WO2019192078A1 - Two-stage turbocharging system - Google Patents

Two-stage turbocharging system Download PDF

Info

Publication number
WO2019192078A1
WO2019192078A1 PCT/CN2018/091995 CN2018091995W WO2019192078A1 WO 2019192078 A1 WO2019192078 A1 WO 2019192078A1 CN 2018091995 W CN2018091995 W CN 2018091995W WO 2019192078 A1 WO2019192078 A1 WO 2019192078A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure stage
heat exchanger
low
internal combustion
combustion engine
Prior art date
Application number
PCT/CN2018/091995
Other languages
French (fr)
Chinese (zh)
Inventor
舒歌群
李晓雅
田华
李君峰
Original Assignee
天津大学
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 天津大学 filed Critical 天津大学
Publication of WO2019192078A1 publication Critical patent/WO2019192078A1/en

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/065—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
    • F01K17/06—Returning energy of steam, in exchanged form, to process, e.g. use of exhaust steam for drying solid fuel or plant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F02B29/0437—Liquid cooled heat exchangers
    • F02B29/0443—Layout of the coolant or refrigerant circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/32—Engines with pumps other than of reciprocating-piston type
    • F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
    • F02B33/40—Engines with pumps other than of reciprocating-piston type with rotary pumps of non-positive-displacement type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F02B39/02—Drives of pumps; Varying pump drive gear ratio
    • F02B39/08—Non-mechanical drives, e.g. fluid drives having variable gear ratio
    • F02B39/085—Non-mechanical drives, e.g. fluid drives having variable gear ratio the fluid drive using expansion of fluids other than exhaust gases, e.g. a Rankine cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F02B39/02—Drives of pumps; Varying pump drive gear ratio
    • F02B39/12—Drives characterised by use of couplings or clutches therein
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F02B39/16—Other safety measures for, or other control of, pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • F02G5/04—Profiting from waste heat of exhaust gases in combination with other waste heat from combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2260/00—Recuperating heat from exhaust gases of combustion engines and heat from cooling circuits
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to the field of turbochargers, and more particularly to a two-stage turbocharger system.
  • the supercharging technology can improve the power and economy of the internal combustion engine.
  • the operating conditions of the internal combustion engine are variable, and the speed range is from the lowest stable speed to the rated speed, or even higher.
  • the load change can be from zero to full load until the smoke limit.
  • the choice of design point usually results in two kinds of results: if the high speed is matched, the internal pressure of the internal combustion engine will be insufficient at low speed, and the torque characteristic will be significantly deteriorated. If the speed is matched, the internal combustion engine is Under heavy load conditions, the charge air pressure is too high and the supercharger is overspeed.
  • turbocharger itself and the booster system.
  • These technologies have achieved good results in the matching of turbochargers and internal combustion engines.
  • In order to simultaneously consider high speed and low speed performance there is inevitably a problem of compromise and energy waste, which is caused by insufficient exhaust energy at low speed. Limitation of insufficient booster air pressure. If the problem of low speed torque difference can be overcome, the torque characteristics of the turbocharged internal combustion engine will be further improved.
  • the cooling system After the normal operation of the internal combustion engine, the cooling system will work normally, which is limited by the current internal combustion engine technology. Generally, the energy contained in the internal combustion engine cooling system accounts for more than 20% of the total heat of the fuel combustion. If this part of energy can be recycled, the low-speed operation of the internal combustion engine. Pushing a turbine to work with the original exhaust-driven turbocharger can improve the torque difference of the turbocharged internal combustion engine under low-speed conditions.
  • the invention is based on the above-mentioned state of the art and research ideas, and proposes a two-stage turbocharging system driven by residual heat of an internal combustion engine to improve the low speed performance of the turbocharged internal combustion engine.
  • the waste heat recovery system is optimized to realize the effective utilization of the residual heat energy in the turbocharged internal combustion engine at high speed.
  • a basic structure of a two-stage turbocharger system proposed by the present invention includes an internal combustion engine, an intercooler, a high-pressure stage turbocharger, and a low-pressure stage turbocharger, and the high-pressure stage turbocharger.
  • the high-pressure stage compressor is composed of a coaxially connected high-pressure stage compressor and a high-pressure stage turbine;
  • the low-pressure stage turbocharger is composed of a low-pressure stage compressor and a low-pressure stage turbine;
  • the high-pressure stage compressor is connected in series with the low-pressure stage compressor.
  • the high pressure stage compressor is connected to the internal combustion engine through a charge air side of the intercooler, the low pressure stage turbine of the two stage boost system is driven by a waste heat recovery system, the waste heat recovery system comprising cooling in series a working fluid tank, a compressor, a cylinder and a water jacket heat exchanger, wherein an outlet of the compressor is connected to a working fluid side inlet of the cylinder water heat exchanger, and a working fluid side of the cylinder water heat exchanger The outlet is connected to the working medium side inlet of the cooler after passing through the low pressure stage turbine; the cylinder liner water of the internal combustion engine passes through the outlet pipe and enters the water side of the cylinder liner water heat exchanger after sufficient heat exchange After the return pipe Into the cylinder liner of the internal combustion engine; a coupling is also arranged between the low-pressure stage turbine and the low-pressure stage compressor.
  • the two-stage turbocharging system of the present invention can further optimize the above basic scheme according to the actual situation, thereby realizing efficient recycling of the residual heat energy of the internal combustion engine in the whole working condition while improving the low-speed torque performance of the internal combustion engine.
  • Another improved technical solution proposed by the present invention is to connect the outlet of the compressor to the inlet of the secondary fluid side of the intercooler based on the above basic scheme, and the secondary fluid side of the intercooler
  • the outlet is connected to the working side inlet of the liner water heat exchanger, and the working side outlet of the cylinder water heat exchanger is connected to the low pressure stage turbine.
  • the two-stage turbocharger system proposed by the present invention realizes the utilization of the exhaust heat energy of the internal combustion engine by adding a flue gas heat exchanger, that is, the water jacket heat exchanger of the cylinder liner a flue gas heat exchanger is further disposed between the working medium side outlet and the low pressure stage turbine, and the exhaust gas of the internal combustion engine is connected to the flue gas side inlet of the flue gas heat exchanger via the high pressure stage turbine, the smoke The gas side outlet is connected to the atmosphere or to the internal combustion engine aftertreatment system.
  • a flue gas heat exchanger that is, the water jacket heat exchanger of the cylinder liner
  • a flue gas heat exchanger is further disposed between the working medium side outlet and the low pressure stage turbine, and the exhaust gas of the internal combustion engine is connected to the flue gas side inlet of the flue gas heat exchanger via the high pressure stage turbine, the smoke The gas side outlet is connected to the atmosphere or to the internal combustion engine aftertreatment system.
  • the recovery of the spent steam energy of the low-pressure stage turbine outlet working medium is realized by adding an intermediate heat exchanger, that is, an intermediate heat exchanger is disposed between the working medium side outlet of the cylinder jacket water heat exchanger and the flue gas heat exchanger.
  • the medium is connected to the low pressure working side of the intermediate heat exchanger and the cooler in turn via the low pressure stage turbine, and the working medium side outlet of the cylinder water heat exchanger is connected to the high pressure work of the intermediate heat exchanger
  • the mass side inlet so that the low pressure working medium of the low pressure stage turbine outlet enters the intermediate heat exchanger and exchanges with the high pressure working medium discharged from the cylinder jacket water heat exchanger to enter the cooler.
  • the working process of the two-stage turbocharging system proposed by the invention is: in the high-speed working condition of the internal combustion engine, the coupling is disconnected, only the high-pressure turbocharger is used to realize the intake supercharging, and the low-pressure stage turbine will be recycled.
  • the residual heat of the internal combustion engine is converted into effective work output or power generation or as an auxiliary power of the vehicle; in the low speed condition of the internal combustion engine, the coupling is connected, and the low-pressure stage turbocharger and the high-pressure stage turbocharger work simultaneously to realize the intake supercharging.
  • the system of the invention integrates a two-stage turbocharger system and an internal combustion engine waste heat recovery system, and a coupling is arranged between the low-pressure stage turbine and the low-pressure stage compressor, and the high-temperature high-pressure working medium after the residual heat of the internal combustion engine is recovered by the waste heat recovery system. Promote the rotation of the low-pressure stage turbine.
  • the coupling is connected to realize the series-type intake supercharging with the high-pressure turbocharger.
  • the coupling is disconnected, and the residual heat of the internal combustion engine is realized by the low-pressure stage turbine. Can be converted into output work.
  • the installation of the system can not only improve the low-speed torque performance of the turbocharged internal combustion engine, but also realize the waste heat utilization of the full working condition of the internal combustion engine, which has significant economic benefits and application prospects.
  • Embodiment 1 is a schematic structural view of Embodiment 1 of a two-stage turbocharger system of the present invention
  • Embodiment 2 is a schematic structural view of Embodiment 2 of a two-stage turbocharger system according to the present invention
  • Embodiment 3 is a schematic structural view of Embodiment 3 of a two-stage turbocharger system according to the present invention.
  • Embodiment 4 is a schematic structural view of Embodiment 4 of a two-stage turbocharger system according to the present invention.
  • Figure 5 is a schematic structural view of Embodiment 5 of the two-stage turbocharger system of the present invention.
  • Figure 6 is a schematic structural view of Embodiment 6 of the two-stage turbocharger system of the present invention.
  • the thin solid line is the air intake path of the internal combustion engine
  • the dotted line is the secondary fluid side path of the intercooler
  • the dotted line is the exhaust path of the internal combustion engine
  • the dotted line is the closed loop path of the cylinder liner of the internal combustion engine
  • the thick solid line is the power cycle of the waste heat recovery system.
  • 1-Internal combustion engine 2-intercooler, 3-high pressure stage compressor, 4-high pressure stage turbine, 5-low pressure stage compressor, 6-low pressure stage turbine, 7-cooler, 8-plast tank, 9-compression Machine, 10-cylinder jacket water heat exchanger, 11-coupling, 12-smoke heat exchanger, 13-intermediate heat exchanger.
  • a two-stage turbocharger system is configured to include an internal combustion engine 1, an intercooler 2, a high-pressure stage turbocharger, and a low-pressure stage turbocharger, the high-pressure stage.
  • the turbocharger is constituted by a coaxially connected high-pressure stage compressor 3 and a high-pressure stage turbine 4;
  • the low-pressure stage turbocharger is composed of a low-pressure stage compressor 5 and a low-pressure stage turbine 6;
  • the high-pressure stage compressor 3 and The low-pressure stage compressor 5 is connected in series, and the high-pressure stage compressor 3 is connected to the internal combustion engine 1 through a charge air side of the intercooler 2, and the low-pressure stage turbine 6 of the two-stage supercharging system is recovered from waste heat.
  • the waste heat recovery system includes a cooler 7 in series, a working tank 8, a compressor 9 and a jacket water heat exchanger 10, and an outlet of the compressor 9 is connected to the cylinder water heat exchanger a working medium side inlet of the cylinder water heat exchanger 10, the working medium side outlet of the cylinder water heat exchanger 10 is connected to the working medium side inlet of the cooler 7 through the low pressure stage turbine 6; the cylinder liner water of the internal combustion engine 1 After passing through the water outlet pipe, the water side of the cylinder liner water entering the cylinder jacket water heat exchanger 10 passes through sufficient heat exchange.
  • the return pipe enters the cylinder liner of the internal combustion engine to form a closed circuit; and a coupling 11 is further disposed between the low-pressure stage turbine 6 and the low-pressure stage compressor 5.
  • the working process of the two-stage turbocharger system of the first embodiment is as follows: the working medium in the working fluid tank 8 is compressed and pressurized by the compressor 9, and then the water in the cylinder water heat exchanger 10 is absorbed in the cylinder water heat exchanger 10 to form a high temperature and high pressure work. The mass gas then expands into the low pressure stage turbine 6 to propel the low pressure stage turbine 6 to rotate. The cylinder liner water of the internal combustion engine enters the internal combustion engine 1 through heat exchange between the jacket water heat exchanger 10 to form a closed loop.
  • the coupling 11 In the low-speed operating condition of the internal combustion engine, the coupling 11 is connected, and the low-pressure stage turbine drives the low-pressure stage compressor to rotate, so that the first-stage supercharging of the intake air is achieved, and the supercharged air immediately enters the high-pressure stage compressor to realize the intake air. Secondary pressurization.
  • the coupling 11 In the high-speed operating condition of the internal combustion engine, the coupling 11 is disconnected, and only the high-pressure stage turbocharger is used to achieve intake supercharging, and the low-pressure stage turbine 6 converts the recovered residual heat of the internal combustion engine into an effective work output or power generation or as a vehicle. Auxiliary power.
  • the feature of the first embodiment is that the low-pressure stage turbine is driven by the high-temperature high-pressure working gas by completely recovering the residual heat of the liner water under the low-speed operating condition, and the high-speed turbocharger is combined to improve the low-speed torque performance of the turbocharger.
  • the function of the waste heat recovery system is utilized to convert the residual heat of the internal combustion engine into an effective work output or power generation or as an auxiliary power of the vehicle.
  • the two-stage turbocharger system of the second embodiment adds the flue gas heat exchanger 12 to the first embodiment to fully
  • the exhaust gas energy of the high-pressure stage turbine 4 outlet engine is recovered, that is, a flue gas heat exchanger 12 is further disposed between the working medium side outlet of the cylinder jacket water heat exchanger 10 and the low-pressure stage turbine 6, and the exhaust gas of the internal combustion engine 1
  • the gas After passing through the high-pressure stage turbine 4, the gas is connected to the flue gas side inlet of the flue gas heat exchanger 12, and the flue gas side outlet is connected to the atmospheric environment or connected to the internal combustion engine after-treatment system, so that the vortex is exhausted Heat exchange with the working fluid.
  • the working process of the system of the above embodiment 2 is basically the same as that of the first embodiment. The only difference is that the working fluid after absorbing the water energy of the cylinder liner water from the cylinder water heat exchanger 10 enters the flue gas heat exchanger 12 to recover the exhaust of the internal combustion engine. The residual heat energy is then re-expanded into the low-pressure stage turbine 6 to perform work.
  • the system can fully utilize the exhaust energy under high-speed conditions, and further improve the application of the waste heat recovery system under high-speed conditions on the basis of improving the turbocharged low-speed torque performance, and realize the residual heat energy of the internal combustion engine.
  • the efficient use of the internal combustion engine improves the power and economy of the internal combustion engine, and the technical applicability is wide.
  • a two-stage turbocharger system of Embodiment 3 adds the intermediate heat exchanger 13 to the second embodiment, namely: An intermediate heat exchanger 13 is further disposed between the working fluid side outlet of the cylinder water heat exchanger 10 and the flue gas heat exchanger 12, and the working medium is sequentially connected to the intermediate heat exchanger 13 via the low pressure stage turbine 6 a low pressure working fluid side and a cooler 7, the working medium side outlet of the cylinder water heat exchanger 10 is connected to the high pressure working side inlet of the intermediate heat exchanger 13, so that the low pressure working of the low pressure stage turbine 6 outlet The medium enters the intermediate heat exchanger 13 and exchanges heat with the high-pressure working fluid discharged from the cylinder water heat exchanger 10 to enter the cooler 7 to realize recovery of the spent steam energy after the expansion work.
  • the working process of the system of Embodiment 3 is basically the same as that of Embodiment 2, the difference is only: the high-pressure working medium after absorbing the water energy of the cylinder liner water from the water-cylinder water heat exchanger 10 first enters the intermediate heat exchanger 13 and then enters the heat exchange of the flue gas.
  • the compressor 12 expands from the low-pressure stage turbine 6 and enters the intermediate heat exchanger 13 and then enters the cooler 7.
  • the characteristic of the embodiment is that: according to the common method for optimizing the performance of the waste heat recovery system, the intermediate heat exchanger is added to increase the output work of the waste heat recovery system, and the further utilization of energy is realized by recovering the spent steam energy of the turbine outlet working medium.
  • This embodiment is particularly suitable for working conditions where the output of the residual heat recovery system is significantly improved by adding an intermediate heat exchanger.
  • FIG. 4 shows another embodiment of implementing the two-stage turbocharger system of the present invention.
  • the waste heat recovery system is further integrated with the intercooler 2, thereby reducing the original intercooler 2 Increased internal combustion engine power consumption by air cooling or water cooling.
  • the specific structure is: including an internal combustion engine 1, an intercooler 2, a high-pressure stage turbocharger and a low-pressure stage turbocharger, the high-pressure stage turbocharger adopts a coaxial high-pressure stage compressor 3 and a high-pressure stage turbine.
  • the low-pressure stage turbocharger is composed of a low-pressure stage compressor 5 and a low-pressure stage turbine 6; the high-pressure stage compressor 3 is connected in series with the low-pressure stage compressor 5, and the high-pressure stage compressor 3 passes through
  • the charge air side of the intercooler 2 is connected to the internal combustion engine 1, and the low-pressure stage turbine 6 of the two-stage supercharging system is driven by a waste heat recovery system comprising a cooler 7 in series, working medium a tank 8 and a compressor 9, an outlet of the compressor 9 is connected to an inlet of a secondary fluid side of the intercooler 2, and an outlet of the secondary fluid side of the intercooler 2 is connected to the cylinder liner for water exchange a working medium side inlet of the heat exchanger 10, the working medium side outlet of the cylinder water heat exchanger 10 is connected to the working medium side inlet of the cooler 7 through the low pressure stage turbine 6; the cylinder of the internal combustion engine 1 After the water passes through the water outlet pipe, the water side of the cylinder liner water heat exchanger 10
  • the working process of the system of Embodiment 4 is basically the same as that of Embodiment 1, except that the high-pressure working medium compressed and pressurized by the compressor 9 first enters the intercooler 2, absorbs the high-temperature air energy after the supercharging, and then enters the cylinder liner water exchange.
  • the heater 10 implements further integration of the two-stage turbocharger system with the waste heat recovery system.
  • the feature of the fourth embodiment is that an intercooler is usually installed in the engine boosting system to reduce the temperature of the high temperature air after boosting, increase the intake air amount, and obtain a larger output power.
  • Common intercoolers are classified into air-cooled and water-cooled. Air-cooled fan power consumption and water-cooled cylinder liner pump power consumption add power loss to the internal combustion engine. After adopting the system described in Embodiment 4, the charge air in the intercooler is directly cooled by the waste heat recovery system working medium, which reduces the power consumption of the internal combustion engine.
  • a flue gas heat exchanger 12 is further disposed between the working medium side outlet of the cylinder water heat exchanger 10 and the low pressure stage turbine 6, and the internal combustion engine 1
  • the exhaust gas is connected to the flue gas side inlet of the flue gas heat exchanger 12 via the high pressure stage turbine 4, and the flue gas side outlet is connected to the atmospheric environment or to the internal combustion engine aftertreatment system.
  • an intermediate heat exchanger 13 is further disposed between the working medium side outlet of the cylinder water heat exchanger 10 and the flue gas heat exchanger 12, and the working medium is
  • the low pressure stage turbine 6 is sequentially connected to the low pressure working side of the intermediate heat exchanger 13 and the cooler 7, and the working medium side outlet of the cylinder water heat exchanger 10 is connected to the intermediate heat exchanger 13
  • the high pressure working medium side inlet so that the low pressure working medium of the outlet of the low pressure stage turbine 6 enters the intermediate heat exchanger 13 and exchanges with the high pressure working medium discharged from the cylinder water heat exchanger 10 to enter the cooler. 7.
  • the working process and features of Embodiment 6 are combined with Embodiment 3 and Embodiment 4 described above, and are not described herein again.
  • the working fluid of the waste heat recovery system is any one of water, CO 2 and CO 2 -based non-azeotropic mixed working fluid.
  • the system of the present invention drives the low pressure stage turbine 6 through a waste heat recovery system, and a coupling 11 is provided between the low pressure stage turbine 6 and the low pressure stage compressor 5.
  • the coupling 11 In the low-speed working condition of the internal combustion engine 1, the coupling 11 is connected, and the low-pressure stage turbine 6 is powered by the residual heat of the cylinder liner, and the intake boosting is realized by the two-stage turbocharging; the coupling 11 is in the high-speed working condition of the internal combustion engine 1 Disconnected, the intake pressure is only supercharged by the high-pressure stage turbine 4, and the cylinder jacket water, exhaust gas, charge air, and working fluid consumption energy are converted into effective work output or power generation or as a vehicle through the low-pressure stage turbine 6 Auxiliary power.
  • the system can not only solve the problem of low speed torque of turbocharged internal combustion engine, improve the low speed power of internal combustion engine, but also eliminate the original radiator fan, reduce energy loss, and use the waste heat recovery system for vehicle thermal management, which can realize the residual heat of the internal combustion engine under full working condition. Effective recycling of energy to improve fuel economy of internal combustion engines.
  • the compressor 9 and the cooler 7 are different depending on the type of working medium used in the waste heat recovery system. It may be deformed into a working fluid pump and a condenser.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Supercharger (AREA)

Abstract

A two-stage turbocharging system, comprising an internal combustion engine (1), an intercooler (2), a high-pressure stage turbocharger, and a low-pressure stage turbocharger. The high-pressure stage turbocharger consists of a high-pressure stage gas compressor (3) and a high-pressure stage turbine (4) that are coaxially connected. The low-pressure stage turbocharger consists of a low-pressure stage gas compressor (5) and a low-pressure stage turbine (6). The low-pressure stage turbine (6) of the two-stage turbocharging system is driven by a waste heat recovery system. Jacket water of the internal combustion engine (1) enters a jacket water side of a jacket water heat exchanger (10) by means of a water outlet pipe, and then enters a cylinder liner of the internal combustion engine (1) by means of a water return pipe after sufficient heat exchange. A coupling (11) is further provided between the low-pressure stage turbine (6) and the low-pressure stage gas compressor (5). The system not only improves the low-speed power performance of the internal combustion engine, but also implements effective recovery and utilization of waste heat energy under a full work condition of the internal combustion engine, thereby improving the fuel economic efficiency of the internal combustion engine.

Description

一种两级涡轮增压***Two-stage turbocharger system 技术领域Technical field
本发明涉及涡轮增压器技术领域，尤其涉及一种两级涡轮增压***。The present invention relates to the field of turbochargers, and more particularly to a two-stage turbocharger system.
背景技术Background technique
增压技术可提高内燃机的动力性及经济性。内燃机运行工况多变，其转速范围是从最低稳定转速到额定转速，甚至更高，其负荷变化可以从零到满负荷，直至冒烟极限，要使增压内燃机有良好的性能，就必须使涡轮增压器与内燃机有良好的匹配。The supercharging technology can improve the power and economy of the internal combustion engine. The operating conditions of the internal combustion engine are variable, and the speed range is from the lowest stable speed to the rated speed, or even higher. The load change can be from zero to full load until the smoke limit. To make the supercharged internal combustion engine have good performance, it must be The turbocharger is well matched to the internal combustion engine.
涡轮增压器与内燃机匹配时，设计点的选择通常会造成两种结果：如果高速配合，则会造成内燃机在低速时增压空气压力不足，扭矩特性显著变坏，如果低速配合，则内燃机在大负荷工况下增压空气压力过高，增压器超速。When the turbocharger is matched with the internal combustion engine, the choice of design point usually results in two kinds of results: if the high speed is matched, the internal pressure of the internal combustion engine will be insufficient at low speed, and the torque characteristic will be significantly deteriorated. If the speed is matched, the internal combustion engine is Under heavy load conditions, the charge air pressure is too high and the supercharger is overspeed.
目前国内外研究人员对涡轮增压器本身及增压***不断进行改进，出现了多种解决方案，主要有两条途径，一是改变涡轮增压器本身结构，如排气旁通阀、可变几何截面涡轮等，二是改变增压***结构，如进排气旁通、顺序增压、两级增压等。这些技术均在涡轮增压器与内燃机的匹配上取得了良好效果，然而，为同时兼顾高速和低速性能，不可避免的存在折中与能量浪费问题，这是由于受到低速时排气能量不足造成增压空气压力不足的限制。如果能克服低速扭矩差的问题，将进一步改善涡轮增压内燃机的扭矩特性。At present, researchers at home and abroad have continuously improved the turbocharger itself and the booster system. There are various solutions. There are two main ways. One is to change the structure of the turbocharger itself, such as the exhaust bypass valve. Variable geometry cross-section turbines, etc., the second is to change the structure of the booster system, such as intake and exhaust bypass, sequential boost, two-stage supercharging. These technologies have achieved good results in the matching of turbochargers and internal combustion engines. However, in order to simultaneously consider high speed and low speed performance, there is inevitably a problem of compromise and energy waste, which is caused by insufficient exhaust energy at low speed. Limitation of insufficient booster air pressure. If the problem of low speed torque difference can be overcome, the torque characteristics of the turbocharged internal combustion engine will be further improved.
内燃机正常运转后，冷却***随即正常工作，受限于当前内燃机技术，通常内燃机冷却***所含能量约占燃料燃烧总热量的20％以上，如果能够将这部分能量回收利用，在内燃机低速工况下推动一个涡轮做功，配合原有排气驱动的涡轮增压器，则可改善低速工况下涡轮增压内燃机扭矩差的问题。After the normal operation of the internal combustion engine, the cooling system will work normally, which is limited by the current internal combustion engine technology. Generally, the energy contained in the internal combustion engine cooling system accounts for more than 20% of the total heat of the fuel combustion. If this part of energy can be recycled, the low-speed operation of the internal combustion engine. Pushing a turbine to work with the original exhaust-driven turbocharger can improve the torque difference of the turbocharged internal combustion engine under low-speed conditions.
本发明基于上述技术现状和研究思路，提出一种内燃机余热驱动的两级涡轮增压***，用以改善涡轮增压内燃机低速性能。同时在此基础上优化余热回收***，用以实现涡轮增压内燃机高速工况时余热能的有效利用。通过对国内外相关的专利检索和分析，申请人未发现与本发明特征相近的技术方案。The invention is based on the above-mentioned state of the art and research ideas, and proposes a two-stage turbocharging system driven by residual heat of an internal combustion engine to improve the low speed performance of the turbocharged internal combustion engine. At the same time, on the basis of this, the waste heat recovery system is optimized to realize the effective utilization of the residual heat energy in the turbocharged internal combustion engine at high speed. Through the patent search and analysis of related patents at home and abroad, the applicant has not found a technical solution similar to the features of the present invention.
发明内容Summary of the invention
本发明的目的在于提供一种两级涡轮增压***，克服涡轮增压内燃机低速扭矩差的问题。It is an object of the present invention to provide a two-stage turbocharger system that overcomes the problem of low speed torque differentials in turbocharged internal combustion engines.
为了实现上述目的，本发明提出的一种两级涡轮增压***的基本结构是，包括内燃机、中冷器、高压级涡轮增压器和低压级涡轮增压器，所述高压级涡轮增压器采用同轴相连的高压级压气机和高压级涡轮构成；所述低压级涡轮增压器由低压级压气机和低压级涡轮构成；所述高压级压气机与所述低压级压气机串联，所述高压级压气机通过所述中冷器的增 压空气侧连接至所述内燃机，所述两级增压***的低压级涡轮由余热回收***驱动，所述余热回收***包括依次串联的冷却器、工质罐、压缩机和缸套水换热器，所述压缩机的出口连接至所述缸套水换热器的工质侧进口，所述缸套水换热器的工质侧出口经过所述低压级涡轮后连接至所述冷却器的工质侧进口；所述内燃机的缸套水经出水管后进入所述缸套水换热器的缸套水侧经过充分换热后经过回水管进入内燃机缸套；所述低压级涡轮与低压级压气机之间还设有联轴器。In order to achieve the above object, a basic structure of a two-stage turbocharger system proposed by the present invention includes an internal combustion engine, an intercooler, a high-pressure stage turbocharger, and a low-pressure stage turbocharger, and the high-pressure stage turbocharger. The high-pressure stage compressor is composed of a coaxially connected high-pressure stage compressor and a high-pressure stage turbine; the low-pressure stage turbocharger is composed of a low-pressure stage compressor and a low-pressure stage turbine; the high-pressure stage compressor is connected in series with the low-pressure stage compressor. The high pressure stage compressor is connected to the internal combustion engine through a charge air side of the intercooler, the low pressure stage turbine of the two stage boost system is driven by a waste heat recovery system, the waste heat recovery system comprising cooling in series a working fluid tank, a compressor, a cylinder and a water jacket heat exchanger, wherein an outlet of the compressor is connected to a working fluid side inlet of the cylinder water heat exchanger, and a working fluid side of the cylinder water heat exchanger The outlet is connected to the working medium side inlet of the cooler after passing through the low pressure stage turbine; the cylinder liner water of the internal combustion engine passes through the outlet pipe and enters the water side of the cylinder liner water heat exchanger after sufficient heat exchange After the return pipe Into the cylinder liner of the internal combustion engine; a coupling is also arranged between the low-pressure stage turbine and the low-pressure stage compressor.
本发明两级涡轮增压***根据实际可以对上述基本方案进一步优化，从而在改善内燃机低速扭矩性能的同时实现内燃机余热能在全工况范围内的高效回收利用。The two-stage turbocharging system of the present invention can further optimize the above basic scheme according to the actual situation, thereby realizing efficient recycling of the residual heat energy of the internal combustion engine in the whole working condition while improving the low-speed torque performance of the internal combustion engine.
本发明提出的另一种改进的技术方案是在上述基本方案的基础上将所述压缩机的出口连接至所述中冷器的二次流体侧的进口，所述中冷器二次流体侧的出口连接至所述缸套水换热器的工质侧进口，所述缸套水换热器的工质侧出口连接至所述低压级涡轮。Another improved technical solution proposed by the present invention is to connect the outlet of the compressor to the inlet of the secondary fluid side of the intercooler based on the above basic scheme, and the secondary fluid side of the intercooler The outlet is connected to the working side inlet of the liner water heat exchanger, and the working side outlet of the cylinder water heat exchanger is connected to the low pressure stage turbine.
本发明提出的两级涡轮增压***，无论是基本的技术方案还是改进的技术方案中，通过增加烟气换热器实现内燃机排气余热能量的利用，即所述缸套水换热器的工质侧出口与低压级涡轮之间还设有烟气换热器，所述内燃机的排气经所述高压级涡轮后连接至所述烟气换热器的烟气侧进口，所述烟气侧出口连接至大气环境或是连接至内燃机后处理***。The two-stage turbocharger system proposed by the present invention, in the basic technical solution or the improved technical solution, realizes the utilization of the exhaust heat energy of the internal combustion engine by adding a flue gas heat exchanger, that is, the water jacket heat exchanger of the cylinder liner a flue gas heat exchanger is further disposed between the working medium side outlet and the low pressure stage turbine, and the exhaust gas of the internal combustion engine is connected to the flue gas side inlet of the flue gas heat exchanger via the high pressure stage turbine, the smoke The gas side outlet is connected to the atmosphere or to the internal combustion engine aftertreatment system.
通过增加中间换热器实现低压级涡轮出口工质乏汽能量的回收，即所述缸套水换热器的工质侧出口与烟气换热器之间还设有中间换热器，工质经由所述低压级涡轮后依次连接至所述中间换热器的低压工质侧和冷却器，所述缸套水换热器的工质侧出口连接至所述中间换热器的高压工质侧进口，从而使得低压级涡轮出口的低压工质进入所述中间换热器内与所述缸套水换热器排出的高压工质换热后进入所述冷却器。The recovery of the spent steam energy of the low-pressure stage turbine outlet working medium is realized by adding an intermediate heat exchanger, that is, an intermediate heat exchanger is disposed between the working medium side outlet of the cylinder jacket water heat exchanger and the flue gas heat exchanger. The medium is connected to the low pressure working side of the intermediate heat exchanger and the cooler in turn via the low pressure stage turbine, and the working medium side outlet of the cylinder water heat exchanger is connected to the high pressure work of the intermediate heat exchanger The mass side inlet, so that the low pressure working medium of the low pressure stage turbine outlet enters the intermediate heat exchanger and exchanges with the high pressure working medium discharged from the cylinder jacket water heat exchanger to enter the cooler.
本发明提出的两级涡轮增压***的工作过程为：在内燃机高速工况下，联轴器断开连接，只采用高压级涡轮增压器实现进气增压，而低压级涡轮将回收的内燃机余热转化为有效功输出或发电或作为车辆的辅助动力；在内燃机低速工况下，联轴器连接，低压级涡轮增压器与高压级涡轮增压器同时工作实现进气增压。The working process of the two-stage turbocharging system proposed by the invention is: in the high-speed working condition of the internal combustion engine, the coupling is disconnected, only the high-pressure turbocharger is used to realize the intake supercharging, and the low-pressure stage turbine will be recycled. The residual heat of the internal combustion engine is converted into effective work output or power generation or as an auxiliary power of the vehicle; in the low speed condition of the internal combustion engine, the coupling is connected, and the low-pressure stage turbocharger and the high-pressure stage turbocharger work simultaneously to realize the intake supercharging.
本发明的有益效果是：The beneficial effects of the invention are:
本发明所述***集成了两级涡轮增压***与内燃机余热回收***，且在低压级涡轮与低压级压气机之间设有联轴器，通过余热回收***回收内燃机余热后的高温高压工质推动低压级涡轮旋转，内燃机低速工况时联轴器连接，实现与高压级涡轮增压器的串联式进气增压，内燃机高速工况时联轴器断开，通过低压级涡轮实现内燃机余热能转化为输出功。对于车辆来说，安装该***不仅可以改善涡轮增压内燃机低速扭矩性能，而且可以实现内燃机全工况的余热利用，具有显著的经济效益和应用前景。The system of the invention integrates a two-stage turbocharger system and an internal combustion engine waste heat recovery system, and a coupling is arranged between the low-pressure stage turbine and the low-pressure stage compressor, and the high-temperature high-pressure working medium after the residual heat of the internal combustion engine is recovered by the waste heat recovery system. Promote the rotation of the low-pressure stage turbine. When the internal combustion engine is running at low speed, the coupling is connected to realize the series-type intake supercharging with the high-pressure turbocharger. When the internal combustion engine is in high-speed working condition, the coupling is disconnected, and the residual heat of the internal combustion engine is realized by the low-pressure stage turbine. Can be converted into output work. For the vehicle, the installation of the system can not only improve the low-speed torque performance of the turbocharged internal combustion engine, but also realize the waste heat utilization of the full working condition of the internal combustion engine, which has significant economic benefits and application prospects.
附图说明DRAWINGS
图1是本发明两级涡轮增压***实施例1的结构示意图；1 is a schematic structural view of Embodiment 1 of a two-stage turbocharger system of the present invention;
图2是本发明两级涡轮增压***实施例2的结构示意图；2 is a schematic structural view of Embodiment 2 of a two-stage turbocharger system according to the present invention;
图3是本发明两级涡轮增压***实施例3的结构示意图；3 is a schematic structural view of Embodiment 3 of a two-stage turbocharger system according to the present invention;
图4是本发明两级涡轮增压***实施例4的结构示意图；4 is a schematic structural view of Embodiment 4 of a two-stage turbocharger system according to the present invention;
图5是本发明两级涡轮增压***实施例5的结构示意图；Figure 5 is a schematic structural view of Embodiment 5 of the two-stage turbocharger system of the present invention;
图6是本发明两级涡轮增压***实施例6的结构示意图；Figure 6 is a schematic structural view of Embodiment 6 of the two-stage turbocharger system of the present invention;
图中：In the picture:
细实线为内燃机空气进气路径，点线为中冷器二次流体侧路径，虚线为内燃机排气路径，点划线为内燃机缸套水封闭循环路径，粗实线为余热回收***动力循环工质路径；The thin solid line is the air intake path of the internal combustion engine, the dotted line is the secondary fluid side path of the intercooler, the dotted line is the exhaust path of the internal combustion engine, the dotted line is the closed loop path of the cylinder liner of the internal combustion engine, and the thick solid line is the power cycle of the waste heat recovery system. Working path
1-内燃机，2-中冷器，3-高压级压气机，4-高压级涡轮，5-低压级压气机，6-低压级涡轮，7-冷却器，8-工质罐，9-压缩机，10-缸套水换热器，11-联轴器，12-烟气换热器，13-中间换热器。1-Internal combustion engine, 2-intercooler, 3-high pressure stage compressor, 4-high pressure stage turbine, 5-low pressure stage compressor, 6-low pressure stage turbine, 7-cooler, 8-plast tank, 9-compression Machine, 10-cylinder jacket water heat exchanger, 11-coupling, 12-smoke heat exchanger, 13-intermediate heat exchanger.
具体实施方式detailed description
下面结合附图和具体实施例对本发明技术方案作进一步详细描述，所描述的具体实施例仅对本发明进行解释说明，并不用以限制本发明。The technical solutions of the present invention are further described in detail below with reference to the accompanying drawings and specific embodiments.
实施例1Example 1
如图1所示，本发明提出的一种两级涡轮增压***，其结构是：包括内燃机1、中冷器2、高压级涡轮增压器和低压级涡轮增压器，所述高压级涡轮增压器采用同轴相连的高压级压气机3和高压级涡轮4构成；所述低压级涡轮增压器由低压级压气机5和低压级涡轮6构成；所述高压级压气机3与所述低压级压气机5串联，所述高压级压气机3通过所述中冷器2的增压空气侧连接至所述内燃机1，所述两级增压***的低压级涡轮6由余热回收***驱动，所述余热回收***包括依次串联的冷却器7、工质罐8、压缩机9和缸套水换热器10，所述压缩机9的出口连接至所述缸套水换热器10的工质侧进口，所述缸套水换热器10的工质侧出口经过所述低压级涡轮6后连接至所述冷却器7的工质侧进口；所述内燃机1的缸套水经出水管后进入所述缸套水换热器10的缸套水侧经过充分换热后经过回水管进入内燃机1缸套，形成封闭回路；所述低压级涡轮6与低压级压气机5之间还设有联轴器11。As shown in FIG. 1 , a two-stage turbocharger system according to the present invention is configured to include an internal combustion engine 1, an intercooler 2, a high-pressure stage turbocharger, and a low-pressure stage turbocharger, the high-pressure stage. The turbocharger is constituted by a coaxially connected high-pressure stage compressor 3 and a high-pressure stage turbine 4; the low-pressure stage turbocharger is composed of a low-pressure stage compressor 5 and a low-pressure stage turbine 6; the high-pressure stage compressor 3 and The low-pressure stage compressor 5 is connected in series, and the high-pressure stage compressor 3 is connected to the internal combustion engine 1 through a charge air side of the intercooler 2, and the low-pressure stage turbine 6 of the two-stage supercharging system is recovered from waste heat. System driven, the waste heat recovery system includes a cooler 7 in series, a working tank 8, a compressor 9 and a jacket water heat exchanger 10, and an outlet of the compressor 9 is connected to the cylinder water heat exchanger a working medium side inlet of the cylinder water heat exchanger 10, the working medium side outlet of the cylinder water heat exchanger 10 is connected to the working medium side inlet of the cooler 7 through the low pressure stage turbine 6; the cylinder liner water of the internal combustion engine 1 After passing through the water outlet pipe, the water side of the cylinder liner water entering the cylinder jacket water heat exchanger 10 passes through sufficient heat exchange. The return pipe enters the cylinder liner of the internal combustion engine to form a closed circuit; and a coupling 11 is further disposed between the low-pressure stage turbine 6 and the low-pressure stage compressor 5.
上述实施例1的两级涡轮增压***的工作过程为：工质罐8中工质经由压缩机9压缩增压后在缸套水换热器10中吸收内燃机缸套水余热形成高温高压工质气体，随后进入低压级涡轮6中膨胀，推动低压级涡轮6旋转。内燃机缸套水经由缸套水换热器10换热后进入内燃机1，形成封闭回路。在内燃机低速工况下，联轴器11连接，低压级涡轮带动低压级压气机旋转，实现进气的第一级增压，增压后的空气随即进入高压级压气机，实现进气的第二级增压。在内燃机高速工况下，联轴器11断开连接，只采用高压级涡轮增压器实现进气增压，而低压级涡轮6将回收的内燃机余热转化为有效功输出或发电或作为车辆的辅助动力。The working process of the two-stage turbocharger system of the first embodiment is as follows: the working medium in the working fluid tank 8 is compressed and pressurized by the compressor 9, and then the water in the cylinder water heat exchanger 10 is absorbed in the cylinder water heat exchanger 10 to form a high temperature and high pressure work. The mass gas then expands into the low pressure stage turbine 6 to propel the low pressure stage turbine 6 to rotate. The cylinder liner water of the internal combustion engine enters the internal combustion engine 1 through heat exchange between the jacket water heat exchanger 10 to form a closed loop. In the low-speed operating condition of the internal combustion engine, the coupling 11 is connected, and the low-pressure stage turbine drives the low-pressure stage compressor to rotate, so that the first-stage supercharging of the intake air is achieved, and the supercharged air immediately enters the high-pressure stage compressor to realize the intake air. Secondary pressurization. In the high-speed operating condition of the internal combustion engine, the coupling 11 is disconnected, and only the high-pressure stage turbocharger is used to achieve intake supercharging, and the low-pressure stage turbine 6 converts the recovered residual heat of the internal combustion engine into an effective work output or power generation or as a vehicle. Auxiliary power.
本实施例1的特点是：内燃机低速工况下通过完全回收利用缸套水余热而由高温高压 工质气体驱动低压级涡轮，联合高压级涡轮增压器改善涡轮增压器低速扭矩性能。内燃机高速工况下发挥余热回收***功能，将内燃机余热转化为有效功输出或发电或作为车辆的辅助动力。所述***在内燃机全工况下均能产生净收益。图1仅为本发明的基本构成，当实际应用时，需要增加阀门、管道、旁路***及控制***等，这些属于本领域的公知常识，在此不再赘述。The feature of the first embodiment is that the low-pressure stage turbine is driven by the high-temperature high-pressure working gas by completely recovering the residual heat of the liner water under the low-speed operating condition, and the high-speed turbocharger is combined to improve the low-speed torque performance of the turbocharger. Under the high-speed operating conditions of the internal combustion engine, the function of the waste heat recovery system is utilized to convert the residual heat of the internal combustion engine into an effective work output or power generation or as an auxiliary power of the vehicle. The system can generate net revenue under all operating conditions of the internal combustion engine. 1 is only a basic configuration of the present invention. When it is actually applied, it is necessary to add a valve, a pipe, a bypass system, a control system, etc., which are common knowledge in the art, and will not be described herein.
实施例2Example 2
为了进一步拓展内燃机高速工况下余热回收***的性能，如图2所示，该实施例2的两级涡轮增压***是在实施例1的基础上增加了烟气换热器12，以充分回收高压级涡轮4出口内燃机排气能量，即：所述缸套水换热器10的工质侧出口与低压级涡轮6之间还设有烟气换热器12，所述内燃机1的排气经所述高压级涡轮4后连接至所述烟气换热器12的烟气侧进口，所述烟气侧出口连接至大气环境或是连接至内燃机后处理***，从而使涡后排气与工质换热。In order to further expand the performance of the waste heat recovery system under high-speed operating conditions of the internal combustion engine, as shown in FIG. 2, the two-stage turbocharger system of the second embodiment adds the flue gas heat exchanger 12 to the first embodiment to fully The exhaust gas energy of the high-pressure stage turbine 4 outlet engine is recovered, that is, a flue gas heat exchanger 12 is further disposed between the working medium side outlet of the cylinder jacket water heat exchanger 10 and the low-pressure stage turbine 6, and the exhaust gas of the internal combustion engine 1 After passing through the high-pressure stage turbine 4, the gas is connected to the flue gas side inlet of the flue gas heat exchanger 12, and the flue gas side outlet is connected to the atmospheric environment or connected to the internal combustion engine after-treatment system, so that the vortex is exhausted Heat exchange with the working fluid.
上述实施例2***的工作过程与实施例1基本相同，不同的区别仅为：从缸套水换热器10中吸收缸套水能量后的工质进入烟气换热器12回收内燃机排气余热能量，随后再进入低压级涡轮6膨胀做功。The working process of the system of the above embodiment 2 is basically the same as that of the first embodiment. The only difference is that the working fluid after absorbing the water energy of the cylinder liner water from the cylinder water heat exchanger 10 enters the flue gas heat exchanger 12 to recover the exhaust of the internal combustion engine. The residual heat energy is then re-expanded into the low-pressure stage turbine 6 to perform work.
实施例2的特点：该***在高速工况下能充分利用排气能量，在改善涡轮增压低速扭矩性能的基础上，进一步拓展了余热回收***在高速工况下的应用，实现内燃机余热能的高效利用，提高内燃机的动力性及经济性，技术适用性广。The characteristics of the second embodiment: the system can fully utilize the exhaust energy under high-speed conditions, and further improve the application of the waste heat recovery system under high-speed conditions on the basis of improving the turbocharged low-speed torque performance, and realize the residual heat energy of the internal combustion engine. The efficient use of the internal combustion engine improves the power and economy of the internal combustion engine, and the technical applicability is wide.
实施例3Example 3
为了进一步回收膨胀做功后工质乏汽能量，如图3所示，实施例3的一种两级涡轮增压***是在实施例2的基础上增加了中间换热器13，即：所述缸套水换热器10的工质侧出口与烟气换热器12之间还设有中间换热器13，工质经由所述低压级涡轮6后依次连接至所述中间换热器13的低压工质侧和冷却器7，所述缸套水换热器10的工质侧出口连接至所述中间换热器13的高压工质侧进口，从而使得低压级涡轮6出口的低压工质进入所述中间换热器13内与所述缸套水换热器10排出的高压工质换热后进入所述冷却器7，实现膨胀做功后工质乏汽能量的回收。In order to further recover the exhaust gas energy of the working fluid after the expansion work, as shown in FIG. 3, a two-stage turbocharger system of Embodiment 3 adds the intermediate heat exchanger 13 to the second embodiment, namely: An intermediate heat exchanger 13 is further disposed between the working fluid side outlet of the cylinder water heat exchanger 10 and the flue gas heat exchanger 12, and the working medium is sequentially connected to the intermediate heat exchanger 13 via the low pressure stage turbine 6 a low pressure working fluid side and a cooler 7, the working medium side outlet of the cylinder water heat exchanger 10 is connected to the high pressure working side inlet of the intermediate heat exchanger 13, so that the low pressure working of the low pressure stage turbine 6 outlet The medium enters the intermediate heat exchanger 13 and exchanges heat with the high-pressure working fluid discharged from the cylinder water heat exchanger 10 to enter the cooler 7 to realize recovery of the spent steam energy after the expansion work.
实施例3***的工作过程与实施例2基本相同，不同仅为：从缸套水换热器10中吸收缸套水能量后的高压工质先进入中间换热器13再进入烟气换热器12，从低压级涡轮6膨胀做功后的工质进入中间换热器13后再进入冷却器7。The working process of the system of Embodiment 3 is basically the same as that of Embodiment 2, the difference is only: the high-pressure working medium after absorbing the water energy of the cylinder liner water from the water-cylinder water heat exchanger 10 first enters the intermediate heat exchanger 13 and then enters the heat exchange of the flue gas. The compressor 12 expands from the low-pressure stage turbine 6 and enters the intermediate heat exchanger 13 and then enters the cooler 7.
本实施例的特点是：根据余热回收***性能优化常用方法，通过增加中间换热器以提升余热回收***的输出功，通过回收涡轮出口工质的乏汽能量实现对能量的进一步利用。本实施例特别适用于通过增加中间换热器后余热回收***输出功有显著提升的工质场合。The characteristic of the embodiment is that: according to the common method for optimizing the performance of the waste heat recovery system, the intermediate heat exchanger is added to increase the output work of the waste heat recovery system, and the further utilization of energy is realized by recovering the spent steam energy of the turbine outlet working medium. This embodiment is particularly suitable for working conditions where the output of the residual heat recovery system is significantly improved by adding an intermediate heat exchanger.
实施例4Example 4
图4示出了实现本发明两级涡轮增压***的另一种实施方案，在实施例1技术方案的 基础上将余热回收***与中冷器2进一步集成，从而降低原中冷器2因采用空冷或水冷而增加的内燃机功耗。其具体结构是：包括内燃机1、中冷器2、高压级涡轮增压器和低压级涡轮增压器，所述高压级涡轮增压器采用同轴相连的高压级压气机3和高压级涡轮4构成；所述低压级涡轮增压器由低压级压气机5和低压级涡轮6构成；所述高压级压气机3与所述低压级压气机5串联，所述高压级压气机3通过所述中冷器2的增压空气侧连接至所述内燃机1，所述两级增压***的低压级涡轮6由余热回收***驱动，所述余热回收***包括依次串联的冷却器7、工质罐8和压缩机9，所述压缩机9的出口连接至所述中冷器2的二次流体侧的进口，所述中冷器2二次流体侧的出口连接至所述缸套水换热器10的工质侧进口，所述缸套水换热器10的工质侧出口经过所述低压级涡轮6后连接至所述冷却器7的工质侧进口；所述内燃机1的缸套水经出水管后进入所述缸套水换热器10的缸套水侧经过充分换热后经过回水管进入内燃机1缸套；所述低压级涡轮6与低压级压气机5之间还设有联轴器11。FIG. 4 shows another embodiment of implementing the two-stage turbocharger system of the present invention. Based on the technical solution of the first embodiment, the waste heat recovery system is further integrated with the intercooler 2, thereby reducing the original intercooler 2 Increased internal combustion engine power consumption by air cooling or water cooling. The specific structure is: including an internal combustion engine 1, an intercooler 2, a high-pressure stage turbocharger and a low-pressure stage turbocharger, the high-pressure stage turbocharger adopts a coaxial high-pressure stage compressor 3 and a high-pressure stage turbine. 4; the low-pressure stage turbocharger is composed of a low-pressure stage compressor 5 and a low-pressure stage turbine 6; the high-pressure stage compressor 3 is connected in series with the low-pressure stage compressor 5, and the high-pressure stage compressor 3 passes through The charge air side of the intercooler 2 is connected to the internal combustion engine 1, and the low-pressure stage turbine 6 of the two-stage supercharging system is driven by a waste heat recovery system comprising a cooler 7 in series, working medium a tank 8 and a compressor 9, an outlet of the compressor 9 is connected to an inlet of a secondary fluid side of the intercooler 2, and an outlet of the secondary fluid side of the intercooler 2 is connected to the cylinder liner for water exchange a working medium side inlet of the heat exchanger 10, the working medium side outlet of the cylinder water heat exchanger 10 is connected to the working medium side inlet of the cooler 7 through the low pressure stage turbine 6; the cylinder of the internal combustion engine 1 After the water passes through the water outlet pipe, the water side of the cylinder liner water heat exchanger 10 is fully replaced. After the return pipe into the internal combustion engine, the cylinder liner 1; 6 between the low-pressure stage turbine and the low-pressure stage compressor 5 is also provided with the coupling 11.
实施例4***的工作过程与实施例1基本相同，不同仅为：经压缩机9压缩增压后的高压工质首先进入中冷器2吸收增压后高温空气能量后再进入缸套水换热器10，实现两级涡轮增压***与余热回收***的进一步集成。The working process of the system of Embodiment 4 is basically the same as that of Embodiment 1, except that the high-pressure working medium compressed and pressurized by the compressor 9 first enters the intercooler 2, absorbs the high-temperature air energy after the supercharging, and then enters the cylinder liner water exchange. The heater 10 implements further integration of the two-stage turbocharger system with the waste heat recovery system.
本实施例4的特点是：内燃机增压***中通常会安装中冷器以降低增压后的高温空气温度，提高进气量，获得更大的输出功率。常见的中冷器分为风冷式和水冷式，风冷式风扇耗功、水冷式缸套水泵耗功均给内燃机增加了功率损失。采用实施例4所述***后，中冷器中增压空气直接由余热回收***工质冷却，降低了内燃机功耗。The feature of the fourth embodiment is that an intercooler is usually installed in the engine boosting system to reduce the temperature of the high temperature air after boosting, increase the intake air amount, and obtain a larger output power. Common intercoolers are classified into air-cooled and water-cooled. Air-cooled fan power consumption and water-cooled cylinder liner pump power consumption add power loss to the internal combustion engine. After adopting the system described in Embodiment 4, the charge air in the intercooler is directly cooled by the waste heat recovery system working medium, which reduces the power consumption of the internal combustion engine.
实施例5Example 5
如图5所示，在上述实施例4的基础上，所述缸套水换热器10的工质侧出口与低压级涡轮6之间还设有烟气换热器12，所述内燃机1的排气经所述高压级涡轮4后连接至所述烟气换热器12的烟气侧进口，所述烟气侧出口连接至大气环境或是连接至内燃机后处理***。实施例5的工作过程和特点综合了上述实施例2和实施例4，在此不再赘述。As shown in FIG. 5, on the basis of the above-mentioned embodiment 4, a flue gas heat exchanger 12 is further disposed between the working medium side outlet of the cylinder water heat exchanger 10 and the low pressure stage turbine 6, and the internal combustion engine 1 The exhaust gas is connected to the flue gas side inlet of the flue gas heat exchanger 12 via the high pressure stage turbine 4, and the flue gas side outlet is connected to the atmospheric environment or to the internal combustion engine aftertreatment system. The working process and features of Embodiment 5 are combined with Embodiment 2 and Embodiment 4 described above, and are not described herein again.
实施例6Example 6
如图6所示，在上述实施例5的基础上，所述缸套水换热器10的工质侧出口与烟气换热器12之间还设有中间换热器13，工质经由所述低压级涡轮6后依次连接至所述中间换热器13的低压工质侧和冷却器7，所述缸套水换热器10的工质侧出口连接至所述中间换热器13的高压工质侧进口，从而使得低压级涡轮6出口的低压工质进入所述中间换热器13内与所述缸套水换热器10排出的高压工质换热后进入所述冷却器7。实施例6的工作过程和特点综合了上述实施例3和实施例4，在此不再赘述。As shown in FIG. 6, on the basis of the above-mentioned embodiment 5, an intermediate heat exchanger 13 is further disposed between the working medium side outlet of the cylinder water heat exchanger 10 and the flue gas heat exchanger 12, and the working medium is The low pressure stage turbine 6 is sequentially connected to the low pressure working side of the intermediate heat exchanger 13 and the cooler 7, and the working medium side outlet of the cylinder water heat exchanger 10 is connected to the intermediate heat exchanger 13 The high pressure working medium side inlet, so that the low pressure working medium of the outlet of the low pressure stage turbine 6 enters the intermediate heat exchanger 13 and exchanges with the high pressure working medium discharged from the cylinder water heat exchanger 10 to enter the cooler. 7. The working process and features of Embodiment 6 are combined with Embodiment 3 and Embodiment 4 described above, and are not described herein again.
本发明中，所述余热回收***的工质是水、CO 2和基于CO 2的非共沸混合工质中的任何一种。 In the present invention, the working fluid of the waste heat recovery system is any one of water, CO 2 and CO 2 -based non-azeotropic mixed working fluid.
综上，本发明***通过余热回收***驱动低压级涡轮6，低压级涡轮6与低压级压气机 5之间设有联轴器11。内燃机1低速工况下，联轴器11连接，通过回收缸套水余热为低压级涡轮6提供动力，采用两级涡轮增压实现进气增压；内燃机1高速工况下，联轴器11断开，仅由高压级涡轮4增压实现进气增压，而通过低压级涡轮6将缸套水、排气、增压空气、工质乏汽能量转化为有效功输出或发电或作为车辆的辅助动力。该***不仅可解决涡轮增压内燃机低速扭矩小的问题，改善内燃机低速动力性，而且取消原有散热器风扇，减少能量损失，用余热回收***进行车辆热管理，可实现内燃机全工况下余热能量的有效回收利用，改善内燃机燃油经济性。In summary, the system of the present invention drives the low pressure stage turbine 6 through a waste heat recovery system, and a coupling 11 is provided between the low pressure stage turbine 6 and the low pressure stage compressor 5. In the low-speed working condition of the internal combustion engine 1, the coupling 11 is connected, and the low-pressure stage turbine 6 is powered by the residual heat of the cylinder liner, and the intake boosting is realized by the two-stage turbocharging; the coupling 11 is in the high-speed working condition of the internal combustion engine 1 Disconnected, the intake pressure is only supercharged by the high-pressure stage turbine 4, and the cylinder jacket water, exhaust gas, charge air, and working fluid consumption energy are converted into effective work output or power generation or as a vehicle through the low-pressure stage turbine 6 Auxiliary power. The system can not only solve the problem of low speed torque of turbocharged internal combustion engine, improve the low speed power of internal combustion engine, but also eliminate the original radiator fan, reduce energy loss, and use the waste heat recovery system for vehicle thermal management, which can realize the residual heat of the internal combustion engine under full working condition. Effective recycling of energy to improve fuel economy of internal combustion engines.
尽管上面结合附图对本发明进行了描述，但是本发明并不局限于上述的具体实施方式，上述的具体实施方式仅仅是示意性的，而不是限制性的，本领域的普通技术人员在本发明的启示下，在不脱离本发明宗旨的情况下，还可以做出很多变形，这些均属于本发明的保护之内，如因余热回收***采用工质的种类不同，压缩机9与冷却器7可能相应变形为工质泵与冷凝器。While the invention has been described hereinabove in connection with the drawings, the invention is not limited to the specific embodiments described above, and the specific embodiments described above are merely illustrative and not restrictive. In the light of the present invention, many modifications can be made without departing from the spirit of the invention, and these are within the protection of the present invention. For example, the compressor 9 and the cooler 7 are different depending on the type of working medium used in the waste heat recovery system. It may be deformed into a working fluid pump and a condenser.

Claims (7)

  1. 一种两级涡轮增压***，包括内燃机(1)、中冷器(2)、高压级涡轮增压器和低压级涡轮增压器，所述高压级涡轮增压器采用同轴相连的高压级压气机(3)和高压级涡轮(4)构成；所述低压级涡轮增压器由低压级压气机(5)和低压级涡轮(6)构成；所述高压级压气机(3)与所述低压级压气机(5)串联，所述高压级压气机(3)通过所述中冷器(2)的增压空气侧连接至所述内燃机(1)，其特征在于：A two-stage turbocharging system includes an internal combustion engine (1), an intercooler (2), a high-pressure stage turbocharger, and a low-pressure stage turbocharger, the high-pressure stage turbocharger adopting a coaxially connected high voltage a stage compressor (3) and a high pressure stage turbine (4); the low pressure stage turbocharger is composed of a low pressure stage compressor (5) and a low pressure stage turbine (6); the high pressure stage compressor (3) and The low-pressure stage compressor (5) is connected in series, and the high-pressure stage compressor (3) is connected to the internal combustion engine (1) through a charge air side of the intercooler (2), characterized in that:
    所述两级增压***的低压级涡轮(6)由余热回收***驱动，所述余热回收***包括依次串联的冷却器(7)、工质罐(8)、压缩机(9)和缸套水换热器(10)，所述压缩机(9)的出口连接至所述缸套水换热器(10)的工质侧进口，所述缸套水换热器(10)的工质侧出口经过所述低压级涡轮(6)后连接至所述冷却器(7)的工质侧进口；所述内燃机(1)的缸套水经出水管后进入所述缸套水换热器(10)的缸套水侧经过充分换热后经过回水管进入内燃机(1)缸套；所述低压级涡轮(6)与低压级压气机(5)之间还设有联轴器(11)。The low-pressure stage turbine (6) of the two-stage supercharging system is driven by a waste heat recovery system comprising a cooler (7), a working medium tank (8), a compressor (9) and a cylinder liner connected in series. a water heat exchanger (10), an outlet of the compressor (9) is connected to a working medium side inlet of the cylinder water heat exchanger (10), and a working fluid of the cylinder water heat exchanger (10) a side outlet is connected to the working medium side inlet of the cooler (7) after passing through the low pressure stage turbine (6); the cylinder liner water of the internal combustion engine (1) enters the cylinder liner water heat exchanger through the outlet pipe The water side of the cylinder liner of (10) passes through the return water pipe and enters the cylinder liner of the internal combustion engine (1); there is also a coupling between the low-pressure stage turbine (6) and the low-pressure stage compressor (5) (11) ).
  2. 根据权利要求1所述两级涡轮增压***，其特征在于：所述缸套水换热器(10)的工质侧出口与低压级涡轮(6)之间还设有烟气换热器(12)，所述内燃机(1)的排气经所述高压级涡轮(4)后连接至所述烟气换热器(12)的烟气侧进口，所述烟气侧出口连接至大气环境或是连接至内燃机后处理***。The two-stage turbocharging system according to claim 1, characterized in that: a flue gas heat exchanger is further arranged between the working medium side outlet of the cylinder jacket water heat exchanger (10) and the low pressure stage turbine (6) (12), the exhaust gas of the internal combustion engine (1) is connected to a flue gas side inlet of the flue gas heat exchanger (12) via the high pressure stage turbine (4), and the flue gas side outlet is connected to the atmosphere The environment is either connected to the internal combustion engine aftertreatment system.
  3. 根据权利要求2所述两级涡轮增压***，其特征在于：所述缸套水换热器(10)的工质侧出口与烟气换热器(12)之间还设有中间换热器(13)，工质经由所述低压级涡轮(6)后依次连接至所述中间换热器(13)的低压工质侧和冷却器(7)，所述缸套水换热器(10)的工质侧出口连接至所述中间换热器(13)的高压工质侧进口，从而使得低压级涡轮(6)出口的低压工质进入所述中间换热器(13)内与所述缸套水换热器(10)排出的高压工质换热后进入所述冷却器(7)。The two-stage turbocharging system according to claim 2, characterized in that the intermediate heat exchange between the working medium side outlet of the cylinder jacket water heat exchanger (10) and the flue gas heat exchanger (12) is further provided. (13), the working medium is sequentially connected to the low-pressure working side of the intermediate heat exchanger (13) and the cooler (7) via the low-pressure stage turbine (6), the cylinder-sea water heat exchanger ( 10) The working medium side outlet is connected to the high pressure working side inlet of the intermediate heat exchanger (13), so that the low pressure working medium of the low pressure stage turbine (6) outlet enters the intermediate heat exchanger (13) The high-pressure working fluid discharged from the liner water heat exchanger (10) enters the cooler (7) after heat exchange.
  4. 一种两级涡轮增压***，包括内燃机(1)、中冷器(2)、高压级涡轮增压器和低压级涡轮增压器，所述高压级涡轮增压器采用同轴相连的高压级压气机(3)和高压级涡轮(4)构成；所述低压级涡轮增压器由低压级压气机(5)和低压级涡轮(6)构成；所述高压级压气机(3)与所述低压级压气机(5)串联，所述高压级压气机(3)通过所述中冷器(2)的 增压空气侧连接至所述内燃机(1)，其特征在于：A two-stage turbocharging system includes an internal combustion engine (1), an intercooler (2), a high-pressure stage turbocharger, and a low-pressure stage turbocharger, the high-pressure stage turbocharger adopting a coaxially connected high voltage a stage compressor (3) and a high pressure stage turbine (4); the low pressure stage turbocharger is composed of a low pressure stage compressor (5) and a low pressure stage turbine (6); the high pressure stage compressor (3) and The low-pressure stage compressor (5) is connected in series, and the high-pressure stage compressor (3) is connected to the internal combustion engine (1) through a charge air side of the intercooler (2), characterized in that:
    所述两级增压***的低压级涡轮(6)由余热回收***驱动，所述余热回收***包括依次串联的冷却器(7)、工质罐(8)和压缩机(9)，所述压缩机(9)的出口连接至所述中冷器(2)的二次流体侧的进口，所述中冷器(2)二次流体侧的出口连接至所述缸套水换热器(10)的工质侧进口，所述缸套水换热器(10)的工质侧出口经过所述低压级涡轮(6)后连接至所述冷却器(7)的工质侧进口；所述内燃机(1)的缸套水经出水管后进入所述缸套水换热器(10)的缸套水侧经过充分换热后经过回水管进入内燃机(1)缸套；所述低压级涡轮(6)与低压级压气机(5)之间还设有联轴器(11)。The low-pressure stage turbine (6) of the two-stage supercharging system is driven by a waste heat recovery system comprising a cooler (7), a working medium tank (8) and a compressor (9) connected in series, An outlet of the compressor (9) is connected to an inlet of a secondary fluid side of the intercooler (2), and an outlet of the secondary fluid side of the intercooler (2) is connected to the cylinder jacket water heat exchanger ( 10) a working medium side inlet, the working medium side outlet of the cylinder jacket water heat exchanger (10) is connected to the working medium side inlet of the cooler (7) after passing through the low pressure stage turbine (6); The cylinder liner water of the internal combustion engine (1) enters the cylinder jacket water side of the cylinder jacket water heat exchanger (10) through the outlet pipe and passes through the return water pipe to enter the internal combustion engine (1) cylinder liner; the low pressure stage A coupling (11) is also provided between the turbine (6) and the low pressure stage compressor (5).
  5. 根据权利要求4所述两级涡轮增压***，其特征在于：所述缸套水换热器(10)的工质侧出口与低压级涡轮(6)之间还设有烟气换热器(12)，所述内燃机(1)的排气经所述高压级涡轮(4)后连接至所述烟气换热器(12)的烟气侧进口，所述烟气侧出口连接至大气环境或是连接至内燃机后处理***。A two-stage turbocharging system according to claim 4, characterized in that a flue gas heat exchanger is further arranged between the working medium side outlet of the cylinder jacket water heat exchanger (10) and the low pressure stage turbine (6) (12), the exhaust gas of the internal combustion engine (1) is connected to a flue gas side inlet of the flue gas heat exchanger (12) via the high pressure stage turbine (4), and the flue gas side outlet is connected to the atmosphere The environment is either connected to the internal combustion engine aftertreatment system.
  6. 根据权利要求5所述两级涡轮增压***，其特征在于：所述缸套水换热器(10)的工质侧出口与烟气换热器(12)之间还设有中间换热器(13)，工质经由所述低压级涡轮(6)后依次连接至所述中间换热器(13)的低压工质侧和冷却器(7)，所述缸套水换热器(10)的工质侧出口连接至所述中间换热器(13)的高压工质侧进口，从而使得低压级涡轮(6)出口的低压工质进入所述中间换热器(13)内与所述缸套水换热器(10)排出的高压工质换热后进入所述冷却器(7)。The two-stage turbocharging system according to claim 5, characterized in that the intermediate heat exchange between the working medium side outlet of the cylinder jacket water heat exchanger (10) and the flue gas heat exchanger (12) is further provided. (13), the working medium is sequentially connected to the low-pressure working side of the intermediate heat exchanger (13) and the cooler (7) via the low-pressure stage turbine (6), the cylinder-sea water heat exchanger ( 10) The working medium side outlet is connected to the high pressure working side inlet of the intermediate heat exchanger (13), so that the low pressure working medium of the low pressure stage turbine (6) outlet enters the intermediate heat exchanger (13) The high-pressure working fluid discharged from the liner water heat exchanger (10) enters the cooler (7) after heat exchange.
  7. 根据权利要求1至6任一所述两级涡轮增压***，其特征在于：所述余热回收***的工质是水、CO 2和基于CO 2的非共沸混合工质中的任何一种。 The two-stage turbocharging system according to any one of claims 1 to 6, wherein the working fluid of the waste heat recovery system is any one of water, CO 2 and CO 2 -based non-azeotropic mixed working fluid. .
PCT/CN2018/091995 2018-04-03 2018-06-20 Two-stage turbocharging system WO2019192078A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201810291852.9 2018-04-03
CN201810291852.9A CN108691639A (en) 2018-04-03 2018-04-03 A kind of two turbocharging systems

Publications (1)

Publication Number Publication Date
WO2019192078A1 true WO2019192078A1 (en) 2019-10-10

Family

ID=63844861

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2018/091995 WO2019192078A1 (en) 2018-04-03 2018-06-20 Two-stage turbocharging system

Country Status (2)

Country Link
CN (1) CN108691639A (en)
WO (1) WO2019192078A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110529283A (en) * 2019-08-21 2019-12-03 中国北方车辆研究所 A kind of cooling coupled system with cogeneration of tank armored vehicle engine
CN110985230B (en) * 2019-12-16 2021-03-16 西安交通大学 Automobile waste heat recycling system and operation method thereof

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102182583A (en) * 2011-04-13 2011-09-14 北京理工大学 Combined-type residual heat recovery system suitable for internal combustion engine
JP2012007500A (en) * 2010-06-23 2012-01-12 Hino Motors Ltd Exhaust heat recovery device of internal combustion engine
CN104265502A (en) * 2014-07-25 2015-01-07 天津大学 Combined-type diesel engine waste heat energy recycling system
CN104632357A (en) * 2014-12-30 2015-05-20 清华大学 Two-stage supercharging system of internal combustion engine

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102230418B (en) * 2011-06-17 2012-08-08 北京理工大学 Electricity-auxiliary two-stage supercharging system capable of reusing exhaust gas
CN102748124A (en) * 2012-07-26 2012-10-24 湖南大学 Device for realizing air inflow pressurization by utilizing waste heat of exhaust gas of internal-combustion engine
CN103726949B (en) * 2013-12-27 2015-06-24 天津大学 Double-pressure double-loop multistage-expansion internal combustion engine waste heat recovery system
CN103670558B (en) * 2013-12-27 2015-09-02 天津大学 The afterheat of IC engine reclaiming system of two pressure multi-stage expansion reheating
DE102016200566A1 (en) * 2016-01-18 2017-07-20 Mahle International Gmbh Engine system

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012007500A (en) * 2010-06-23 2012-01-12 Hino Motors Ltd Exhaust heat recovery device of internal combustion engine
CN102182583A (en) * 2011-04-13 2011-09-14 北京理工大学 Combined-type residual heat recovery system suitable for internal combustion engine
CN104265502A (en) * 2014-07-25 2015-01-07 天津大学 Combined-type diesel engine waste heat energy recycling system
CN104632357A (en) * 2014-12-30 2015-05-20 清华大学 Two-stage supercharging system of internal combustion engine

Also Published As

Publication number Publication date
CN108691639A (en) 2018-10-23

Similar Documents

Publication Publication Date Title
CN104265502A (en) Combined-type diesel engine waste heat energy recycling system
CN108730069B (en) Miniaturized integrated system for recycling waste heat of internal combustion engine and control method thereof
CN102840026A (en) System for recycling waste heat energy of exhaust gas of internal combustion engine by using air circulation
CN103615309A (en) All-work-condition adjustable two-stage pressurizing system of internal combustion engine
JP2001132442A (en) Engine provided with energy recovering device
CN102748124A (en) Device for realizing air inflow pressurization by utilizing waste heat of exhaust gas of internal-combustion engine
WO2019192078A1 (en) Two-stage turbocharging system
CN101328828A (en) Internal combustion engine turbocharging system
CN113202643B (en) System with energy recovery device and control method
CN111075601A (en) Organic Rankine cycle waste heat recovery device for vehicle engine
CN109931184B (en) Diesel engine waste heat source recovery system based on carbon dioxide Brayton cycle
CN214304016U (en) Two-stage waste heat recovery system of diesel engine
CN109339938A (en) Three condition two-stage consecutive pressurization system and its control method
CN111734549A (en) Circulating system and method for waste heat recovery of EGR diesel engine
CN204877711U (en) Adopt a closed boulez endless automobile exhaust waste heat power generation facility
CN108716435A (en) A kind of pressurization system of internal combustion engine of integrated waste heat recovery
CN110107384A (en) A kind of energy recovery utilizing system being classified separation output based on low speed machine exhaust energy
CN102889147A (en) High-efficiency and low-emission novel composite thermodynamic cycle control method for engine
CN113482806B (en) Two-stage supercharged engine EGR double-circulation cooling system and automobile
CN109372628A (en) A kind of electronic pressurization realization Miller cycle diesel engine system
CN113202620A (en) Turbine composite system with multistage energy utilization and control method
CN210033657U (en) Diesel engine waste heat source recovery system based on carbon dioxide Brayton cycle
KR20130106495A (en) Turbo compound system with improved structure
CN209293909U (en) A kind of electronic pressurization realization Miller cycle diesel engine system
CN108644021B (en) Multi-stage combined recovery control method for exhaust energy of vehicle-mounted engine

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18913621

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

32PN Ep: public notification in the ep bulletin as address of the adressee cannot be established

Free format text: NOTING OF LOSS OF RIGHTS PURSUANT TO RULE 112(1) EPC (EPO FORM 1205A DATED 25/01/2021)

122 Ep: pct application non-entry in european phase

Ref document number: 18913621

Country of ref document: EP

Kind code of ref document: A1