WO2019153496A1 - V型12缸柴油机 - Google Patents

V型12缸柴油机 Download PDF

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Publication number
WO2019153496A1
WO2019153496A1 PCT/CN2018/083192 CN2018083192W WO2019153496A1 WO 2019153496 A1 WO2019153496 A1 WO 2019153496A1 CN 2018083192 W CN2018083192 W CN 2018083192W WO 2019153496 A1 WO2019153496 A1 WO 2019153496A1
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WO
WIPO (PCT)
Prior art keywords
oil
diesel
cylinder block
intercooler
cylinder
Prior art date
Application number
PCT/CN2018/083192
Other languages
English (en)
French (fr)
Inventor
黄永仲
黄第云
沈捷
李伟
Original Assignee
广西玉柴机器股份有限公司
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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
Priority to JP2020518114A priority Critical patent/JP6937900B2/ja
Priority to EP18905111.3A priority patent/EP3653857B1/en
Publication of WO2019153496A1 publication Critical patent/WO2019153496A1/zh

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    • 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
    • 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
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • 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
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/03—Mounting or connecting of lubricant purifying means relative to the machine or engine; Details of lubricant purifying means
    • 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
    • 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
    • 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
    • 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
    • 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
    • F01P2060/02—Intercooler
    • 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
    • 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
    • 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
    • F02B2075/1848—Number of cylinders twelve
    • 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 V-type 12-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 present invention provides a V-type 12-cylinder diesel engine comprising: a V-shaped cylinder block, wherein the V-shaped cylinder block is arranged with twelve rows of cylinder bores arranged in a V shape, and the two rows of cylinder bores The angle between the two is 60 degrees.
  • the V-shaped cylinder block on the outer side of the two cylinder bores is respectively cast with a sleeve corresponding to the number of cylinder bores; 12 individual cylinder heads respectively corresponding to the cylinder ports of the V-shaped cylinder block
  • the oil supply system includes a diesel tank, a fuel supply pipeline and 12 electric control unit pumps, and 12 electronic control unit pumps are respectively installed in the sleeve, and the 12 electronic control unit pumps are respectively used Controlling the injection of diesel into each cylinder, the diesel tank and the oil supply pipeline are connected.
  • the oil supply pipeline includes a left oil pipe and a right oil pipe, and the left oil pipe and the right oil pipe respectively pass a vertical high pressure oil pipe and 12 electric control monomers respectively.
  • the pump is connected; the air intake system is used to supply fresh air to the V-type 12-cylinder diesel engine; the lubrication system includes an oil pan, a pre-supply pump, an oil pump, an oil filter and an oil cooler, and the oil sump is provided At the bottom of the V-shaped cylinder block, the pre-supply pump is located on the front side of the oil pan, and the oil pump is provided.
  • the left and lower positions of the front end of the V-shaped cylinder block, the oil filter and the oil cooler are both disposed at the upper left position of the front end of the V-shaped cylinder block; and the cooling system includes a high temperature water circulation circuit and a low temperature water circulation circuit, and the low temperature water circulation circuit includes The rear radiator and the low temperature water pump, the low temperature water circulation circuit is used to cool 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 and 12 single 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 intake system includes a left intake manifold, a right intake manifold, a left booster, a right booster, a left intercooler, and a right intercooler, a left intercooler, and a right side
  • the coolers are respectively installed on both sides of the rear end of the V-shaped cylinder block, and the left supercharger and the right supercharger are correspondingly mounted above the left intercooler and the right intercooler and both protrude from the V-shaped cylinder
  • a left air cleaner is connected to the left supercharger
  • a right air cleaner is connected to the right supercharger
  • the left and right intake pipes are respectively connected to the left intercooler.
  • the upper end positions of the V-shaped cylinder block are arranged.
  • the cryopump is disposed at a position of the front end of the V-shaped cylinder block near the oil pump
  • the high temperature water pump is disposed at a position of the front end of the V-shaped cylinder block near the diesel distributor, the low temperature water pump, the high temperature water pump, the oil pump, and the diesel distributor
  • the crankshaft pulley drives the cryogenic water pump and the high temperature water pump respectively.
  • the coolant flowing through the V-shaped cylinder block and the 12 individual cylinder heads enters the front radiator, the water outlet manifold and the front radiator.
  • thermostats There are three thermostats connected in parallel, the thermostat is arranged in the upper right position of the front end of the V-shaped cylinder block, the thermostat is connected to the front radiator through the radiator water pipe, and the radiator water pipe is arranged in the V-shaped cylinder block. top.
  • the low temperature water circulation circuit comprises a low temperature water distributor fixed at a front end of the V-shaped cylinder block near the crank pulley, and the low temperature cooling water in the low temperature water pump is distributed to the oil cooler and the left side cold through the low temperature water distributor. And the right intercooler.
  • the left intercooler and the right intercooler are square housings, the inside of the square housing has an air circulation cavity, and the square housing around the air circulation cavity is provided with a coolant flow channel, and the square housing An additional housing is arranged on the front side, and an intermediate housing is arranged between the left intercooler and the right intercooler, and the two sides of the intermediate housing are respectively attached to the left intercooler and the right intercooler.
  • the inner end faces are connected together, and the additional casing and the intermediate casing are provided with a circulation passage communicating with the coolant flow passages inside the left intercooler and the right intercooler, and the water inlet and the outlet of the circulation passage are arranged in the middle On the front end surface of the casing, the water inlet and the water outlet are connected to the low temperature water distributor through a water pipe.
  • the diesel fuel supply system further comprises a diesel distributor, the diesel distributor is fixed at the front end of the V-shaped cylinder block, and the diesel fuel in the diesel tank is respectively connected to the left and right oil pipes through the diesel distributor, the left oil pipe and the right side
  • the diesel filter is respectively connected to the oil pipe, and the diesel filters on the left and right sides are respectively installed on both sides of the V-shaped cylinder block.
  • the diesel fuel supply system further comprises an oil pump and a diesel filter, the oil pump is connected between the diesel tank and the diesel filter, and the diesel filter is respectively connected with the left oil pipe and the right oil pipe, and the oil pump is fixed at the V
  • the fuel filter is fixed to the right side of the V-shaped cylinder block at the lower right end of the cylinder block.
  • the V-type 12-cylinder diesel engine has a stroke to bore ratio of 1.05-1.23.
  • the V-type 12-cylinder diesel engine has an adjacent cylinder center-to-bore ratio of 1.25-1.4.
  • the invention has the following beneficial effects: by providing a V-shaped cylinder block and 12 single cylinder heads, the diesel supply system realizes double-side oil supply, and the intake system is matched with two sets of supercharged intercoolers, and the compression is performed. After the air is cooled, the density is further increased, 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.
  • the engine is more fuel efficient and meets the requirements of high power and high torque of the V-type 12-cylinder diesel engine.
  • the body is more compact and has high strength.
  • FIG. 1 is a schematic structural view of a V-shaped cylinder block of a V-type 12-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 V-type 12-cylinder diesel engine according to the present invention
  • Figure 3 is a structural view of a whole machine of a V-type 12-cylinder diesel engine according to the present invention.
  • Figure 4 is a structural view of an oil supply line in a V-type 12-cylinder diesel engine according to the present invention.
  • Figure 5 is a structural view showing another oil supply line in a V-type 12-cylinder diesel engine according to the present invention.
  • FIG. 6 is a schematic diagram of a cooling system in a V-type 12-cylinder diesel engine in accordance with the present invention.
  • Figure 7 is a structural view of an intercooler in a V-type 12-cylinder diesel engine according to the present invention.
  • the present scheme proposes a V-type 12-cylinder diesel engine, from a cylinder assembly system, a power system, Fuel system, cooling system, and lubrication system are improved.
  • the electric control unit pump technology is adopted, the injection pressure is large, and the fuel injection amount can be accurately and dynamically adjusted to ensure that the diesel engine is well atomized under different load conditions, the combustion is sufficient, the transient speed regulation is good, the loading ability is strong, and the fuel consumption is low.
  • the minimum fuel consumption rate is 195g/kWh. It adopts one cylinder and one electric control unit pump.
  • the pressure at the pump end is large, the control is simple, and the injector with large injection pressure is equipped.
  • the atomization is good, the combustion is sufficient, the fuel consumption is low, and each unit pump has a correction code to ensure consistency.
  • Sex. The design of one cover per cylinder has a high cylinder head strength.
  • the cooling is separated by high and low temperature water, the two intercoolers and the oil cooler are cooled by the low temperature water, and the cylinder block and the cylinder head are cooled by the high temperature water.
  • the intake system, the lubrication system and the cooling system on the body the machine body is more compact while meeting the high strength, high power and large torque.
  • a V-type 12-cylinder diesel engine includes a V-shaped cylinder block 100, 12 single cylinder heads 200, a diesel supply system, an intake system, a lubricating system and a cooling system, wherein the V-shaped cylinder block 100 is provided with twelve rows of cylinder holes arranged in a V shape, and the angle between the two rows of cylinder bores of the V-shaped cylinder block 100 is 60 degrees, two columns A sleeve 101 corresponding to the number of cylinder bores is cast on the V-shaped cylinder block 100 outside the cylinder bore, and 12 individual cylinder heads 200 are respectively mounted on the cylinder ports of the V-shaped cylinder block 100.
  • the diesel fuel supply system includes 12 electric control unit pumps 14, a diesel tank and a fuel supply pipeline, and 12 electronic control unit pumps 14 are respectively installed in the sleeve 101, and the 12 electronic control unit pumps 14 are respectively used Controlling the injection of diesel into each cylinder, the diesel tank and the oil supply pipeline are connected.
  • This embodiment provides two specific oil supply pipelines (see below for details).
  • the oil supply pipeline includes a left oil pipe and a right oil pipe, and the left oil pipe and the right oil pipe are respectively connected by a vertical high pressure oil pipe and 12 electric control unit pumps.
  • the air intake system is used to supply fresh air to the V-type 12-cylinder diesel engine.
  • the lubrication system includes an oil pan, a pre-supply pump 7, an oil pump 5, an oil filter 2 and an oil cooler 1, the oil pan is disposed at the bottom of the V-shaped cylinder block 100, and the pre-supply pump 7 is disposed in the oil pan On the front side, the oil pump 5 is disposed at the lower left position of the front end of the V-shaped cylinder block 100, and the oil filter 2 and the oil cooler 1 are both disposed at the upper left position of the front end of the V-shaped cylinder block 100.
  • the cooling system includes a high temperature water circulation loop including a rear radiator and a low temperature water pump 4, a low temperature water circulation loop for cooling the oil cooler 1, and a high temperature water circulation loop including a front radiator and a high temperature water pump 9, high temperature water circulation
  • the circuit is used to cool the V-shaped cylinder block 100 and the 12 individual cylinder heads.
  • 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 present embodiment provides two specific diesel fuel supply systems, and FIG. 4 shows one of the diesel fuel supply pipelines.
  • the diesel fuel supply system includes 12 electronically controlled unit pumps 14.
  • the diesel fuel tank and the oil supply pipeline are respectively used for controlling the diesel fuel injected into each cylinder, and the diesel fuel tank and the oil supply pipeline are connected.
  • the oil supply pipeline includes a left oil pipe 43 and a right oil pipe 42.
  • the right oil pipe 42 and the left oil pipe 43 are respectively connected by a vertical high pressure oil pipe 46 and 12 electric control unit pumps, and the diesel fuel supply system further includes a diesel distributor 49 fixed to the V-shaped cylinder block 100.
  • the diesel fuel in the diesel tank is connected to the right oil pipe 42 and the left oil pipe 43 through the diesel distributor 49, and the diesel fuel filter is respectively connected to the right oil pipe 42 and the left oil pipe 43 respectively, and the diesel filters on the left and right sides are respectively connected.
  • the cleaners are respectively mounted on both sides of the V-shaped cylinder block 100 (see Fig. 3, showing the diesel filter 11 on the right side).
  • the oil pump 8 (see FIG. 3) pumps the diesel oil into the diesel distributor 49 through the oil delivery pipe 41, and the diesel fuel in the diesel distributor 49 is connected to the right oil pipe 42 and the left oil pipe 43 respectively.
  • the disconnected joint in the pipeline of the right oil pipe 42 and the left oil pipe 43 is connected to the corresponding diesel filter.
  • the right oil pipe 42 and the left oil pipe 43 are respectively connected to the corresponding electric control unit pump through the erected high pressure oil pipe 46 and the high pressure connection pipe 47, and the oil return of the electric control unit pump passes through the left return oil pipe 45 and the right return oil pipe respectively. 44 is returned to the relief valve and the relief valve is integrated into the diesel distributor 49. Further, the high pressure oil pipe 46 and the high pressure connection pipe 47 of the present embodiment are fixed to the positions of the cylinder heads on both sides of the V-shaped cylinder block 100 by the brackets 48.
  • FIG. 5 shows another diesel fuel supply line of the embodiment.
  • the diesel fuel supply system further includes an oil pump 8 and a diesel filter 11, and the oil pump 8 is connected to the diesel tank and the diesel oil. Between the filters 11, the diesel fuel in the diesel tank is input to the diesel filter 11 through the oil delivery pipe 31 through the oil delivery pump 8.
  • the diesel filter 11 has two outlets, which are respectively connected to the left oil pipe 32 and the right oil pipe 33.
  • the oil pump 8 is fixed to the lower right position of the front end of the V-shaped cylinder block 100 (see Fig. 3), the diesel filter 11 is fixed to the right side of the V-shaped cylinder block 100, and Fig. 3 shows the second diesel supply line.
  • the left oil pipe 32 and the right oil pipe 33 are respectively connected to the electric control unit pump through the erected high pressure oil pipe 36 and the high pressure connection pipe 37 respectively, and the oil return of the electric control unit pump passes through the left return oil pipe 35 and the right return oil pipe respectively. 34 is returned to the relief valve 39.
  • the high pressure oil pipe 36 and the high pressure connection pipe 37 of the present embodiment are fixed to the positions of the cylinder heads on both sides of the V-shaped cylinder block 100 by the brackets 38.
  • the intake manifold, supercharger, intercooler, air cleaner, and exhaust pipe appearing in FIG. 3 are partially labeled.
  • the intake system includes a left intake pipe, a right intake pipe 15, a left supercharger, a right supercharger 18, a left intercooler, and a right intercooler 16, a left intercooler, and a right side.
  • the coolers 16 are respectively mounted on both sides above the rear end of the V-shaped cylinder block 100, and the left side supercharger and the right side supercharger 18 are correspondingly mounted above the left intercooler and the right intercooler 16 and are both convex.
  • a left air cleaner is connected to the left supercharger, and a right air cleaner 17 is connected to the right supercharger 18, and the left intake pipe and the right intake pipe are connected.
  • 15 is respectively disposed at the upper end positions of both sides of the V-shaped cylinder block 100 after being connected to the left intercooler and the right intercooler 16.
  • a vortex rear exhaust pipe 19 is disposed on the left supercharger, and a vortex rear exhaust pipe is also disposed on the right supercharger 18.
  • the V-type 12-cylinder diesel engine also includes a corresponding exhaust system
  • the exhaust system includes an exhaust pipe 21 (two left and right), the exhaust pipe 21 (two left and right) corresponding to the left supercharger and the right
  • the side supercharger is connected, and the exhaust pipe 21 (two left and right) is disposed at the top intermediate position of the V-shaped cylinder block 100.
  • the cryopump 4 is disposed at a position near the front end of the V-shaped cylinder block 100 near the oil pump 5, the high temperature water pump 9 is disposed at the front end of the V-shaped cylinder block 100, and the high temperature water pump 9 and the cryogenic water pump 4 are respectively located at the crankshaft.
  • the low temperature water pump 4, the high temperature water pump 9, the oil pump 5 and the oil pump 8 are arranged around the crank pulley (the silicone shock absorber 6 is arranged on the crank pulley), and the crank pulley drives the low temperature water pump 4 and the high temperature water pump 9, respectively.
  • the coolant flowing through the V-shaped cylinder block 100 and the 12 individual cylinder heads 200 enters the front radiator 242 through the water outlet manifold, and three parallel thermostats 23 are connected between the water outlet manifold and the front radiator 242.
  • the warmer 23 is disposed at a right upper position of the front end of the V-shaped cylinder block 100, and the thermostat 23 communicates with the front radiator 242 through the radiator water pipe 20, and the radiator water pipe 20 is disposed at the top of the V-shaped cylinder block 100.
  • the low temperature water circulation circuit includes a low temperature water distributor 3 fixed to a position above the front end of the V-shaped cylinder block 100 near the crank pulley, and a low temperature water distributor 3 is provided.
  • the purpose is that the low temperature water circuit can simultaneously cool the oil cooler 1 and the two intercoolers. So far, as shown in FIG. 6, the present embodiment proposes separate cooling with high and low temperature water, low temperature water cooling of two intercoolers and oil cooler 1, high temperature water cooling cylinder block and cylinder head, and the cooling system belongs to a forced closed cycle.
  • the coolant should be anti-freeze and anti-rust coolant.
  • 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. 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 cryogenic water pump cools the two intercoolers and the oil cooler and then returns to the radiator 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 present embodiment provides a specific intercooler structure.
  • the left intercooler and the right intercooler are square housings 501, and the interior of the square housing 501 has The air circulation cavity is provided with a coolant flow passage in a square casing around the air circulation cavity, and the front side of the square casing 501 is provided with an additional casing 502, and a left intercooler and a right intercooler are disposed between The intermediate casing 503, the two sides of the intermediate casing 503 are respectively connected with the inner end faces of the additional casing 502 of the left intercooler and the right intercooler, and the additional casing 502 and the intermediate casing 503 are provided with A circulation passage communicating with the coolant flow passage inside the left intercooler and the right intercooler, a water inlet 504 and a water outlet 505 of the circulation passage are disposed on the front end surface of the intermediate casing 503, the water inlet 504 and the water outlet 505
  • the water pipe is connected to the low temperature water distributor
  • the existing exhaust gas turbocharging technology is adopted.
  • exhaust from the engine exhaust pipe enters the turbine, and heat in the exhaust pressure 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 manifold through the conduit, and the cooled and expanded exhaust gases exiting the turbine are directed by the turbine casing to the engine exhaust system and into 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 ECU 10 is attached to the right side of the V-shaped cylinder block 100 of the present embodiment, and the oil port 12 and the starter motor 13 are added.
  • the V-type 12-cylinder diesel engine has a stroke to cylinder 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 V-type 12-cylinder diesel engine 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 V-type 12-cylinder diesel engine of the present embodiment is provided with a V-shaped cylinder block 100 and 12 individual cylinder heads 200, and the diesel supply system realizes double-side oil supply, and the intake system is provided with two sets of supercharged intercoolers.
  • the compressed air is cooled to further increase the density, which 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 are classified and cooled, which can reduce the intake air temperature and oil temperature, and reduce the heat loss.
  • the engine is more fuel efficient 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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Abstract

一种V型12缸柴油机，包括V形气缸体（100）和12个单体气缸盖（200）；油供给系统，包括左侧油管（43）和右侧油管（42），左侧油管（43）和右侧油管（42）分别通过竖向的高压油管（46）和12个电控单体泵对应连接；进气系统，用来给V型12缸柴油机供新鲜空气；润滑系统；以及冷却系统，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（4），低温水循环回路用来冷却机油冷却器（1），高温水循环回路包括前排散热器（242）和高温水泵（9），高温水循环回路用来冷却V形气缸体（100）和12个单体气缸盖（200）。机体紧凑、功率高、扭矩大。

Description

V型12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201810123071.9、发明名称为“V型12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V型12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V型12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V型12缸柴油机，包括：V形气缸体，该V形气缸体上布置有12个呈V形排列的两列气缸孔，该两列气缸孔之间的夹角为60度，两列气缸孔外侧的V形气缸体上分别铸造有与缸孔数目对应的套筒；12个单体气缸盖，其分别对应安装在V形气缸体的缸口部位；油供给系统，其包括柴油箱、供油管路和12个电控单体泵，12个电控单体泵分别对应安装在套筒内，该12个电控单 体泵分别用来控制给每缸喷射柴油，柴油箱和供油管路连通，供油管路包括左侧油管和右侧油管，左侧油管和右侧油管分别通过竖向的高压油管和12个电控单体泵对应连接；进气系统，其用来给V型12缸柴油机供新鲜空气；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，机油滤清器和机油冷却器均设在V形气缸体的前端的左上方位置；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，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12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，进气系统包括左侧进气管、右侧进气管、左侧增压器、右侧增压器、左侧中冷器和右侧中冷器，左侧中冷器和右侧中冷器分别安装在V形气缸体后端上方的两侧，左侧增压器和右侧增压器对应安装在左侧中冷器和右侧中冷器的上方且均凸出V形气缸体的顶部，左侧增压器上连接有左侧空气滤清器，右侧增压器上连接有右侧空气滤清器，左侧进气管和右侧进气管分别与左侧中冷器和右侧中冷器接通后布置在V形气缸体的两侧上端位置。
优选地，低温水泵设置在V形气缸体的前端靠近机油泵上方的位置，高温水泵设置在V形气缸体的前端靠近柴油分配器上方的位置，低温水泵、高温水泵、机油泵和柴油分配器围绕在曲轴皮带轮的四周，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12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三个并联的节温器，节温器设置在V形气缸体的前端的右上方位置，节温器通过散热器水管与前排散热器连通，散热器水管布置在V形气缸体的顶部。
优选地，低温水循环回路包括低温水分配器，低温水分配器固定在V形气缸体的前端靠近曲轴皮带轮上方的位置，低温水泵内的低温冷却水经低温水分配器分配给机油冷却器和左侧中冷器与右侧中冷器。
优选地，左侧中冷器和右侧中冷器为方形壳体，方形壳体的内部具有空气流通腔体，空气流通腔体周围的方形壳体内设有冷却液流道，方形壳体的前侧设有附加壳体，左侧中冷器和右侧中冷器之间设有中间壳体，中间壳体的两侧分别与左侧中冷器和右侧中冷器的附加壳体的内侧端面连接在一起，附加壳体和中间壳体内设有与左侧中冷器和右侧中冷器内部的冷却液流道连通的循环通道，循环通道的进水口和出水口设置在中间壳体的前端面上，进水口和出水口通过水管与低温水分配器接通。
优选地，柴油供给系统还包括柴油分配器，柴油分配器固定在V形气缸体的前端，柴油箱内的柴油经过柴油分配器分别与左侧油管和右侧油管连通，左侧油管和右侧油管中分别接入柴油滤清器，左右两侧的柴油滤清器分别安装在V形气缸体的两侧。
优选地，柴油供给系统还包括输油泵和柴油滤清器，输油泵接入柴油箱和柴油滤清器之间，柴油滤清器分别与左侧油管和右侧油管连通，输油泵固定在V形气缸体的前端右下方位置，柴油滤清器固定在V形气缸体的右侧。
优选地，该V型12缸柴油机的冲程与缸径比值为1.05-1.23。
优选地，该V型12缸柴油机的相邻气缸中心距与缸径比值为1.25-1.4。
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、12个单体气缸盖，柴油供给系统实现双侧供油，进气系统配套两套增压中冷器，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V型12缸柴油机高功率、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V型12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V型12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V型12缸柴油机的一种整机结构图；
图4是根据本发明的V型12缸柴油机中一种供油管路的结构图；
图5是根据本发明的V型12缸柴油机中另一种供油管路的结构图；
图6是根据本发明的V型12缸柴油机中冷却系统的原理图；
图7是根据本发明的V型12缸柴油机中中冷器的结构图。
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。
根据本发明具体实施方式的一种V型12缸柴油机，为了满足大功率高速柴油机高功率、大扭矩的要求，本方案提出一种V型12缸柴油机，从缸体总成系统、动力系统、燃油系统、冷却系统、润滑系统进行改进。采用电控单体泵技术，喷射压力大，能精确动态调整喷油量，保证柴油机在不同负荷的情况下，雾化好，燃烧充分，瞬态调速性好，加载能力强，油耗低，最低燃油消耗率达到195g/kW h。采用一缸一个电控单体泵，泵端压力大，控制简单，配上喷射压力大的喷油器，雾化好，燃烧充分，油耗低，每个单体泵均带修正码，确保一致性。每缸一盖的设计，缸盖强度高。采用高低温水分开冷却，低温水冷却两个中冷器、机油冷却器，高温水冷却气缸体与气缸盖。以及柴油供给系统、进气系统、润滑系统和冷却系统在机体上的合理布置，满足强度大、功率高、扭矩大的同时，机体更加紧凑。
具体地，如图1至图3所示，根据本发明具体实施方式的一种V型12缸柴油机，包括V形气缸体100、12个单体气缸盖200、柴油供给系统、进气系统、润滑系统和冷却系统，其中该V形气缸体100上布置有12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60度，两列气缸孔外侧的V形气缸体100上分别铸造有与缸孔数目对应的套筒101，12个单体气缸盖200分别对应安装在V形气缸体100的缸口部位。柴油供给系统包括12个电控单体泵14、柴油箱和供油管路，12个电控单体泵14分别对应安装在套筒101内，该12个电控单体泵14分别用来控 制给每缸喷射柴油，柴油箱和供油管路连通，本实施例提供两种具体的供油管路(详细见下文)。总的来讲，供油管路包括左侧油管和右侧油管，左侧油管和右侧油管分别通过竖向的高压油管和12个电控单体泵对应连接。进气系统用来给V型12缸柴油机供新鲜空气。润滑系统包括油底壳、预供油泵7、机油泵5、机油滤清器2和机油冷却器1，油底壳设在V形气缸体100的底部，预供油泵7设在油底壳的前侧，机油泵5设在V形气缸体100的前端左下方位置，机油滤清器2和机油冷却器1均设在V形气缸体100的前端的左上方位置。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4，低温水循环回路用来冷却机油冷却器1，高温水循环回路包括前排散热器和高温水泵9，高温水循环回路用来冷却V形气缸体100和12个单体气缸盖。
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。
如图4和图5所示，本实施例提供了两种具体的柴油供给系统，图4示出其中一种柴油供给管路，结合图3，柴油供给系统包括12个电控单体泵14、柴油箱和供油管路，12个电控单体泵14分别用来控制给每缸喷射柴油，柴油箱和供油管路连通，供油管路包括左侧油管43和右侧油管42，右侧油管42和左侧油管43分别通过竖向的高压油管46和12个电控单体泵对应连接，柴油供给系统还包括柴油分配器49，柴油分配器49固定在V形气缸体100的前端，柴油箱内的柴油经过柴油分配器49分别与右侧油管42和左侧油管43连通，右侧油管42和左侧油管43中分别接入柴油滤清器，左右两侧的柴油滤清器分别安装在V形气缸体100的两侧(参见图3，示出右侧的柴油滤清器11)。此柴油供给管路中，输油泵8(参见图3)通过输油管41将柴油泵入柴油分配器49，柴油分配器49内的柴油分两支分别与右侧油管42和左侧油管43接通，参见图4，右侧油管42和左侧油管43的管路中断开的接头接入对应的柴油滤清器。右侧油管42和左侧油管43分别通过竖立的高压油管46和高压接管47与对应的电控单体泵连接，电控单体泵的回油分别通过左侧回油管45和右侧回油管44回流到溢流阀内，溢流阀集成在柴油分配器49内。另外，本实施例的高压油管46和高压接管47通过支架48固定在V形气缸体100的两侧靠近缸盖的位置。
如图5所示，图5示出本实施例的另一种柴油供给管路，结合图3，柴油供给系统还包括输油泵8和柴油滤清器11，输油泵8接入柴油箱和柴油滤清器11之间，柴油箱内的柴油通过输油泵8经输油管31输入柴油滤清器11，柴油滤清器11具有两个出口，分别与左侧油管32和右侧油管33连通，输油泵8固定在V形气缸体100的前端右下方位置(参见图3)，柴油滤清器11固定在V形气缸体100的右侧，图3示出第二种柴油供给管路。左侧油管32和右侧油管33分别通过竖立的高压油管36和高压接管37分别对应与电控单体泵连接，电控单体泵的回油分别通过左侧回油管35和右侧回油管34回流到溢流阀39内。另外，本实施例的高压油管36和高压接管37通过支架38固定在V形气缸体100的两侧靠近缸盖的位置。
作为一种优选实施例，如图3所示，图3中对成出现的进气管、增压器、中冷器、空气滤清器以及排气管进行局部标注。进气系统包括左侧进气管、右侧进气管15、左侧增压器、右侧增压器18、左侧中冷器和右侧中冷器16，左侧中冷器和右侧中冷器16分别安装在V形气缸体100后端上方的两侧，左侧增压器和右侧增压器18对应安装在左侧中冷器和右侧中冷器16的上方且均凸出V形气缸体100的顶部，左侧增压器上连接有左侧空气滤清器，右侧增压器18上连接有右侧空气滤清器17，左侧进气管和右侧进气管15分别与左侧中冷器和右侧中冷器16接通后布置在V形气缸体100的两侧上端位置。另外，左侧增压器上设有涡后排气管19，右侧增压器18上也设有涡后排气管。实际上，该V型12缸柴油机还包括相应的排气系统，排气系统包括排气管21(左右两根)，排气管21(左右两根)对应的与左侧增压器和右侧增压器连接，排气管21(左右两根)布置在V形气缸体100的顶部中间位置。
作为一种优选实施例，低温水泵4设置在V形气缸体100的前端靠近机油泵5上方的位置，高温水泵9设置在V形气缸体100的前端，高温水泵9和低温水泵4分别处于曲轴皮带轮的上方两侧，低温水泵4、高温水泵9、机油泵5和输油泵8围绕在曲轴皮带轮的四周(曲轴皮带轮上设置硅胶减震器6)，曲轴皮带轮分别驱动低温水泵4和高温水泵9，流经V形气缸体100和12个单体气缸盖200的冷却液经出水总管进入前排散热器242，出水总管和前排散热器242之间连接有三个并联的节温器23，节温器23设置在V形气缸体100的前端的右上方位置，节温器23通过散热器水管20与前排散热器242连通，散热器水管20布置在V形气缸体100的顶部。
如图3和图6所示，作为一种优选实施例，低温水循环回路包括低温水分配器3，低温水分配器3固定在V形气缸体100的前端靠近曲轴皮带轮上方的位置，设置低温 水分配器3的目的就是，低温水循环回路可以同时冷却机油冷却器1和两个中冷器。至此，如图6所示，本实施例提出的采用高低温水分开冷却，低温水冷却两个中冷器和机油冷却器1，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，低温水冷却两个中冷器、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。低温水泵则冷却两个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。
如图7所示，作为一种优选实施例，本实施例提出一种具体的中冷器结构，左侧中冷器和右侧中冷器为方形壳体501，方形壳体501的内部具有空气流通腔体，空气流通腔体周围的方形壳体内设有冷却液流道，方形壳体501的前侧设有附加壳体502，左侧中冷器和右侧中冷器之间设有中间壳体503，中间壳体503的两侧分别与左侧中冷器和右侧中冷器的附加壳体502的内侧端面连接在一起，附加壳体502和中间壳体503内设有与左侧中冷器和右侧中冷器内部的冷却液流道连通的循环通道，循环通道的进水口504和出水口505设置在中间壳体503的前端面上，进水口504和出水口505通过水管与低温水分配器接通，进而实现低温水泵内4的低温冷却水经低温水分配器3分配给机油冷却器1和左侧中冷器与右侧中冷器16。
上述方案中，采用现有的废气涡轮增压技术。通过左右各有一套独立的增压中冷系统。增压发动机工作时，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引向发动机排气系统并进入大气。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。
补充说明：本实施例的V形气缸体100的右侧还安装有ECU10，加机油口12和启动电机13。
作为一种优选实施例，该V型12缸柴油机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，该V型12缸柴油机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V型12缸柴油机，通过设置V形气缸体100、12个单体气缸盖200，柴油供给系统实现双侧供油，进气系统配套两套增压中冷器，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 (10)

  1. 一种V型12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12个呈V形排列的两列气缸孔，该两列气缸孔之间的夹角为60度，所述两列气缸孔外侧的V形气缸体上分别铸造有与缸孔数目对应的套筒；
    12个单体气缸盖，其分别对应安装在所述V形气缸体的缸口部位；
    柴油供给系统，其包括柴油箱、供油管路和12个电控单体泵，所述12个电控单体泵分别对应安装在所述套筒内，该12个电控单体泵分别用来控制给每缸喷射柴油，所述柴油箱和所述供油管路连通，所述供油管路包括左侧油管和右侧油管，所述左侧油管和所述右侧油管分别通过竖向的高压油管和所述12个电控单体泵对应连接；
    进气系统，其用来给所述V型12缸柴油机供新鲜空气；
    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，所述机油滤清器和所述机油冷却器均设在所述V形气缸体的前端的左上方位置；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，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12个单体气缸盖。
  2. 根据权利要求1所述的V型12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V型12缸柴油机，其特征在于，所述进气系统包括左侧进气管、右侧进气管、左侧增压器、右侧增压器、左侧中冷器和右侧中冷器，所述左侧中冷器和所述右侧中冷器分别安装在所述V形气缸体后端上方的两侧，所述左侧 增压器和所述右侧增压器对应安装在所述左侧中冷器和所述右侧中冷器的上方且均凸出所述V形气缸体的顶部，所述左侧增压器上连接有左侧空气滤清器，所述右侧增压器上连接有右侧空气滤清器，所述左侧进气管和所述右侧进气管分别与所述左侧中冷器和所述右侧中冷器接通后布置在所述V形气缸体的两侧上端位置。
  4. 根据权利要求3所述的V型12缸柴油机，其特征在于，所述低温水泵设置在所述V形气缸体的前端靠近所述机油泵上方的位置，所述高温水泵设置在所述V形气缸体的前端靠近所述柴油分配器上方的位置，所述低温水泵、所述高温水泵、所述机油泵和所述柴油分配器围绕在曲轴皮带轮的四周，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12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三个并联的节温器，所述节温器设置在所述V形气缸体的前端的右上方位置，所述节温器通过散热器水管与所述前排散热器连通，所述散热器水管布置在所述V形气缸体的顶部。
  5. 根据权利要求4所述的V型12缸柴油机，其特征在于，所述低温水循环回路包括低温水分配器，所述低温水分配器固定在所述V形气缸体的前端靠近所述曲轴皮带轮上方的位置，所述低温水泵内的低温冷却水经所述低温水分配器分配给所述机油冷却器和所述左侧中冷器与所述右侧中冷器。
  6. 根据权利要求5所述的V型12缸柴油机，其特征在于，所述左侧中冷器和所述右侧中冷器为方形壳体，所述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方形壳体内设有冷却液流道，所述方形壳体的前侧设有附加壳体，所述左侧中冷器和所述右侧中冷器之间设有中间壳体，所述中间壳体的两侧分别与所述左侧中冷器和所述右侧中冷器的附加壳体的内侧端面连接在一起，所述附加壳体和所述中间壳体内设有与所述左侧中冷器和所述右侧中冷器内部的冷却液流道连通的循环通道，所述循环通道的进水口和出水口设置在所述中间壳体的前端面上，所述进水口和所述出水口通过水管与所述低温水分配器接通。
  7. 根据权利要求1所述的V型12缸柴油机，其特征在于，所述柴油供给系统还包括柴油分配器，所述柴油分配器固定在所述V形气缸体的前端，所述柴油箱内的柴油经过所述柴油分配器分别与所述左侧油管和所述右侧油管连通，所述左侧油管和所 述右侧油管中分别接入柴油滤清器，左右两侧的柴油滤清器分别安装在所述V形气缸体的两侧。
  8. 根据权利要求1所述的V型12缸柴油机，其特征在于，所述柴油供给系统还包括输油泵和柴油滤清器，所述输油泵接入所述柴油箱和所述柴油滤清器之间，所述柴油滤清器分别与所述左侧油管和所述右侧油管连通，所述输油泵固定在所述V形气缸体的前端右下方位置，所述柴油滤清器固定在所述V形气缸体的右侧。
  9. 根据权利要求1所述的V型12缸柴油机，其特征在于，该V型12缸柴油机的冲程与缸径比值为1.05-1.23。
  10. 根据权利要求1所述的V型12缸柴油机，其特征在于，该V型12缸柴油机的相邻气缸中心距与缸径比值为1.25-1.4。
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JP2020522646A (ja) 2020-07-30
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