filter 120 and the sensor 117, after being condensed, the working medium enters the elec- tronic 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 re- frigeration 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 ex- changer 128 through the sensor 127 for condensation and heat re- lease, then enters the branch circuit where the expansion valve 134 is located through the one-way check valve 129 and the elec- tromagnetic expansion valve 130 and communicates with the heat ex- changer, 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 en- ters 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 revers- ing valve 118 after evaporation and heat absorption of the working medium at the radiator 116, and air source heating circulation is realized.

Claims (8)

CONCLUSIESCONCLUSIONS 1. Thermisch beheersysteem voor hybride energie van het koelende type met faseovergang van vloeibare ammoniak, welke omvat een in- jector, een waterstoftoevoersysteem voor vloeibare ammonia, een common-railleiding voor vloeibare ammonia, een common-railleiding voor brandstofolie en een olietank, waarbij het waterstoftoevoer- systeem voor vloeibare ammoniak omvat een opslagtank voor vloeiba- re ammoniak, een pompsysteem voor ammoniak, een stroomverdelings- systeem en een ammoniakinlaat- en uitlaatsysteem, waarbij de com- mon-railleiding voor brandstofolie respectievelijk is verbonden met de olietank en een eenrichting olie-inlaat van de injector, waarbij de common-railleiding voor vloeibare ammonia respectieve- lijk is verbonden met het ammoniak inlaat- en uitlaatsysteem en een eenrichting ammoniak-inlaat van de injector, waarbij een ammo- niak inlaatleiding en een ammoniak retourleiding zijn aangebracht in het ammoniak inlaat- en uitlaatsysteem, het ammoniak pompsys- teem omvat een stroomverdeler voor vloeibare ammoniakopslag, een lagedrukpomp en een hogedrukpomp, waarbij het stroomverdelingssys- teem omvat een opslagtank, een ammoniak inlaatregelklep, een vei- ligheidsklep en een ammoniak uitlaat regelklep, waarbij een uit- laat van de vloeibare ammoniak opslagtank achtereenvolgens is ver- bonden met de lagedrukpomp, de hogedrukpomp, de stroomverdeler voor vloeibare ammoniakopslag, de opslagtank en de ammoniak inlaat regelklep, waarbij de ammoniak inlaatregeling klep is verbonden met de comnon rail-leiding voor vloeibare ammoniak via de ammoniak inlaatleiding, waarbij een inlaat van de opslagtank voor vloeibare ammoniak achtereenvolgens is verbonden met een ammoniakretourre- gelklep en de veiligheidsklep, waarbij de veiligheidsklep is ver- bonden met de injector via de ammoniakretour pijp, en waarbij de opslagtank voor vloeibare ammoniak respectievelijk is verbonden met een waterstofopslagtank en een stikstofopslagtank.1. Liquid ammonia phase change refrigeration type hybrid energy thermal management system comprising an injector, a liquid ammonia hydrogen supply system, a liquid ammonia common rail line, a fuel oil common rail line and an oil tank, Liquid ammonia hydrogen supply system includes a liquid ammonia storage tank, an ammonia pumping system, a power distribution system and an ammonia inlet and outlet system, where the fuel oil common rail pipe is connected to the oil tank and a one-way oil pipe respectively. - inlet of the injector, wherein the common rail line for liquid ammonia is connected to the ammonia inlet and exhaust system respectively and a one-way ammonia inlet of the injector, wherein an ammonia inlet line and an ammonia return line are arranged in the ammonia inlet and outlet system, the ammonia pump system includes a flow divider for liquid ammonia storage, a low pressure pump and a high pressure pump, the flow distribution system includes a storage tank, an ammonia inlet control valve, a safety valve and an ammonia outlet control valve, where an out - the end of the liquid ammonia storage tank is successively connected to the low-pressure pump, the high-pressure pump, the flow distributor for liquid ammonia storage, the storage tank and the ammonia inlet control valve, whereby the ammonia inlet control valve is connected to the common rail line for liquid ammonia via the ammonia inlet pipe, wherein an inlet of the liquid ammonia storage tank is connected successively to an ammonia return control valve and the safety valve, wherein the safety valve is connected to the injector via the ammonia return pipe, and wherein the liquid ammonia storage tank is respectively connected with a hydrogen storage tank and a nitrogen storage tank. 2. Thermisch beheersysteem voor hybride energie van het koelende type met faseovergang van vloeibare ammoniak volgens conclusie 1, waarbij de injector een injectorlichaam, een injectiedeel voor vloeibare ammoniak en een injectiedeel voor diesel omvat, waarbij het injectiedeel voor vloeibare ammoniak en het injectiedeel voor diesel zich bevinden in het injectorlichaam, waarbij het injectie- deel voor vloeibare amoniak omvat een drukmodule, een eerste drukopslag resonantiestroom beperkende module, een superhysterese elektromagnetische regelactuator en een faseovergang bestuurbare super-atomisatie mondstukmodule die van boven naar beneden zijn gerangschikt, en waarbij het injectiedeel voor diesel omvat een tweede drukopslag resonantiestroom beperkende module, een extra drukmodule, een elektromagnetische regelactuator van het drukba- lanstype en een naaldklep met een excentrisch zelf instellend mondstuk die van boven naar beneden zijn gerangschikt.2. The liquid ammonia phase change cooling type hybrid energy thermal management system according to claim 1, wherein 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 being located in the injector body, wherein the liquid ammonia injection part includes a pressure module, a first pressure storage resonance current limiting module, a super hysteresis electromagnetic control actuator and a phase change controllable super-atomization nozzle module arranged from top to bottom, and wherein the diesel injection part includes a second pressure storage resonant current limiting module, an additional pressure module, a pressure balance type electromagnetic control actuator and a needle valve with an eccentric self-adjusting nozzle arranged from top to bottom. 3. Thermisch beheersysteem voor hybride energie van het koelende type met faseovergang van vloeibare ammoniak volgens conclusie 2, waarbij de onder druk zettende module omvat een onder druk zettend magneetjuk, onder druk zettende hoofd- en extra magneetpolen, een onder druk zettende hoofdzuiger, een onder druk zettend anker, een onder druk zettend beperkt blok, een onder druk zettende dubbelaf- dichtende klepstang, een onder druk zettende bovenste klepstang- zitting en een onder druk zettende onderste klepstangzitting, waarbij het onder druk zettende anker de bovenkant van de onder druk zettende dubbel afdichtende klepstang omhult, waarbij een on- der druk zettende terugstelveer is aangebracht tussen het onder druk zettende magneetjuk en het onder druk zettende anker, waarbij de onder druk zettende hoofd- en extra magneetpolen zijn aange- bracht aan de buitenzijde van de onder druk zettende terugstel- veer, waarbij spoelen zijn gewikkeld rond de onder druk zettende hoofd- en extra magneetpolen, waarbij het midden van de onder druk zettende dubbel afdichtende klepstang zich bevindt in de onder druk zettende bovenste klepstangzitting, waarbij de onderkant van de onder druk zettende dubbel afdichtende klepstang zich bevindt in de onder druk zettende onderste klepstangzitting, het midden van de onder druk zettende dubbel afdichtende klepstang is omhuld met een onder druk zettende klepstang-terugstelveer, een onder druk zettend dubbel afdichtend uitsteeksel is aangebracht tussen het midden en de onderkant van de onder druk zettende dubbel af- dichtende klepstang, waarbij afdichtende oppervlakken zijn aange-3. The liquid ammonia phase change cooling type hybrid energy thermal management system according to claim 2, wherein the pressurizing module includes a pressurizing magnet yoke, pressurizing main and auxiliary magnet poles, a pressurizing main piston, a pressurizing pressurizing armature, a pressurizing limited block, a pressurizing double seal valve stem, a pressurizing upper valve stem seat and a pressurizing lower valve stem seat, with the pressurizing anchor touching the top of the pressurizing double sealing valve stem, with a pressurized return spring located between the pressurized magnet yoke and the pressurized armature, the pressurized main and auxiliary magnet poles being mounted on the outside of the pressurized return - spring, having coils wound around the pressurizing main and auxiliary magnet poles, with the center of the pressurizing double-sealing valve stem located in the pressurizing upper valve stem seat, with the bottom of the pressurizing double-sealing valve stem located in the pressurizing lower valve stem seat, the center of the pressurizing double sealing valve stem is encased in a pressurizing valve stem return spring, a pressurizing double sealing protrusion is provided between the center and the bottom of the pressurizing folding double-sealing valve stem, with sealing surfaces bracht op de oppervlakken, overeenkomend met de onder druk zetten- de dubbel afdichtende klepstang, van de onder druk zettende boven- ste klepstangzitting en de onder druk zettende onderste klepstang- zitting, waarbij de hoofddrukzuiger zich bevindt onder de onder druk zettende onderste klepstangzitting en uitwendig is omhuld met een hoofddrukzuigerterugstelveer, een aangesloten ammoniakretour- kanaal is aangebracht in de onder druk zettende bovenste klep- stangzitting, een ammoniak inlaatkanaal en een middelste pijplei- ding zijn aangebracht in de onder druk zettende klepstangzitting, waarbij de ruimte waar het onder druk zettende dubbel afdichtende uitsteeksel zich bevindt in de onder druk zettende onderste klep- stangzitting een verbonden ruimte is, en de verbonden ruimte com- municeert met de middelste pijpleiding.applied to the surfaces, corresponding to the pressurized double seal valve stem, of the pressurized upper valve stem seat and the pressurized lower valve stem seat, the main pressure piston being located below the pressurized lower valve stem seat and externally is encased in a main pressure piston return spring, a connected ammonia return channel is provided in the pressurizing upper valve stem seat, an ammonia inlet channel and a center pipeline are provided in the pressurizing valve stem seat, with the space where the pressurizing double sealing protrusion located in the pressurized lower valve stem seat is a bonded space, and the bonded space communicates with the center pipeline. 4. Thermisch beheersysteem voor hybride energie van het koelende type met faseovergang van vloeibare ammoniak volgens conclusie 2, waarbij de eerste drukopslag resonantiestroom beperkende module een resonantieblok, een middenblok, een prismatisch afdichtblok, een stroom beperkende zuiger en een klepzitting voor drukopslag omvat, waarbij een drukopslagholte is gevormd in het injectorli- chaam onder de hoofddrukzuiger, waarbij de eenrichtingsinlaat voor ammoniak is gevormd in de zijwand van de drukopslagholte, waarbij een vloeistofkoelleidinginlaat wordt gevormd in het injector li- chaam en communiceert met de drukopslagholte, waarbij het resonan- tieblok, het middenblok, het prismatische afdichtingsblok en de drukopslag klepzitting achtereenvolgens zijn gerangschikt onder de drukopslagholte, waarbij de stroom beperkende zuiger is gerang- schikt in de drukopslag klepzitting, waarbij in het middenblok een terugstelveer voor het middenblok is aangebracht, een ammoniak- inlaatgat en een smoorgat in het ammoniak-inlaatpad van het reso- nantieblok respectievelijk zijn gevormd in de onderkant van het middelste blok, waarbij het prismatische afdichtingsblok zich be- vindt boven de stroom beperkende zuiger, een middelste gat is ge- vormd in de stroom beperkende zuiger, een terugstelveer van de stroom beperkende zuiger is aangebracht onder de stroom beperkende zuiger en een opslag holte wordt gevormd onder de terugstelveer van de stroom beperkende zuiger.4. The liquid ammonia phase change cooling type hybrid energy thermal management system according to claim 2, wherein the first pressure storage resonant current limiting module includes a resonant block, a center block, a prismatic sealing block, a flow limiting piston and a pressure storage valve seat, wherein a pressure storage cavity is formed in the injector body below the main pressure piston, wherein the one-way inlet for ammonia is formed in the side wall of the pressure storage cavity, wherein a liquid cooling line inlet is formed in the injector body and communicates with the pressure storage cavity, wherein the resonance block, the center block, the prismatic sealing block and the pressure storage valve seat are arranged successively under the pressure storage cavity, with the flow restricting piston arranged in the pressure storage valve seat, with a center block return spring, an ammonia inlet hole and a throttling hole in the center block. the ammonia inlet path of the resonance block are respectively formed in the bottom of the center block, with the prismatic seal block located above the flow restricting piston, a center hole is formed in the flow restricting piston, a return spring of the flow restricting piston is arranged under the flow restricting piston and a storage cavity is formed under the return spring of the flow restricting piston. 5. Thermisch beheersysteem voor hybride energie van het koelende type met faseovergang van vloeibare ammoniak volgens conclusie 2, waarbij de superhysterese elektromagnetische regelactuator omvat superhysterese hoofd- en extra magneetpolen, een hysteresezitting, een superhysterese bovenste klepstang, een superhysterese onderste kegelklep en een superhysterese schotelklep, waarbij spoelen zijn gewikkeld in de superhysterese hoofd- en extra magneetpolen, waar- bij een superhysterese materiaal is aangebracht in doorgaande ga- ten van de superhysterese hoofd- en extra magneetpolen, waarbij een hysterese zitting, een superhysterese bovenste klepstang, een superhysterese onderste eindconusklep en een superhysterese scho- telklep achtereenvolgens zijn gerangschikt onder het superhystere- se materiaal, waarbij de superhysterese schotelklep zich bevindt in een super-hysterese schotelklepholte, waarbij een superhystere- se schotelklepterugstelveer is aangebracht onder de superhysterese schotelklep, een olieretouroliekanaal en een olie-inlaatoliekanaal zijn aangebracht In het injectorlichaam waar de superhysterese elektromagnetische regelactuator zich bevindt, waarbij het oliere- touroliekanaal communiceert met de superhysterese schotelklephol- te, een superhysterese conusklep olie-inlaatgat is gevormd in een superhysterese onderste uiteinde conusklepschaal buiten de super- hysterese onderste kegelklep, en de superhysterese conusklep olie- inlaatgat communiceert met het olie-inlaatoliekanaal.5. The thermal management system for hybrid energy of liquid ammonia phase change refrigeration type according to claim 2, wherein the super hysteresis electromagnetic control actuator includes super hysteresis main and auxiliary magnet poles, a hysteresis seat, a super hysteresis upper valve stem, a super hysteresis lower cone valve and a super hysteresis poppet valve, wherein coils are wound in the superhysteresis main and auxiliary magnet poles, wherein a superhysteresis material is arranged in through holes of the superhysteresis main and auxiliary magnet poles, wherein a hysteresis seat, a superhysteresis upper valve stem, a superhysteresis lower end cone valve and a super hysteresis poppet valve are arranged successively under the super hysteresis material, wherein the super hysteresis poppet valve is located in a super hysteresis poppet valve cavity, wherein a super hysteresis poppet valve return spring is arranged under the super hysteresis poppet valve, an oil return oil channel and an oil inlet oil channel are provided In the injector body where the super hysteresis electromagnetic control actuator is located, where 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 cone valve, and the super hysteresis cone valve oil inlet hole communicates with the oil inlet oil channel. 6. Thermisch beheersysteem voor hybride energie van het koelende type met faseovergang van vloeibare ammoniak volgens conclusie 2, waarbij de superatomisatie mondstukmodule met regelbare faseveran- dering omvat een superatomisatie mondstuklichaam, een superatomi- satie klepzitting, een statische lekvrije cilinder, een superato- misatie naaldkleplichaam en een superatomisatie regelklepstang, waarbij de superatomisatie klepzitting zich bevindt in het supera- tomisatie mondstuklichaam, waarbij de statische lekvrije cilinder en het superatomisatie naaldkleplichaam zich bevinden in de su- peratomisatie klepzitting, waarbij de kop van het superatomisatie naaldkleplichaam zich bevindt in de statische lekvrije cilinder, waarbij een superatomisatie naaldkleplichaam-terugstelveer is aan-6. The thermal management system for hybrid energy of liquid ammonia phase change refrigeration type according to claim 2, wherein the superatomization nozzle module with controllable phase change includes a superatomization nozzle body, a superatomization valve seat, a static leak-proof cylinder, a superatomization needle valve body and a superatomization control valve stem, wherein the superatomization valve seat is located in the superatomization nozzle body, wherein the static leak-free cylinder and the superatomization needle valve body are located in the super-atomization valve seat, the head of the superatomization needle valve body is located in the static leak-free cylinder , where a superatomization needle valve body return spring is fitted gebracht tussen het midden van het superatomisatie naaldklep- lichaam en de statische lekvrije cilinder, waarbij een ammoniakop- slagholte wordt gevormd tussen de statische lekvrije cilinder, het superatomisatie naaldkleplichaam en de superatomisatie klepzit- ting, waarbij een inlaatpijpleiding voor vloeibaar koelend ar- beidsmedium en een uitlaatpijpleiding voor vloeibaar koelend ar- beidsmedium zijn gevormd tussen de superatomisatie klepzitting en het superatomisatie mondstuklichaam, waarbij de onderkant van het superatomisatie naaldkleplichaam en de onderkant van de superato- misatie klepzitting een superatomisatie injectiestroomkanaal vor- men, waarbij de ammoniakopslagholte communiceert met de opslaghol- te, en een superatomisatie controleholte wordt gevormd tussen de bovenkant van het superatomisatie naaldkleplichaam en het in- jectorlichaam boven het superatomisatie naaldkleplichaam.between the center of the superatomization needle valve body and the static leak-proof cylinder, thereby forming an ammonia storage cavity between the static leak-proof cylinder, the super-atomization needle valve body and the super-atomization valve seat, forming an inlet pipeline for liquid cooling working medium and a exhaust pipeline for liquid cooling working medium are formed between the superatomization valve seat and the superatomization nozzle body, wherein the bottom of the superatomization needle valve body and the bottom of the superatomization valve seat form a superatomization injection flow channel, wherein the ammonia storage cavity communicates with the storage cavity , and a superatomization control cavity is formed between the top of the superatomization needle valve body and the injector body above the superatomization needle valve body. 7. Thermisch beheersysteem voor hybride energie van het koelende type met faseovergang van vloeibare ammoniak volgens conclusie 2, waarbij de structuur van de tweede resonantie stroom beperkende module van de drukopslag dezelfde is als die van de eerste reso- nantie stroom beperkende module van de drukopslag, en de tweede resonantie stroom beperkende module van de drukopslag en de eerste resonantie stroom beperkende module van de drukopslag parallel in het injectorlichaam zijn gerangschikt.The liquid ammonia phase change cooling type hybrid energy thermal management system according to claim 2, wherein the structure of the second resonance current limiting module of the pressure storage is the same as that of the first resonant current limiting module of the pressure storage, and the second resonance current limiting module of the pressure storage and the first resonance current limiting module of the pressure storage are arranged in parallel in the injector body. 8. Thermisch beheersysteem voor hybride energie van het koelende type met faseovergang van vloeibare ammoniak volgens conclusie 2, waarbij de extra drukmodule omvat een extra drukmagneetjuk, extra drukhoofd- en extra magneetpolen, een extra drukzuiger, een extra drukarmatuur, een extra drukmechanisme, een onder druk zettend be- perkt blok, een extra onder druk zettende dubbele afdichtingsklep- stang, een extra onder druk zettende bovenste klepstangzitting en een extra onder druk zettende onderste klepstangzitting, waarbij het extra onder druk zettende armatuur de bovenkant van de extra onder druk zettende dubbel afdichtende klepstang omhult, een extra drukterugstelveer is aangebracht tussen het extra drukmagneet juk en het extra drukarmatuur, waarbij extra onder druk zettende hoofd- en extra magneetpolen zijn aangebracht aan de buitenzijde van de extra onder druk zettende terugstelveer, spoelen zijn ge- wikkeld rond de extra onder druk zettende hoofd- en extra magneet- polen, het midden van de extra onder druk zettende dubbelafdich- tende klepstang zich bevindt in de extra onder druk zettende bo-8. The liquid ammonia phase change cooling type hybrid energy thermal management system according to claim 2, wherein the additional pressure module includes an additional pressure magnet yoke, additional pressure main and additional magnet poles, an additional pressure piston, an additional pressure armature, an additional pressure mechanism, an additional pressurized limited block, an additional pressurization double seal valve stem, an additional pressurization upper valve stem seat and an additional pressurization lower valve stem seat, with the additional pressurization fitting covering the top of the additional pressurization double seal valve stem, an additional pressure return spring is provided between the additional pressure magnet yoke and the additional pressure armature, with additional pressurizing main and additional magnet poles being provided on the outside of the additional pressurizing return spring, coils are wound around the additional lower pressurizing main and auxiliary magnet poles, the center of the auxiliary pressurizing double-sealing valve stem is located in the auxiliary pressurizing top venste klepstangzitting, waarbij de onderkant van de extra onder druk zettende dubbel afdichtende klepstang zich bevindt in de ex- tra onder druk zettende onderste klepstangzitting, het midden van de extra onder druk zettende dubbel afdichtende klepstang is om- huld door een extra onder druk zettende klepstang terugstelveer,window valve stem seat, wherein the bottom of the extra pressurized double seal valve stem is located in the extra pressurized lower valve stem seat, the center of the extra pressurized double seal valve stem is encased in an extra pressurized valve stem return spring, waarbij een extra onder druk zettende dubbel afdichtend uitsteek- sel is aangebracht tussen het midden en de onderkant van de extra onder druk zettende dubbel afdichtende klepstang, waarbij afdich- tende oppervlakken zijn aangebracht op de oppervlakken, overeenko- mend met de extra onder druk zettende dubbel afdichtende klep-wherein an additional pressurized double seal projection is provided between the center and the bottom of the additional pressurized double seal valve stem, sealing surfaces being provided on the surfaces corresponding to the additional pressurization double sealing valve - stang, van de extra onder druk zettende bovenste klepstangzitting en de extra onder druk zettende onderste klepstangzitting, waarbij de extra onder druk zettende zuiger zich bevindt onder de extra onder druk zettende onderste klepstangzitting en die aan de bui- tenkant is omhuld met een extra onder druk zettende zuigerterug-rod, of the additional pressurized upper valve stem seat and the additional pressurized lower valve stem seat, the additional pressurized piston being located below the additional pressurized lower valve stem seat and being enveloped on the outside by an additional pressurized setting piston return stelveer , waarbij een olie retourleiding is aangebracht in de ex- tra onder druk zettende bovenste klepstang zitting, waarbij een extra kanaal voor onder druk zettende olie en een extra verbin- dingskanaal voor onder druk brengen zijn aangebracht in de onder- ste klepstang zitting, waarbij het extra kanaal voor onder druk zettende olie respectievelijk in verbinding staat met een olie- inlaatkanaal en het onderste gedeelte van het dubbele onder druk zettende uitsteeksel, waarbij de ruimte waar het extra onder druk zettende dubbel afdichtende uitsteeksel zich bevindt in een aange- sloten ruimte, waarbij het extra onder druk zettende communicatie-adjusting spring, wherein an oil return line is provided in the additional pressurization upper valve stem seat, wherein an additional pressurization oil channel and an additional pressurization connection channel are provided in the lower valve stem seat, wherein the auxiliary pressurizing oil channel is respectively connected to an oil inlet channel and the lower portion of the double pressurization projection, the space where the additional pressurization double sealing projection is located in a connected space, where the additional pressure on communication kanaal respectievelijk in verbinding staat met de aangesloten ruimte en het bovenste gedeelte van de extra onder druk zettende zuiger, waarbij een afdichtingskogel is aangebracht in het olie- inlaatkanaal, waarbij een terugstelveer voor de afdichtingskogel onder de afdichtingskogel is aangebracht, en waarbij een olielei-channel is respectively in communication with the connected space and the upper part of the additional pressurization piston, a sealing ball being arranged in the oil inlet channel, a sealing ball return spring being arranged under the sealing ball, and an oil guide ding voor onder druk zettende olie onder de extra drukzuiger is aangebracht en in verbinding staat met het olie-inlaatkanaal onder de terugstelveer van de afdichtingskogel.pressurizing oil device is located under the additional pressure piston and is connected to the oil inlet channel under the return spring of the sealing ball.
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