WO2019153498A1 - 大功率v型多缸柴油机系统 - Google Patents

大功率v型多缸柴油机系统 Download PDF

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Publication number
WO2019153498A1
WO2019153498A1 PCT/CN2018/083194 CN2018083194W WO2019153498A1 WO 2019153498 A1 WO2019153498 A1 WO 2019153498A1 CN 2018083194 W CN2018083194 W CN 2018083194W WO 2019153498 A1 WO2019153498 A1 WO 2019153498A1
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Prior art keywords
oil
cylinder
diesel engine
type multi
temperature water
Prior art date
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PCT/CN2018/083194
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English (en)
French (fr)
Inventor
黄第云
黄永仲
沈捷
吴可
覃文
李伟
陈悦
谢夏琳
Original Assignee
广西玉柴机器股份有限公司
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Publication of WO2019153498A1 publication Critical patent/WO2019153498A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M5/00—Heating, cooling, or controlling temperature of lubricant; Lubrication means facilitating engine starting
    • F01M5/002—Cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/04—Arrangements of liquid pipes or hoses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/02—Arrangements for cooling cylinders or cylinder heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
    • F01P7/165—Controlling of coolant flow the coolant being liquid by thermostatic control characterised by systems with two or more loops
    • 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
    • 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
    • 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
    • F02B37/001—Engines characterised by provision of pumps driven at least for part of the time by exhaust using exhaust drives arranged in parallel
    • 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
    • F02B37/004—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust drives arranged in series
    • 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
    • F02B37/007—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in parallel, e.g. at least one pump supplying alternatively
    • 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
    • F02B37/013—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in series
    • 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
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F7/0065—Shape of casings for other machine parts and purposes, e.g. utilisation purposes, safety
    • F02F7/007—Adaptations for cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/02—Arrangements for cooling cylinders or cylinder heads
    • F01P2003/028—Cooling cylinders and cylinder heads in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
    • F01P2005/105—Using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P2060/00—Cooling circuits using auxiliaries
    • F01P2060/04—Lubricant cooler
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F7/0002—Cylinder arrangements
    • F02F7/0012—Crankcases of V-engines
    • 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 invention relates to the field of engines, and in particular to a high-power V-type multi-cylinder diesel engine system.
  • High-power high-speed diesel engines are generally used in generator stations, petrochemicals, high-speed light ships and ships. Basically, it is a four-stroke machine. Since the high-power high-speed diesel engine requires very high single-machine power, its strong load requirement is higher than that of the general diesel engine. For foreign advanced high-speed diesel engines, the average effective pressure is up to 3 MPa, and the highest explosion pressure is the highest. Up to 20MPa. Because high-power high-speed diesel engines require high power and high torque, they have high requirements for several important critical systems, such as cylinder assembly systems, power systems, diesel systems, cooling systems, and lubrication systems.
  • the object of the present invention is to provide a high-power V-type multi-cylinder diesel engine system which is compact, high in power and large in torque.
  • the present invention provides a high-power V-type multi-cylinder diesel engine system, comprising: a V-shaped cylinder block, wherein the V-shaped cylinder block is arranged with a plurality of two rows of cylinder holes arranged in a V shape, the two columns The angle between the cylinder bores is 90 degrees; a plurality of single cylinder heads respectively corresponding to the cylinder ports of the two rows of cylinder bores; and an intake system comprising four turbochargers and an intercooler, The intercooler is fixed at a position above the rear end of the V-shaped cylinder block, and each of the two turbochargers is arranged in a group, and the two sets of turbochargers are respectively arranged in two rows of the cylinder heads along the arrangement direction of the two rows of cylinder bores.
  • each set of turbocharger turbines are oppositely arranged and two vortex exhaust pipes converge to form an exhaust gas exhaust port, and each set of turbocharger compressors is connected with a transverse air filter, each The compressors of the turbochargers are respectively connected by a gas pipe and an intercooler, and the air coolers are respectively provided at two sides of the bottom of the intercooler, and the two air outlets are respectively connected with an intake pipe, and the intake pipe passes through five single pipes.
  • each unit is integrated into a single tube
  • a lubrication system comprising an oil sump, two pre-supply pumps, two oil pumps, an oil filter and an oil cooler, the oil sump is arranged at the bottom of the V-shaped cylinder block, and two pre-supplys are provided.
  • the oil pump is arranged on the front side of the oil sump, and the two oil pumps are arranged at the lower sides of the front end crank pulley of the V-shaped cylinder block, and the oil cooler is arranged at the upper left position of the front end of the V-shaped cylinder block, and the oil filter Located in the upper right position of the front end of the V-shaped cylinder block, the oil in the oil sump is simultaneously input into the oil cooler through two pre-supply pumps and two oil pumps, and the oil cooler and the oil filter are connected through the oil pipe, and the oil filter
  • the oil outlet of the cleaner is connected with the main oil passage of the V-shaped cylinder block; and the cooling system includes a high temperature water circulation loop including a rear radiator and a low temperature water pump, and a low temperature water circulation loop for cooling the oil
  • the cooler and the intercooler, the high temperature water circulation circuit includes a front radiator and a high temperature water pump, and the high temperature water circulation circuit is used to cool the V-shaped cylinder block and the plurality of unit
  • the two rows of cylinder bores of the V-shaped cylinder block are provided with a piston having a W combustion chamber, the piston has an inner cooling oil passage, and the circumferential wall of the piston is provided with four annular grooves.
  • the high temperature water pump and the low temperature water pump are disposed on the upper sides of the crankshaft pulley of the front end of the V-shaped cylinder block, and the crankshaft pulley drives the low temperature water pump and the high temperature water pump respectively, and the coolant flowing through the V-shaped cylinder block and the plurality of single cylinder heads
  • the outlet main pipe enters the front radiator, and a thermostat is connected between the outlet main pipe and the front radiator, and the thermostat is disposed on the V-shaped cylinder block on the rear side of the oil cooler.
  • the intercooler has a rectangular casing, the interior of the rectangular casing has an air circulation cavity, and the rectangular casing around the air circulation cavity is provided with a coolant flow passage, a low temperature water circulation circuit and a coolant flow passage in the rectangular casing. Connected.
  • the oil filter comprises a seat body and a plurality of filter cartridges disposed on the seat body, the plurality of filter cartridges being horizontally disposed.
  • the stroke and bore ratio of the high power V-type multi-cylinder diesel engine system is 1.05-1.23.
  • the high power V-type multi-cylinder diesel engine system has an adjacent cylinder center-to-bore ratio of 1.25-1.4.
  • the high power V-type multi-cylinder diesel engine system has a cylinder number of 12, 16, or 20.
  • the present invention has the following beneficial effects: by providing a V-shaped cylinder block, a plurality of single cylinder heads, four superchargers and an intercooler, the compressed air is cooled to further increase its density. It is beneficial to improve the power and improve the performance of the engine.
  • the cooling system is cooled by high and low temperature water, so that the high temperature and low temperature components can be classified and cooled, which can reduce the intake air temperature and oil temperature, and reduce the heat energy loss.
  • the engine is more fuel efficient and meets the high power and high speed diesel engine. Power, high torque requirements, the body is more compact and strong.
  • FIG. 1 is a schematic structural view of a V-shaped cylinder block of a high-power V-type multi-cylinder diesel engine system according to the present invention
  • FIG. 2 is a schematic structural view showing a single cylinder head disposed on a V-shaped cylinder block of a high-power V-type multi-cylinder diesel engine system according to the present invention
  • Figure 3 is a front elevational view of a high power V-type 20 cylinder diesel engine system in accordance with the present invention
  • Figure 4 is a right side elevational view of the high power V-type 20 cylinder diesel engine system in accordance with the present invention.
  • Figure 5 is a left side elevational view of a high power V-type 20 cylinder diesel engine system in accordance with the present invention.
  • Figure 6 is a top plan view of a high power V-type 20 cylinder diesel engine system in accordance with the present invention.
  • Figure 7 is a schematic diagram of a cooling system of a high power V-type multi-cylinder diesel engine system in accordance with the present invention.
  • a high-power V-type multi-cylinder diesel engine system includes a V-shaped cylinder block 100 and a plurality of unitary cylinder heads 200, wherein the V-shaped cylinder block 100 is mounted thereon.
  • a plurality of two rows of cylinder bores arranged in a V shape are arranged.
  • the angle between the two rows of cylinder bores of the V-shaped cylinder block 100 is 90 degrees, and the plurality of single cylinder heads 200 are respectively mounted on the V-shaped cylinder block 100.
  • the number of cylinders of the high-power V-type multi-cylinder diesel engine system provided in this embodiment may be 12, 16, or 20. In this embodiment, 20 cylinders are taken as an example for description.
  • the high-power V-type multi-cylinder diesel engine system includes a V-shaped cylinder block 100 and 20 single cylinder heads 200, wherein the V-shaped cylinder block 100 is provided with 20 V-shaped arrays.
  • the cylinder bores are arranged at an angle of 90 degrees between the two rows of cylinder bores of the V-shaped cylinder block 100, and the 20 individual cylinder heads 200 respectively correspond to the cylinder ports of the two rows of cylinder bores mounted on the V-shaped cylinder block 100.
  • An intake system is further included, the intake system includes four turbochargers and an intercooler 1, and each of the two turbochargers is arranged in a group, and the two sets of turbochargers are respectively arranged along the arrangement direction of the two rows of cylinder bores.
  • each set of turbocharger turbines 21 are oppositely disposed and two The vortex rear exhaust pipes converge to form an exhaust gas exhaust port 23, and each set of turbocharger compressors is connected with a transverse air filter 22, and each turbocharger compressor passes through the air pipe 24 and the intercooler respectively.
  • the air conditioner 1 is connected to the two sides of the bottom of the intercooler 1 (see FIG. 4), and the two air outlets 11 are respectively connected with an air inlet pipe 6, which is connected by five single tubes.
  • Each section of the single tube is integrally formed with an intake nozzle.
  • the lubrication system includes an oil pan 5, two pre-supply pumps 9, two oil pumps 8, an oil filter 10 and an oil cooler 4, and the oil pan 5 is provided at the bottom of the V-shaped cylinder block 100, and two pre-supplys
  • the oil pump 9 is disposed on the front side of the oil pan 5, and the two oil pumps 8 are disposed at the lower side positions of the front end crank pulley of the V-shaped cylinder block 100, and the oil cooler 4 is disposed at the upper left side of the front end of the V-shaped cylinder block 100.
  • the cooling system includes a high temperature water circulation circuit including a rear radiator and a low temperature water pump 6, and a low temperature water circulation circuit for cooling the oil cooler 4 and the intercooler 1.
  • the high temperature water circulation circuit includes a front radiator and a high temperature The water pump 7, the high temperature water circulation circuit is used to cool the V-shaped cylinder block 100 and the 20 individual cylinder heads 200.
  • the cooling system includes a high temperature water circulation circuit including a rear radiator and a low temperature water pump, and a low temperature water circulation circuit for cooling the oil cooler.
  • the high temperature water circulation circuit includes a front radiator and a high temperature water pump, and the high temperature water circulation circuit is used for Cooling the V-shaped cylinder block 100 and 20 single cylinder heads 200, which are cooled by high and low temperature water, low temperature water cooling intercooler and oil cooler, high temperature water cooling cylinder block and cylinder head, which can reduce intake air temperature and oil Temperature, while reducing heat loss, the engine is more fuel efficient.
  • a supercharged intercooling system is formed by providing four independent superchargers and an intercooler.
  • the exhaust gas from the engine exhaust pipe enters the turbine, and the exhaust gas pressure
  • the heat causes the turbine to rotate and rotates the compressor coaxial with the turbine.
  • the compressor draws in and compresses the air and then enters the engine intake pipe through the duct, and the cooled and expanded exhaust gas leaving the turbine is directed from the turbine casing to the exhaust gas exhaust port 23 at the intermediate position of the supercharger to enter the atmosphere.
  • the intake air is compressed, the air density charged into the cylinder is increased, and with the good cooperation of the oil supply system, more fuel is fully burned, the power is increased, and the economy is improved.
  • a piston having a W combustion chamber is disposed in the two rows of cylinder bores of the V-shaped cylinder block 100.
  • the piston has an inner cooling oil passage therein, and the circumferential wall of the piston is provided with four annular grooves.
  • the W combustion chamber technology is adopted, the intake air amount is large, the mixing is uniform, the combustion is more sufficient, and the power range region with low fuel consumption is wide.
  • the piston adopts an internal cooling oil passage structure, which has good cooling and a four-ring groove structure, and the sealing effect is better.
  • the high temperature water pump 7 and the low temperature water pump 6 are disposed on both sides of the front end crank pulley of the V-shaped cylinder block 100, and the crank pulley respectively drives the low temperature water pump 6 and the high temperature water pump 7, respectively, flowing through
  • the coolant of the V-shaped cylinder block 100 and the 20 individual cylinder heads 200 enters the front radiator through the water outlet main pipe, and the thermostat is connected between the water discharge main pipe and the front radiator, and the thermostat is disposed behind the oil cooler 4 On the side of the V-shaped cylinder block 100.
  • the intercooler 1 has a rectangular casing, and the interior of the rectangular casing has an air circulation cavity.
  • the rectangular casing around the air circulation cavity is provided with a coolant flow passage, a low temperature water circulation loop and a rectangular casing.
  • the coolant flow path is connected.
  • a low temperature water distributor can be arranged in the low temperature water circulation loop, and the low temperature water distributor can be fixed at a position near the front end of the V-shaped cylinder block near the crank pulley.
  • the purpose of the low temperature water distributor is to cool the oil cooler at the same time. 4 and intercooler 1.
  • the oil filter 10 includes a seat body and a plurality of filter cartridges disposed on the seat body.
  • the plurality of filter cartridges are horizontally disposed, preferably eight filter cartridges.
  • the present embodiment provides separate cooling using high and low temperature water, a low temperature water cooling intercooler and an oil cooler, and a high temperature water cooling cylinder block and a cylinder head.
  • the cooling system belongs to a forced closed circulating water cooling system and is cooled.
  • the liquid should be anti-freeze and anti-rust coolant.
  • Separate cooling with high and low temperature water, low temperature water cooling intercooler and oil cooler, high temperature water cooling cylinder block and cylinder head, high temperature water outlet water temperature is controlled at 75 ⁇ 95 °C
  • oil temperature is controlled at 80 ⁇ 110 °C.
  • pumps and fans, radiators, and oil coolers are the main components of the cooling system.
  • the high-low temperature water pump When the engine is running, the high-low temperature water pump is driven by the crankshaft timing gear through the left and right idle gears to drive the water pump impeller to rotate, and the coolant generates a certain pressure under the centrifugal force of the water pump, and flows out from the pump outlet.
  • the coolant pushed out by the high temperature water pump enters the cooling water jacket of the cylinder block and the cylinder head. After cooling the cylinder block and the cylinder head to the water outlet manifold, the coolant flows into the radiator through the thermostat.
  • the thermostat is installed at the end of the water outlet pipe, and the thermostat automatically controls the temperature function. When the coolant temperature is greater than 75 ° C, the thermostat is turned on.
  • the thermostat When the coolant temperature is greater than 85 ° C, the thermostat is fully opened, and the cooling is performed at this time. The liquid enters the radiator and flows back to the pump. If the coolant temperature is less than 75 ° C, it does not need to be cooled by the radiator to directly flow to the pump to go back to the cooling cycle.
  • the cryopump cools the intercooler and the oil cooler and then returns to the heat sink for heat dissipation. This high-temperature and low-temperature component is classified and cooled to reduce intake air temperature and oil temperature while reducing heat loss and making the engine more fuel efficient.
  • the high power V-type multi-cylinder diesel engine system has a stroke to bore ratio of 1.05-1.23.
  • the smaller stroke-to-bore ratio is used to reduce the height, width and weight of the diesel engine, and the speed of the diesel engine can be increased to increase the power of the diesel engine.
  • the high power V-type multi-cylinder diesel engine system has an adjacent cylinder center-to-bore ratio of 1.25-1.4.
  • the cylinder center distance and bore ratio are 1.25-1.4, the length of the diesel engine is more compact, the diesel engine is more strengthened, and the crankshaft and the body are more rigid.
  • the length of the crankshaft is shortened, the torsional stiffness is enhanced, the frequency of the self-vibrating circle of the shafting is improved, and the torsional vibration performance is improved.
  • the high-power V-type multi-cylinder diesel engine system of the present embodiment has a V-shaped cylinder block 100 and a plurality of single cylinder heads 200, and the intake system is provided with four superchargers and an intercooler, and the compressed air passes through Cooling, further increasing its density, is beneficial to improve engine power and improve performance.
  • the cooling system is cooled by high and low temperature water, so that high temperature and low temperature components can be classified and cooled, which can reduce intake air temperature and oil temperature, and reduce heat loss. It saves fuel and meets the requirements of high power and high torque of high-power high-speed diesel engines.
  • the body is more compact and has high strength.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Abstract

一种大功率V型多缸柴油机系统，包括V形气缸体（100）和多个单体气缸盖（200）；进气系统，其包括四个涡轮增压器和一个中冷器（1）；润滑系统，其包括油底壳（5）、两个预供油泵（9）、两个机油泵（8）、机油滤清器（10）和机油冷却器（4）；以及冷却系统，其包括高温水循环回路和低温水循环回路，低温水循环回路用来冷却机油冷却器（4）和中冷器（1），高温水循环回路包括前排散热器和高温水泵（7），高温水循环回路用来冷却V形气缸体（100）和多个单体气缸盖（200）。该大功率V型多缸柴油机系统机体紧凑、功率高、扭矩大。

Description

大功率V型多缸柴油机系统
本发明要求广西玉柴机器股份有限公司于2018年02月07日向中国专利局提交的、申请号为201810122083.X、发明名称为“大功率V型多缸柴油机系统”的中国专利申请的优先权，该申请的全部内容通过引用结合在本发明中。
技术领域
本发明涉及发动机领域，特别涉及一种大功率V型多缸柴油机系统。
背景技术
大功率高速柴油机一般应用于发电机站、石油化工、高速轻型船舶和舰艇等。基本为四冲程机，由于大功率高速柴油机要求有非常高的单机功率，因此，其强载度要求较一般柴油机高，对于国外先进的高速柴油机，其平均有效压力最高达3MPa，最高爆压最高达20MPa。由于大功率高速柴油机要求具有高功率、大扭矩的特点，其对几项重要关键系统的要求比较高，比如缸体总成系统、动力系统、柴油系统、冷却系统、润滑系统等。
公开于该背景技术部分的信息仅仅旨在增加对本发明的总体背景的理解，而不应当被视为承认或以任何形式暗示该信息构成已为本领域一般技术人员所公知的现有技术。
发明内容
本发明的目的在于提供一种大功率V型多缸柴油机系统，机体紧凑、功率高、扭矩大。
为实现上述目的，本发明提供了一种大功率V型多缸柴油机系统，包括：V形气缸体，该V形气缸体上布置有多个呈V形排列的两列气缸孔，该两列气缸孔之间的夹角为90度；多个单体气缸盖，其分别对应安装在两列气缸孔的缸口部位；进气系统，其包括四个涡轮增压器和一个中冷器，中冷器固定在V形气缸体的后端上方位置， 每两个涡轮增压器设置成一组，两组涡轮增压器分别沿两列气缸孔的排列方向布置在两列单体气缸盖的后端上方位置，每组涡轮增压器的涡轮机相对设置且两个涡后排气管汇聚形成一个废气排气口，每组涡轮增压器的压气机上连接有横向的空气滤清器，每个涡轮增压器的压气机分别通过气管和中冷器接通，中冷器的底部两侧分别设有空气出口，该两个空气出口上分别连接有进气管，进气管通过五节单管连接而成，每节单管上一体成型有进气接管；润滑系统，其包括油底壳、两个预供油泵、两个机油泵、机油滤清器和机油冷却器，油底壳设在V形气缸体的底部，两个预供油泵设在油底壳的前侧，两个机油泵设在V形气缸体的前端曲轴皮带轮的下方两侧位置，机油冷却器设在V形气缸体的前端的左上方位置，机油滤清器设在V形气缸体的前端的右上方位置，油底壳内的机油通过两个预供油泵和两个机油泵同时输入机油冷却器，机油冷却器和机油滤清器通过油管连接，机油滤清器的出油口与V形气缸体的主机油道连通；以及冷却系统，其包括高温水循环回路和低温水循环回路，低温水循环回路包括后排散热器和低温水泵，低温水循环回路用来冷却机油冷却器和中冷器，高温水循环回路包括前排散热器和高温水泵，高温水循环回路用来冷却V形气缸体和多个单体气缸盖。
优选地，V形气缸体的两列气缸孔内设置有具有W燃烧室的活塞，活塞内部具有内冷油道，活塞的圆周壁上设有四道环槽。
优选地，高温水泵和低温水泵设置在V形气缸体的前端曲轴皮带轮的上方两侧，曲轴皮带轮分别驱动低温水泵和高温水泵，流经V形气缸体和多个单体气缸盖的冷却液经出水总管进入前排散热器，出水总管和前排散热器之间连接有节温器，节温器设置在机油冷却器后侧的V形气缸体上。
优选地，中冷器呈长方形壳体，长方形壳体的内部具有空气流通腔体，空气流通腔体周围的长方形壳体内设有冷却液流道，低温水循环回路与长方形壳体内的冷却液流道连通。
优选地，机油滤清器包括座体和设置在该座体上的多个滤筒，多个滤筒水平设置。
优选地，大功率V型多缸柴油机系统的冲程与缸径比值为1.05-1.23。
优选地，大功率V型多缸柴油机系统的相邻气缸中心距与缸径比值为1.25-1.4。
优选地，大功率V型多缸柴油机系统缸数为12、16或20。
与现有技术相比，本发明具有如下有益效果：通过设置V形气缸体、多个单体气缸盖，四个增压器和一个中冷器，压缩空气经过冷却，使其密度进一步提高，有利于提高发动机的功率、改善性能，冷却系统采用高低温水分开冷却，这样高温和低温部件分类冷却，可降低进气温度和机油温度，同时减少热能损失，发动机更省油，满足大功率高速柴油机高功率、大扭矩的要求，机体更加紧凑，强度大。
附图说明
图1是根据本发明的大功率V型多缸柴油机系统的V形气缸体的结构示意图；
图2是根据本发明的大功率V型多缸柴油机系统的V形气缸体上布置单体气缸盖的结构示意图；
图3是根据本发明的大功率V型20缸柴油机系统的主视图；
图4是根据本发明的大功率V型20缸柴油机系统的右视图；
图5是根据本发明的大功率V型20缸柴油机系统的左视图；
图6是根据本发明的大功率V型20缸柴油机系统的俯视图；
图7是根据本发明的大功率V型多缸柴油机系统的冷却系统的原理图。
具体实施方式
下面结合附图，对本发明的具体实施方式进行详细描述，但应当理解本发明的保护范围并不受具体实施方式的限制。
除非另有其它明确表示，否则在整个说明书和权利要求书中，术语“包括”或其变换如“包含”或“包括有”等等将被理解为包括所陈述的元件或组成部分，而并未排除其它元件或其它组成部分。
如图1至图2所示，根据本发明具体实施方式的一种大功率V型多缸柴油机系统，包括V形气缸体100和多个单体气缸盖200，其中该V形气缸体100上布置有多个呈V形排列的两列气缸孔，该V形气缸体100的两列气缸孔之间的夹角为90度，多个 单体气缸盖200分别对应安装在V形气缸体100上两列气缸孔的缸口部位。
本实施例提供的大功率V型多缸柴油机系统的缸数可以为12、16或20，本实施例以20缸为例进行说明。
如图3至6所示，该大功率V型多缸柴油机系统包括V形气缸体100和20个单体气缸盖200，其中该V形气缸体100上布置有20个呈V形排列的两列气缸孔，该V形气缸体100的两列气缸孔之间的夹角为90度，20个单体气缸盖200分别对应安装在V形气缸体100上两列气缸孔的缸口部位。还包括进气系统，进气系统包括四个涡轮增压器和一个中冷器1，每两个涡轮增压器设置成一组，两组涡轮增压器分别沿两列气缸孔的排列方向布置在两列单体气缸盖的后端上方位置(参见图6，沿两列气缸孔的排列方向设置的两个涡轮增压器成一组)，每组涡轮增压器的涡轮机21相对设置且两个涡后排气管汇聚形成一个废气排气口23，每组涡轮增压器的压气机上连接有横向的空气滤清器22，每个涡轮增压器的压气机分别通过气管24和中冷器1接通，中冷器1的底部两侧分别设有空气出口11(参见图4)，该两个空气出口11上分别连接有进气管6，进气管6通过五节单管连接而成，每节单管上一体成型有进气接管。润滑系统包括油底壳5、两个预供油泵9、两个机油泵8、机油滤清器10和机油冷却器4，油底壳5设在V形气缸体100的底部，两个预供油泵9设在油底壳5的前侧，两个机油泵8设在V形气缸体100的前端曲轴皮带轮的下方两侧位置，机油冷却器4设在V形气缸体100的前端的左上方位置，机油滤清器10设在V形气缸体100的前端的右上方位置，油底壳5内的机油同时通过两个预供油泵9和两个机油泵8输入机油冷却器4，机油冷却器4和机油滤清器10通过油管连接，机油滤清器10的出油口与V形气缸体100的主机油道连通。冷却系统包括高温水循环回路和低温水循环回路，低温水循环回路包括后排散热器和低温水泵6，低温水循环回路用来冷却机油冷却器4和中冷器1，高温水循环回路包括前排散热器和高温水泵7，高温水循环回路用来冷却V形气缸体100和20个单体气缸盖200。
上述方案中，每缸一盖的设计，缸盖强度高。冷却系统包括高温水循环回路和低温水循环回路，低温水循环回路包括后排散热器和低温水泵，低温水循环回路用来冷却机油冷却器，高温水循环回路包括前排散热器和高温水泵，高温水循环回路用来冷却V形气缸体100和20个单体气缸盖200，这种采用高低温水分开冷却，低温水冷却中冷器和机油冷却器，高温水冷却气缸体与气缸盖，可降低进气温度和机油温度，同时减少热能损失，发动机更省油。采用现有的废气涡轮增压技术，通过设置四个独 立的增压器和一个中冷器形成一种增压中冷系统，发动机工作时，来自发动机排气管的废气进入涡轮，废气压力中的热能使涡轮转动，并使与涡轮同轴的压气机转动。压气机将空气吸入并压缩，然后通过管道进入发动机进气管，离开涡轮的已冷却和膨胀的废气由涡轮壳集中引向增压器中间位置的废气排气口23进入大气。进气经压缩后，提高了充入气缸的空气密度，在供油系统的良好配合下，使更多的燃料得以充分燃烧，提高了功率，并改善经济性。
作为一种优选实施例，V形气缸体100的两列气缸孔内设置有具有W燃烧室的活塞，活塞内部具有内冷油道，活塞的圆周壁上设有四道环槽。本方案中，采用W燃烧室技术，进气量大，混合均匀，燃烧更充分，油耗低的功率范围区域宽。活塞采用内冷油道结构，冷却好，四环槽结构，密封效果更好。
作为一种优选实施例，如图5所示，高温水泵7和低温水泵6设置在V形气缸体100的前端曲轴皮带轮的上方两侧，曲轴皮带轮分别驱动低温水泵6和高温水泵7，流经V形气缸体100和20个单体气缸盖200的冷却液经出水总管进入前排散热器，出水总管和前排散热器之间连接有节温器，节温器设置在机油冷却器4后侧的V形气缸体100上。
作为一种优选实施例，中冷器1呈长方形壳体，长方形壳体的内部具有空气流通腔体，空气流通腔体周围的长方形壳体内设有冷却液流道，低温水循环回路与长方形壳体内的冷却液流道连通。本方案中，低温水循环回路中可以设置低温水分配器，低温水分配器可以固定在V形气缸体的前端靠近曲轴皮带轮上方的位置，设置低温水分配器的目的就是，低温水循环回路可以同时冷却机油冷却器4和中冷器1。
作为一种优选实施例，机油滤清器10包括座体和设置在该座体上的多个滤筒，多个滤筒水平设置，最好设置8个滤筒。
如图7所示，本实施例提出的采用高低温水分开冷却，低温水冷却中冷器和机油冷却器，高温水冷却气缸体与气缸盖，该冷却系统属于强制闭式循环水冷却系统，冷却液应采用防冻、防锈冷却液。采用高、低温水分开冷却，低温水冷却中冷器和机油冷却器，高温水冷却气缸体与气缸盖，高温水出水温度控制在75～95℃，机油温度控制在80～110℃较适宜。该系统中，水泵及风扇、散热器、机油冷却器是冷却系统的主要部件。发动机运行时，由曲轴正时齿轮通过左右惰齿轮分别驱动高低温水泵，带动水泵叶轮转动，冷却液在水泵离心力作用下产生一定的压力，从水泵出口处流出。高 温水泵压出的冷却液进入气缸体、气缸盖的冷却水套，冷却液在冷却气缸体、气缸盖后至出水总管，经节温器后流入散热器。节温器装在出水管端部，节温器自动控制温度功能，当冷却液温度大于75℃时，节温器开启，当冷却液温度大于85℃时，节温器全开，此时冷却液全部进入散热器，再流回至水泵。若冷却液温度小于75℃，无需经散热器散热冷却而直接流至水泵重新走冷却循环。低温水泵则冷却中冷器与机油冷却器，然后回到散热器进行散热。这种高温和低温部件分类冷却，可降低进气温度和机油温度，同时减少热能损失，发动机更省油。
作为一种优选实施例，大功率V型多缸柴油机系统的冲程与缸径比值为1.05-1.23。本方案中，选用较小的行程与缸径比值，可以减小柴油机的高度、宽度和重量，柴油机的转速可增加，提高了柴油机的功率。
作为一种优选实施例，大功率V型多缸柴油机系统的相邻气缸中心距与缸径比值为1.25-1.4。本方案中，气缸中心距与缸径比1.25-1.4，柴油机的长度更紧凑，柴油机的强化程度更高，曲轴及机体的刚度更强。由于曲轴长度缩短，扭转刚度增强，提高了轴系自振圆频率，扭振性能获得改善。
综上，本实施例的大功率V型多缸柴油机系统，通过设置V形气缸体100、多个单体气缸盖200，进气系统配套四个增压器和一个中冷器，压缩空气经过冷却，使其密度进一步提高，有利于提高发动机的功率、改善性能，冷却系统采用高低温水分开冷却，这样高温和低温部件分类冷却，可降低进气温度和机油温度，同时减少热能损失，发动机更省油，满足大功率高速柴油机高功率、大扭矩的要求，机体更加紧凑，强度大。
前述对本发明的具体示例性实施方案的描述是为了说明和例证的目的。这些描述并非想将本发明限定为所公开的精确形式，并且很显然，根据上述教导，可以进行很多改变和变化。对示例性实施例进行选择和描述的目的在于解释本发明的特定原理及其实际应用，从而使得本领域的技术人员能够实现并利用本发明的各种不同的示例性实施方案以及各种不同的选择和改变。本发明的范围意在由权利要求书及其等同形式所限定。

Claims (8)

  1. 一种大功率V型多缸柴油机系统，其特征在于，包括：
    V形气缸体，该V形气缸体上布置有多个呈V形排列的两列气缸孔，该两列气缸孔之间的夹角为90度；
    多个单体气缸盖，其分别对应安装在所述两列气缸孔的缸口部位；
    进气系统，其包括四个涡轮增压器和一个中冷器，所述中冷器固定在所述V形气缸体的后端上方位置，每两个涡轮增压器设置成一组，两组涡轮增压器分别沿所述两列气缸孔的排列方向布置在两列单体气缸盖的后端上方位置，每组涡轮增压器的涡轮机相对设置且两个涡后排气管汇聚形成一个废气排气口，每组涡轮增压器的压气机上连接有横向的空气滤清器，每个涡轮增压器的压气机分别通过气管和所述中冷器接通，所述中冷器的底部两侧分别设有空气出口，该两个空气出口上分别连接有进气管，所述进气管通过五节单管连接而成，每节单管上一体成型有进气接管；
    润滑系统，其包括油底壳、两个预供油泵、两个机油泵、机油滤清器和机油冷却器，所述油底壳设在所述V形气缸体的底部，所述两个预供油泵设在所述油底壳的前侧，所述两个机油泵设在所述V形气缸体的前端曲轴皮带轮的下方两侧位置，所述机油冷却器设在所述V形气缸体的前端的左上方位置，所述机油滤清器设在所述V形气缸体的前端的右上方位置，所述油底壳内的机油通过所述两个预供油泵和所述两个机油泵同时输入所述机油冷却器，所述机油冷却器和所述机油滤清器通过油管连接，所述机油滤清器的出油口与所述V形气缸体的主机油道连通；以及
    冷却系统，其包括高温水循环回路和低温水循环回路，所述低温水循环回路包括后排散热器和低温水泵，所述低温水循环回路用来冷却所述机油冷却器和所述中冷器，所述高温水循环回路包括前排散热器和高温水泵，所述高温水循环回路用来冷却所述V形气缸体和所述多个单体气缸盖。
  2. 根据权利要求1所述的大功率V型多缸柴油机系统，其特征在于，所述V形气缸体的两列气缸孔内设置有具有W燃烧室的活塞，所述活塞内部具有内冷油道， 所述活塞的圆周壁上设有四道环槽。
  3. 根据权利要求1所述的大功率V型多缸柴油机系统，其特征在于，所述高温水泵和所述低温水泵设置在所述V形气缸体的前端曲轴皮带轮的上方两侧，所述曲轴皮带轮分别驱动所述低温水泵和所述高温水泵，流经所述V形气缸体和所述多个单体气缸盖的冷却液经出水总管进入所述前排散热器，所述出水总管和所述前排散热器之间连接有节温器，所述节温器设置在所述机油冷却器后侧的V形气缸体上。
  4. 根据权利要求1所述的大功率V型多缸柴油机系统，其特征在于，所述中冷器呈长方形壳体，所述长方形壳体的内部具有空气流通腔体，所述空气流通腔体周围的长方形壳体内设有冷却液流道，所述低温水循环回路与所述长方形壳体内的冷却液流道连通。
  5. 根据权利要求1所述的大功率V型多缸柴油机系统，其特征在于，所述机油滤清器包括座体和设置在该座体上的多个滤筒，所述多个滤筒水平设置。
  6. 根据权利要求1所述的大功率V型多缸柴油机系统，其特征在于，所述大功率V型多缸柴油机系统的冲程与缸径比值为1.05-1.23。
  7. 根据权利要求1所述的大功率V型多缸柴油机系统，其特征在于，所述大功率V型多缸柴油机系统的相邻气缸中心距与缸径比值为1.25-1.4。
  8. 根据权利要求1所述的大功率V型多缸柴油机系统，其特征在于，所述大功率V型多缸柴油机系统缸数为12、16或20。
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