WO2019153497A1 - 大功率v型16缸柴油机 - Google Patents

大功率v型16缸柴油机 Download PDF

Info

Publication number
WO2019153497A1
WO2019153497A1 PCT/CN2018/083193 CN2018083193W WO2019153497A1 WO 2019153497 A1 WO2019153497 A1 WO 2019153497A1 CN 2018083193 W CN2018083193 W CN 2018083193W WO 2019153497 A1 WO2019153497 A1 WO 2019153497A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
cylinder
cylinder block
temperature water
diesel engine
Prior art date
Application number
PCT/CN2018/083193
Other languages
English (en)
French (fr)
Inventor
沈捷
黄永仲
黄第云
李伟
覃明智
谢夏琳
Original Assignee
广西玉柴机器股份有限公司
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 广西玉柴机器股份有限公司 filed Critical 广西玉柴机器股份有限公司
Publication of WO2019153497A1 publication Critical patent/WO2019153497A1/zh

Links

Images

Classifications

    • 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
    • F02B75/221—Multi-cylinder engines with cylinders in V, fan, or star arrangement with cylinder banks in narrow V-arrangement, having a single cylinder head
    • 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
    • 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
    • F01P3/00—Liquid cooling
    • F01P3/20—Cooling circuits not specific to a single part of engine or machine
    • 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
    • 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
    • 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
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • 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
    • 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
    • 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
    • F02B2075/1804—Number of cylinders
    • F02B2075/1864—Number of cylinders sixteen
    • 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 16-cylinder diesel engine.
  • 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 16-cylinder diesel engine with compact body, high power and large torque.
  • the present invention provides a high-power V-type 16-cylinder diesel engine comprising: a V-shaped cylinder block, wherein the V-shaped cylinder block is arranged with 16 rows of cylinder holes arranged in a V shape, and the two columns of cylinders The angle between the holes is 90 degrees; 16 single cylinder heads respectively corresponding to the cylinder ports of the two rows of cylinder bores; the intake system comprising four turbochargers and an intercooler, The four turbochargers are respectively fixed above the single cylinder head by brackets and arranged in a rectangular array.
  • the compressors of each turbocharger are on the outer side, and the turbine of each turbocharger is on the inner side.
  • each turbocharger is connected to an exhaust pipe on the turbine and aggregates to a central position of the four turbochargers to form an exhaust gas exhaust port, which is intercooled.
  • the device is fixed at a position above the rear end of the V-shaped cylinder block, and the compressor of each turbocharger is connected through a gas pipe and an intercooler, and air outlets are respectively disposed at two sides of the bottom of the intercooler, and the two air outlets are respectively Connected to the intake pipe separately; lubrication
  • the system includes an oil pan, a pre-supply pump, an oil pump, an oil filter and an oil cooler.
  • the oil pan is arranged at the bottom of the V-shaped cylinder block, and the pre-supply pump is arranged on the front side of the oil pan, the oil pump
  • the oil cooler is disposed at the upper left position of the front end of the V-shaped cylinder block, and the oil filter is disposed at the upper right position of the front end of the V-shaped cylinder block, and the oil sump is disposed at the upper right end of the V-shaped cylinder block.
  • the oil is input into the oil cooler through the pre-supply pump and the oil pump, the oil cooler and the oil filter are connected through the oil pipe, the oil outlet of the oil filter is connected with the main oil passage of the V-shaped cylinder block; and the cooling system includes High temperature water circulation loop and low temperature water circulation loop, low temperature water circulation loop includes rear radiator and low temperature water pump, low temperature water circulation loop is used to cool oil cooler and intercooler, high temperature water circulation loop includes front radiator and high temperature water pump, high temperature water circulation loop To cool the V-shaped cylinder block and 16 individual cylinder heads.
  • 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 both 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 16 individual 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 high power V-type 16 cylinder diesel engine has a stroke to bore ratio of 1.1 to 1.3.
  • the ratio of the center-to-cylinder spacing of the adjacent cylinders of the high-power V-type 16-cylinder diesel engine is 1.3-1.45.
  • the invention has the following beneficial effects: by providing a V-shaped cylinder block, 16 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 16-cylinder diesel engine according to the present invention
  • FIG. 2 is a schematic structural view of a single cylinder head disposed on a V-shaped cylinder block of a high-power V-type 16-cylinder diesel engine according to the present invention
  • Figure 3 is a front elevational view of a high power V-type 16 cylinder diesel engine in accordance with the present invention.
  • Figure 4 is a left side elevational view of a high power V-type 16 cylinder diesel engine in accordance with the present invention.
  • Figure 5 is a right side view of a high power V-type 16 cylinder diesel engine in accordance with the present invention.
  • Figure 6 is a plan view of a high power V-type 16 cylinder diesel engine in accordance with the present invention.
  • Figure 7 is a schematic diagram of a cooling system of a high power V-type 16 cylinder diesel engine in accordance with the present invention.
  • a high-power V-type 16-cylinder diesel engine including a V-shaped cylinder block 100 and 16 single cylinder heads 200 according to an embodiment of the present invention, wherein the V-shaped cylinder block 100 is disposed There are six rows of cylinder bores arranged in a V shape. The angle between the two rows of cylinder bores of the V-shaped cylinder block 100 is 90 degrees, and the 16 individual cylinder heads 200 are respectively mounted on the V-shaped cylinder block 100. The cylinder mouth of the two rows of cylinder bores.
  • the high-power V-type 16-cylinder diesel engine further includes an intake system including four turbochargers 2 and an intercooler 1 respectively fixed to the single cylinder head 200 by brackets Above and arranged in a rectangular array (see Figure 6), the compressor of each turbocharger 2 is on the outside, the turbine of each turbocharger 2 is on the inside, and the compressor of each turbocharger 2 is connected An air filter that is erected upward, an exhaust pipe is connected to the turbine of each turbocharger 2 and converges toward a central position of the four turbochargers 2 to form an exhaust gas exhaust port 3 (see Fig.
  • the cooler 1 is fixed at a position above the rear end of the V-shaped cylinder block 100, and the compressor of each turbocharger 2 is connected through the air pipe and the intercooler 1, and the air cooler is respectively provided at both sides of the bottom of the intercooler 1.
  • An air intake pipe 6 is respectively connected to the two air outlets, and the lubrication system includes an oil pan 5, a pre-supply pump 9, an oil pump 8, an oil filter 10 and an oil cooler 4, and the oil pan 5 is arranged in the V-shaped cylinder.
  • the pre-supply pump 9 is disposed on the front side of the oil pan 5, and the oil pump 8 is disposed in the V-cylinder
  • the oil cooler 4 is disposed at the upper left position of the front end of the V-shaped cylinder block 100
  • the oil filter 10 is disposed at the upper right position of the front end of the V-shaped cylinder block 100
  • the oil sump 5 is disposed.
  • the oil is input to the oil cooler 4 through the pre-supply pump 9 and the oil pump 8, and the oil cooler 4 and the oil filter 10 are connected through the oil pipe, the oil outlet of the oil filter 10 and the main oil passage of the V-shaped cylinder block 100. Connected.
  • the cooling system includes a high temperature water circulation circuit including a rear radiator and a low temperature water pump 7, 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 6, the high temperature water circulation circuit is used to cool the V-shaped cylinder block 100 and the 16 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 16 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 concentrated from the turbine casing to the exhaust gas exhaust port 3 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.
  • the angle between the two rows of cylinder bores of the V-shaped cylinder block 100 is 90 degrees, ensuring that the firing angle of each cylinder is 45 degrees and the ignition is uniform.
  • 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 is well cooled and has a four-ring groove structure for better sealing effect.
  • the high temperature water pump 6 and the low temperature water pump 7 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 7 and the high temperature water pump 6, flowing through
  • the cooling liquid of the V-shaped cylinder block 100 and the 16 single 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. And intercooler.
  • 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 16 cylinder diesel engine has a stroke to bore ratio of 1.1 to 1.3.
  • 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 ratio of the center-to-cylinder spacing of the adjacent cylinders of the high-power V-type 16-cylinder diesel engine is 1.3-1.45.
  • the cylinder center distance and cylinder diameter ratio is 1.3-1.45, 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 16-cylinder diesel engine of the present embodiment is provided with a V-shaped cylinder block 100 and 16 single cylinder heads 200, and the intake system is provided with four superchargers and an intercooler, and the compressed air is cooled.
  • the density is further improved, which is beneficial to improve the power of the engine and improve the performance.
  • the cooling system is cooled by high and low temperature water, so that the high temperature and low temperature components are classified and cooled, which can reduce the intake air temperature and the oil temperature, and reduce the heat energy loss, and the engine is more fuel efficient.
  • the body is more compact and strong.

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)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Supercharger (AREA)

Abstract

一种大功率V型16缸柴油机，包括V形气缸体（100）和16个单体气缸盖（200）；进气系统，其包括四个涡轮增压器（2）和一个中冷器（1）；润滑系统，其包括机油冷却器（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（6），高温水循环回路用来冷却V形气缸体（100）和16个单体气缸盖（200）。该柴油机机体紧凑、功率高、扭矩大。

Description

大功率V型16缸柴油机
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201810122575.9、发明名称为“大功率V型16缸柴油机”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16缸柴油机。
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16缸柴油机，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16缸柴油机，包括：V形气缸体，该V形气缸体上布置有16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；16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，该四个涡轮增压器分别通过支架固定在单体气 缸盖的上方且呈矩形阵排列，每个涡轮增压器的压气机处于外侧，每个涡轮增压器的涡轮机处于内侧，每个涡轮增压器的压气机上连接有向上竖立的空气滤清器，每个涡轮增压器的涡轮机上连接有排气管并且向四个涡轮增压器的中心位置汇聚形成一个废气排气口，中冷器固定在V形气缸体的后端上方位置，每个涡轮增压器的压气机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；润滑系统，其包括油底壳、预供油泵、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，预供油泵设在油底壳的前侧，机油泵设在V形气缸体的前端左下方位置，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预供油泵和机油泵输入机油冷却器，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16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16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，大功率V型16缸柴油机的冲程与缸径比值为1.1-1.3。
优选地，大功率V型16缸柴油机的相邻气缸中心距与缸径比值为1.3-1.45。
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、16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16缸柴油机的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16缸柴油机的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16缸柴油机的主视图；
图4是根据本发明的大功率V型16缸柴油机的左视图；
图5是根据本发明的大功率V型16缸柴油机的右视图；
图6是根据本发明的大功率V型16缸柴油机的俯视图；
图7是根据本发明的大功率V型16缸柴油机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16缸柴油机，包括V形气缸体100和16个单体气缸盖200，其中该V形气缸体100上布置有16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，16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。该大功率V型16缸柴油机还包括进气系统，进气系统包括四个涡轮增压器2和一个中冷器1，该四个涡轮增压器2分别通过支架固定在单体气缸盖200的上方且呈矩形阵排列(参见图6)，每个涡轮增压器2的压气机处于外侧，每个涡轮增压器2的涡轮机处 于内侧，每个涡轮增压器2的压气机上连接有向上竖立的空气滤清器，每个涡轮增压器2的涡轮机上连接有排气管并且向四个涡轮增压器2的中心位置汇聚形成一个废气排气口3(参见图6)，中冷器1固定在V形气缸体100的后端上方位置，每个涡轮增压器2的压气机通过气管和中冷器1接通，中冷器1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6，润滑系统包括油底壳5、预供油泵9、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，预供油泵9设在油底壳5的前侧，机油泵8设在V形气缸体100的前端左下方位置，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内的机油通过预供油泵9和机油泵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7，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6，高温水循环回路用来冷却V形气缸体100和16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16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3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。V形气缸体100的两列气缸孔之间的夹角为90度，确保各缸发火间隔角均为45度，发火均匀。
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6和低温水泵7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7和高温水泵6，流经V形气缸体100和16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和中冷器。
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16缸柴油机的冲程与缸径比值为1.1-1.3。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16缸柴油机的相邻气缸中心距与缸径比值为 1.3-1.45。本方案中，气缸中心距与缸径比1.3-1.45，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16缸柴油机，通过设置V形气缸体100、16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 (6)

  1. 一种大功率V型16缸柴油机，其特征在于，包括：
    V形气缸体，该V形气缸体上布置有16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；
    16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，该四个涡轮增压器分别通过支架固定在所述单体气缸盖的上方且呈矩形阵排列，每个涡轮增压器的压气机处于外侧，每个涡轮增压器的涡轮机处于内侧，每个涡轮增压器的压气机上连接有向上竖立的空气滤清器，每个涡轮增压器的涡轮机上连接有排气管并且向所述四个涡轮增压器的中心位置汇聚形成一个废气排气口，所述中冷器固定在所述V形气缸体的后端上方位置，每个涡轮增压器的压气机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；
    润滑系统，其包括油底壳、预供油泵、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，所述预供油泵设在所述油底壳的前侧，所述机油泵设在所述V形气缸体的前端左下方位置，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预供油泵和所述机油泵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16个单体气缸盖。
  2. 根据权利要求1所述的大功率V型16缸柴油机，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16缸柴油机，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16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16缸柴油机，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4所述的大功率V型16缸柴油机，其特征在于，所述大功率V型16缸柴油机的冲程与缸径比值为1.1-1.3。
  6. 根据权利要求5所述的大功率V型16缸柴油机，其特征在于，所述大功率V型16缸柴油机的相邻气缸中心距与缸径比值为1.3-1.45。
PCT/CN2018/083193 2018-02-07 2018-04-16 大功率v型16缸柴油机 WO2019153497A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201810122575.9A CN108194198B (zh) 2018-02-07 2018-02-07 大功率v型16缸柴油机
CN201810122575.9 2018-02-07

Publications (1)

Publication Number Publication Date
WO2019153497A1 true WO2019153497A1 (zh) 2019-08-15

Family

ID=62593248

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2018/083193 WO2019153497A1 (zh) 2018-02-07 2018-04-16 大功率v型16缸柴油机

Country Status (2)

Country Link
CN (1) CN108194198B (zh)
WO (1) WO2019153497A1 (zh)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109611440A (zh) * 2019-02-15 2019-04-12 广西玉柴机器股份有限公司 V型18缸柴油机曲轴

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0095250A1 (en) * 1982-05-24 1983-11-30 General Motors Corporation Compact odd cylinder V-type engine
US20090078240A1 (en) * 2007-09-24 2009-03-26 Ford Global Technologies, Llc Push Rod Engine With Inboard Exhaust
CN202611847U (zh) * 2012-05-22 2012-12-19 广西玉柴机器股份有限公司 V型柴油机冷却水路分配体
CN104832278A (zh) * 2015-05-27 2015-08-12 无锡开普动力有限公司 V型发动机
CN205206948U (zh) * 2015-11-04 2016-05-04 南车玉柴四川发动机股份有限公司 一种运用于中速柴油机上输出端双增压器的增压系统
CN106224094A (zh) * 2016-08-31 2016-12-14 河北华北柴油机有限责任公司 12缸水冷柴油发动机

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4622714B2 (ja) * 2005-07-15 2011-02-02 三浦工業株式会社 エネルギーの有効利用システム
MY145271A (en) * 2006-03-24 2012-01-13 Scuderi Group Llc System and method for split-cycle engine waste heat recovery
CN208040535U (zh) * 2018-02-07 2018-11-02 广西玉柴机器股份有限公司 大功率v型16缸柴油机

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0095250A1 (en) * 1982-05-24 1983-11-30 General Motors Corporation Compact odd cylinder V-type engine
US20090078240A1 (en) * 2007-09-24 2009-03-26 Ford Global Technologies, Llc Push Rod Engine With Inboard Exhaust
CN202611847U (zh) * 2012-05-22 2012-12-19 广西玉柴机器股份有限公司 V型柴油机冷却水路分配体
CN104832278A (zh) * 2015-05-27 2015-08-12 无锡开普动力有限公司 V型发动机
CN205206948U (zh) * 2015-11-04 2016-05-04 南车玉柴四川发动机股份有限公司 一种运用于中速柴油机上输出端双增压器的增压系统
CN106224094A (zh) * 2016-08-31 2016-12-14 河北华北柴油机有限责任公司 12缸水冷柴油发动机

Also Published As

Publication number Publication date
CN108194198A (zh) 2018-06-22
CN108194198B (zh) 2022-04-12

Similar Documents

Publication Publication Date Title
US20150361839A1 (en) Oil cooling system for supercharged engine
WO2019153494A1 (zh) V型多缸柴油机的冷却系统
RU175618U1 (ru) Дизельный двигатель с V-образным расположением рядов цилиндров
WO2019153498A1 (zh) 大功率v型多缸柴油机系统
WO2019006527A1 (pt) Disposição construtiva em turbocompressor de baixa temperatura para motor de combustão interna
CN108317007B (zh) 大功率v型12缸柴油机
WO2019153497A1 (zh) 大功率v型16缸柴油机
WO2019153496A1 (zh) V型12缸柴油机
WO2019153499A1 (zh) V型多缸柴油机的机油供给系统
CN208168978U (zh) 大功率v型多缸柴油机系统
CN208040535U (zh) 大功率v型16缸柴油机
CN208122961U (zh) V型20缸柴油机
CN208330547U (zh) 大功率v型12缸柴油机
CN208203417U (zh) V型12缸柴油机
CN108457742A (zh) V型多缸柴油机的中冷器总成
CN108252801A (zh) V型20缸柴油机
CN204082333U (zh) 一种机械增压式内风冷水平对置发动机
CN207795394U (zh) V型多缸柴油机的中冷器总成
RU181354U1 (ru) Дизельный двигатель с рядным расположением цилиндров
US20140150740A1 (en) Method of Gas Distribution of Internal Combustion Engine
RU168451U1 (ru) Система питания воздухом комбинированного двигателя с глубоким охлаждением
CN208138049U (zh) V型16缸柴油机
CN220185237U (zh) 一种高功率密度的v型16缸发动机
RU225250U1 (ru) Система регистрового турбонаддува корабельного дизеля с дополнительным стабилизатором температуры
WO2019153500A1 (zh) V型多缸柴油机的中冷增压系统

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: 18904935

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18904935

Country of ref document: EP

Kind code of ref document: A1