CN108194198B - High-power V-shaped 16-cylinder diesel engine - Google Patents
High-power V-shaped 16-cylinder diesel engine Download PDFInfo
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- CN108194198B CN108194198B CN201810122575.9A CN201810122575A CN108194198B CN 108194198 B CN108194198 B CN 108194198B CN 201810122575 A CN201810122575 A CN 201810122575A CN 108194198 B CN108194198 B CN 108194198B
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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
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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
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- 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
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- 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
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- 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
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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
- 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
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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
- 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
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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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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- 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
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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
- F02B2075/1804—Number of cylinders
- F02B2075/1864—Number of cylinders sixteen
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- 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
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- Lubrication Of Internal Combustion Engines (AREA)
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Abstract
The invention discloses a high-power V-shaped 16-cylinder diesel engine, which comprises a V-shaped cylinder body and 16 single cylinder covers, wherein the single cylinder covers are arranged on the V-shaped cylinder body; an intake system including four turbochargers and an intercooler; a lubrication system including an oil cooler; and a cooling system including a high-temperature water circulation circuit for cooling the oil cooler and the intercooler, and a low-temperature water circulation circuit including a front radiator and a high-temperature water pump for cooling the V-shaped cylinder block and the 16 single cylinder heads. The engine body is compact, high in power and large in torque.
Description
Technical Field
The invention relates to the field of engines, in particular to a high-power V-shaped 16-cylinder diesel engine.
Background
High-power high-speed diesel engines are generally used in generator stations, petrochemical industry, high-speed light ships, naval vessels and the like. The high-power high-speed diesel engine basically adopts a four-stroke engine, and the high-power high-speed diesel engine requires very high single-engine power, so that the high-load requirement is higher than that of a common diesel engine, the average effective pressure of the high-power high-speed diesel engine can reach 3MPa, and the highest detonation pressure of the high-power high-speed diesel engine can reach 20 MPa. Because the high-power high-speed diesel engine is required to have the characteristics of high power and large torque, the high-power high-speed diesel engine has higher requirements on several important key systems, such as a cylinder assembly system, a power system, a diesel oil system, a cooling system, a lubricating system and the like.
The information disclosed in this background section is only for enhancement of understanding of the general background of the invention and should not be taken as an acknowledgement or any form of suggestion that this information forms the prior art already known to a person skilled in the art.
Disclosure of Invention
The invention aims to provide a high-power V-shaped 16-cylinder diesel engine which is compact in body, high in power and large in torque.
In order to achieve the above object, the present invention provides a high power V-type 16-cylinder diesel engine, comprising: the cylinder block comprises a V-shaped cylinder block, wherein 16 two rows of cylinder holes are arranged in a V shape, and an included angle between the two rows of cylinder holes is 90 degrees; 16 single cylinder heads which are respectively correspondingly arranged at the cylinder port parts of two rows of cylinder holes; the air inlet system comprises four turbochargers and an intercooler, the four turbochargers are respectively fixed above a single cylinder cover through a bracket and are arranged in a rectangular array, a compressor of each turbocharger is positioned at the outer side, a turbine of each turbocharger is positioned at the inner side, the compressor of each turbocharger is connected with an air filter which is erected upwards, the turbine of each turbocharger is connected with an exhaust pipe and converges towards the central positions of the four turbochargers to form an exhaust gas outlet, the intercooler is fixed at the upper position of the rear end of the V-shaped cylinder body, the compressor of each turbocharger is communicated with the intercooler through an air pipe, two sides of the bottom of the intercooler are respectively provided with air outlets, and the two air outlets are respectively connected with an air inlet pipe; the lubricating system comprises an oil pan, a pre-oil supply pump, an oil filter and an oil cooler, wherein the oil pan is arranged at the bottom of the V-shaped cylinder body, the pre-oil supply pump is arranged at the front side of the oil pan, the oil pump is arranged at the left lower position of the front end of the V-shaped cylinder body, the oil cooler is arranged at the left upper position of the front end of the V-shaped cylinder body, the oil filter is arranged at the right upper position of the front end of the V-shaped cylinder body, the oil in the oil pan is input into the oil cooler through the pre-oil supply pump and the oil pump, the oil cooler is connected with the oil filter through an oil pipe, and the oil outlet of the oil filter is communicated with a main oil duct of the V-shaped cylinder body; and the cooling system comprises a high-temperature water circulation loop and a low-temperature water circulation loop, the low-temperature water circulation loop comprises a rear-row radiator and a low-temperature water pump, the low-temperature water circulation loop is used for cooling the engine oil cooler and the intercooler, the high-temperature water circulation loop comprises a front-row radiator and a high-temperature water pump, and the high-temperature water circulation loop is used for cooling the V-shaped cylinder block and the 16 single cylinder covers.
Preferably, pistons with W combustion chambers are arranged in the two rows of cylinder holes of the V-shaped cylinder block, an inner cooling oil channel is arranged inside the pistons, and four ring grooves are formed in the circumferential wall of the pistons.
Preferably, the high-temperature water pump and the low-temperature water pump are arranged on two sides above a crankshaft pulley at the front end of the V-shaped cylinder block, the crankshaft pulley drives the low-temperature water pump and the high-temperature water pump respectively, cooling liquid flowing through the V-shaped cylinder block and the 16 single cylinder heads enters the front-row radiator through a water outlet header pipe, a thermostat is connected between the water outlet header pipe and the front-row radiator, and the thermostat is arranged on the V-shaped cylinder block on the rear side of the oil cooler.
Preferably, the intercooler is a rectangular housing, an air circulation cavity is arranged inside the rectangular housing, a cooling liquid channel is arranged in the rectangular housing around the air circulation cavity, and the low-temperature water circulation loop is communicated with the cooling liquid channel in the rectangular housing.
Preferably, the ratio of the stroke to the cylinder diameter of the high-power V-shaped 16-cylinder diesel engine is 1.1-1.3.
Preferably, the ratio of the center distance between adjacent cylinders to the diameter of the adjacent cylinders of the high-power V-shaped 16-cylinder diesel engine is 1.3-1.45.
Compared with the prior art, the invention has the following beneficial effects: through setting up V-arrangement cylinder block, 16 monomer cylinder heads, four superchargers and an intercooler, compressed air makes its density further improve through the cooling, is favorable to improving the power of engine, improves the performance, and cooling system adopts high low temperature moisture to open the cooling, and high temperature and low temperature part classification cooling like this can reduce inlet air temperature and machine oil temperature, reduces the heat energy loss simultaneously, and the engine is more fuel-efficient, satisfies the requirement of high power high speed diesel engine high power, big moment of torsion, and the organism is compacter, and intensity is big.
Drawings
FIG. 1 is a schematic view of a V-block configuration for a high power V-type 16 cylinder diesel engine according to the present invention;
FIG. 2 is a schematic structural diagram of a single cylinder head arranged on a V-shaped cylinder block of a high-power V-shaped 16-cylinder diesel engine according to the invention;
FIG. 3 is a front view of a high power V-type 16 cylinder diesel engine according to the present invention;
FIG. 4 is a left side view of a high power V-type 16 cylinder diesel engine according to the present invention;
FIG. 5 is a right side view of a high power V-type 16 cylinder diesel engine according to the present invention;
FIG. 6 is a top view of a high power V-type 16 cylinder diesel engine according to the present invention;
fig. 7 is a schematic diagram of a cooling system of a high power V-type 16 cylinder diesel engine according to the present invention.
Detailed Description
The following detailed description of the present invention is provided in conjunction with the accompanying drawings, but it should be understood that the scope of the present invention is not limited to the specific embodiments.
Throughout the specification and claims, unless explicitly stated otherwise, the word "comprise", or variations such as "comprises" or "comprising", will be understood to imply the inclusion of a stated element or component but not the exclusion of any other element or component.
As shown in fig. 1 to 2, a high-power V-type 16-cylinder diesel engine according to an embodiment of the present invention includes a V-shaped cylinder block 100 and 16 single cylinder heads 200, wherein 16 two rows of cylinder bores are arranged in a V-shape on the V-shaped cylinder block 100, an included angle between the two rows of cylinder bores of the V-shaped cylinder block 100 is 90 degrees, and the 16 single cylinder heads 200 are respectively mounted on the V-shaped cylinder block 100 at the cylinder port locations of the two rows of cylinder bores. The high-power V-shaped 16-cylinder diesel engine also comprises an air inlet system, the air inlet system comprises four turbochargers 2 and an intercooler 1, the four turbochargers 2 are respectively fixed above a single cylinder cover 200 through brackets and are arranged in a rectangular array (see figure 6), the air compressor of each turbocharger 2 is arranged at the outer side, the turbine of each turbocharger 2 is arranged at the inner side, the air compressor of each turbocharger 2 is connected with an air filter which is erected upwards, the turbine of each turbocharger 2 is connected with an exhaust pipe and converged towards the central positions of the four turbochargers 2 to form an exhaust gas outlet 3 (see figure 6), the intercooler 1 is fixed at the rear end of the V-shaped cylinder block 100, the air compressor of each turbocharger 2 is communicated with the intercooler 1 through an air pipe, and air outlets are respectively arranged on two sides of the bottom of the intercooler 1, the two air outlets are respectively connected with an air inlet pipe 6, the lubricating system comprises an oil pan 5, a pre-oil supply pump 9, an oil pump 8, an oil filter 10 and an oil cooler 4, the oil pan 5 is arranged at the bottom of the V-shaped cylinder block 100, the pre-oil supply pump 9 is arranged at the front side of the oil pan 5, the oil pump 8 is arranged at the left lower position of the front end of the V-shaped cylinder block 100, the oil cooler 4 is arranged at the left upper position of the front end of the V-shaped cylinder block 100, the oil filter 10 is arranged at the right upper position of the front end of the V-shaped cylinder block 100, oil in the oil pan 5 is input into the oil cooler 4 through the pre-oil supply pump 9 and the oil pump 8, the oil cooler 4 is connected with the oil filter 10 through an oil pipe, and an oil outlet of the oil filter 10 is communicated with a main oil duct of the V-shaped cylinder block 100. The cooling system comprises a high-temperature water circulation loop and a low-temperature water circulation loop, the low-temperature water circulation loop comprises a rear radiator and a low-temperature water pump 7, the low-temperature water circulation loop is used for cooling the oil cooler 4 and the intercooler 1, the high-temperature water circulation loop comprises a front radiator and a high-temperature water pump 6, and the high-temperature water circulation loop is used for cooling the V-shaped cylinder block 100 and the 16 single cylinder heads 200.
In the above scheme, the design of one cover for each cylinder has high strength of the cylinder cover. The cooling system comprises a high-temperature water circulation loop and a low-temperature water circulation loop, the low-temperature water circulation loop comprises a rear-row radiator and a low-temperature water pump, the low-temperature water circulation loop is used for cooling the engine oil cooler, the high-temperature water circulation loop comprises a front-row radiator and the high-temperature water pump, the high-temperature water circulation loop is used for cooling the V-shaped cylinder block 100 and the 16 single cylinder covers 200, the high-temperature water and low-temperature water are used for cooling the intercooler and the engine oil cooler in an open mode, the high-temperature water cools the cylinder block and the cylinder covers, the air inlet temperature and the engine oil temperature can be reduced, meanwhile, the heat energy loss is reduced, and the engine saves oil. The engine adopts the existing exhaust gas turbocharging technology, a supercharging and intercooling system is formed by arranging four independent superchargers and an intercooler, when the engine works, exhaust gas from an exhaust pipe of the engine enters a turbine, heat energy in the pressure of the exhaust gas enables the turbine to rotate, and a compressor which is coaxial with the turbine rotates. The compressor draws in and compresses air which then enters the engine intake through a conduit and the cooled and expanded exhaust gases leaving the turbine are directed centrally from the turbine housing to the exhaust outlet 3 at the central location of the supercharger into the atmosphere. After the intake air is compressed, the density of the air charged into the cylinder is improved, more fuel can be fully combusted under the good matching of an oil supply system, the power is improved, and the economical efficiency is improved. The included angle between two rows of cylinder holes of the V-shaped cylinder block 100 is 90 degrees, so that the ignition interval angle of each cylinder is 45 degrees, and the ignition is uniform.
In a preferred embodiment, pistons with W combustion chambers are arranged in two rows of cylinder bores of the V-shaped cylinder block 100, internal cooling oil passages are arranged in the pistons, and four ring grooves are arranged on the circumferential wall of the pistons. In the scheme, the W combustion chamber technology is adopted, so that the air inflow is large, the mixing is uniform, the combustion is more sufficient, and the power range area with low oil consumption is wide. The piston adopts an inner cooling oil duct structure, so that the cooling is good, the four-ring groove structure is adopted, and the sealing effect is better.
As a preferred embodiment, as shown in fig. 5, the high temperature water pump 6 and the low temperature water pump 7 are disposed on both sides above a front end crank pulley of the V-shaped cylinder block 100, the crank pulley drives the low temperature water pump 7 and the high temperature water pump 6, respectively, the coolant flowing through the V-shaped cylinder block 100 and the 16 unit cylinder heads 200 enters a front radiator through a water outlet header, and a thermostat is connected between the water outlet header and the front radiator, and the thermostat is disposed on the V-shaped cylinder block 100 on the rear side of the oil cooler 4.
As a preferred embodiment, the intercooler 1 is a rectangular housing, an air circulation cavity is provided inside the rectangular housing, a coolant flow passage is provided in the rectangular housing around the air circulation cavity, and the low-temperature water circulation loop is communicated with the coolant flow passage in the rectangular housing. In this scheme, can set up low temperature water distributor among the low temperature water circulation circuit, low temperature water distributor can be fixed in the front end of V-arrangement cylinder block and be close to the position above the crank pulley, and the purpose of setting up low temperature water distributor is, and low temperature water circulation circuit can cool off oil cooler and intercooler simultaneously.
As shown in fig. 7, the present embodiment proposes a high-low temperature water split cooling, a low-temperature water cooling intercooler and an engine oil cooler, the high-temperature water cools the cylinder block and the cylinder head, the cooling system belongs to a forced closed type circulating water cooling system, and the coolant should be an anti-freezing and anti-rust coolant. High-temperature water and low-temperature water are used for cooling, a low-temperature water cools an intercooler and an engine oil cooler, the cylinder body and the cylinder cover are cooled by the high-temperature water, the temperature of the outlet water of the high-temperature water is controlled to be 75-95 ℃, and the temperature of the engine oil is preferably controlled to be 80-110 ℃. In the system, a water pump, a fan, a radiator and an oil cooler are main components of the cooling system. When the engine runs, the crankshaft timing gear drives the high-low temperature water pump through the left idle gear and the right idle gear respectively to drive the water pump impeller to rotate, and the cooling liquid generates certain pressure under the centrifugal force action of the water pump and flows out of the outlet of the water pump. The cooling liquid pumped out by the high-temperature water pump enters the cooling water jackets of the cylinder body and the cylinder cover, and the cooling liquid flows to the water outlet main pipe after cooling the cylinder body and the cylinder cover and flows into the radiator after passing through the thermostat. The thermostat dress is in the delivery pipe tip, and thermostat automatic control temperature function when the coolant temperature is greater than 75 ℃, and the thermostat opens, and when the coolant temperature was greater than 85 ℃, the thermostat was opened fully, and the coolant liquid was whole to get into the radiator this moment, flows back to the water pump again. If the temperature of the cooling liquid is less than 75 ℃, the cooling liquid directly flows to a water pump to re-circulate cooling without heat dissipation and cooling of a radiator. The low-temperature water pump cools the intercooler and the engine oil cooler and then returns to the radiator for heat dissipation. The classified cooling of the high-temperature and low-temperature components can reduce the temperature of the air inlet and the temperature of the engine oil, reduce the loss of heat energy and save the oil of the engine.
As a preferred embodiment, the ratio of the stroke to the cylinder diameter of the high-power V-shaped 16-cylinder diesel engine is 1.1-1.3. In this scheme, select for use less stroke and cylinder diameter ratio, can reduce the height, width and the weight of diesel engine, the rotational speed of diesel engine multiplicable has improved the power of diesel engine.
As a preferred embodiment, the ratio of the center distance between adjacent cylinders to the diameter of the cylinder of the high-power V-shaped 16-cylinder diesel engine is 1.3-1.45. In the scheme, the ratio of the center distance of the cylinders to the diameter of the cylinders is 1.3-1.45, the length of the diesel engine is more compact, the strengthening degree of the diesel engine is higher, and the rigidity of a crankshaft and a machine body is stronger. Because the length of the crankshaft is shortened, the torsional rigidity is enhanced, the self-oscillation circular frequency of the shafting is improved, and the torsional oscillation performance is improved.
In conclusion, according to the high-power V-type 16-cylinder diesel engine of the embodiment, the V-shaped cylinder block 100 and the 16 single cylinder covers 200 are arranged, the air intake system is matched with the four superchargers and the intercooler, compressed air is cooled, so that the density of the compressed air is further improved, the power of the engine is improved, the performance of the engine is improved, the cooling system adopts high-temperature and low-temperature water split cooling, and thus, high-temperature and low-temperature components are classified and cooled, the air intake temperature and the engine oil temperature can be reduced, the heat loss is reduced, the engine is more oil-saving, the requirements of high power and high torque of the high-power high-speed diesel engine are met, and the engine body is more compact and has high strength.
The foregoing descriptions of specific exemplary embodiments of the present invention have been presented for purposes of illustration and description. It is not intended to limit the invention to the precise form disclosed, and obviously many modifications and variations are possible in light of the above teaching. The exemplary embodiments were chosen and described in order to explain certain principles of the invention and its practical application to enable one skilled in the art to make and use various exemplary embodiments of the invention and various alternatives and modifications as are suited to the particular use contemplated. It is intended that the scope of the invention be defined by the claims and their equivalents.
Claims (1)
1. A high power V-type 16 cylinder diesel engine, comprising:
the cylinder block comprises a V-shaped cylinder block, wherein 16 two rows of cylinder holes are arranged in a V shape, and an included angle between the two rows of cylinder holes is 90 degrees;
16 single cylinder heads which are respectively correspondingly arranged at the cylinder port parts of the two rows of cylinder holes;
the air inlet system comprises four turbochargers and an intercooler, the four turbochargers are respectively fixed above the single cylinder cover through a bracket and are arranged in a rectangular array, a compressor of each turbocharger is positioned at the outer side, a turbine of each turbocharger is positioned at the inner side, the compressor of each turbocharger is connected with an air filter which is erected upwards, the turbine of each turbocharger is connected with an exhaust pipe and converged towards the center positions of the four turbochargers to form an exhaust gas outlet, the intercooler is fixed at the upper position of the rear end of the V-shaped cylinder body, the compressor of each turbocharger is communicated with the intercooler through an air pipe, two sides of the bottom of the intercooler are respectively provided with air outlets, and the air outlets at two sides are respectively connected with an air inlet pipe;
the lubricating system comprises an oil pan, a pre-oil supply pump, an oil filter and an oil cooler, wherein the oil pan is arranged at the bottom of the V-shaped cylinder block, the pre-oil supply pump is arranged at the front side of the oil pan, the oil pump is arranged at the left lower position of the front end of the V-shaped cylinder block, the oil cooler is arranged at the left upper position of the front end of the V-shaped cylinder block, the oil filter is arranged at the right upper position of the front end of the V-shaped cylinder block, the oil in the oil pan is input into the oil cooler through the pre-oil supply pump and the oil pump, the oil cooler is connected with the oil filter through an oil pipe, and an oil outlet of the oil filter is communicated with a main oil duct of the V-shaped cylinder block; and
a cooling system including a high-temperature water circulation circuit and a low-temperature water circulation circuit, the low-temperature water circulation circuit including a rear radiator and a low-temperature water pump, the low-temperature water circulation circuit for cooling the oil cooler and the intercooler, the high-temperature water circulation circuit including a front radiator and a high-temperature water pump, the high-temperature water circulation circuit for cooling the V-block and the 16 single cylinder heads;
the piston is provided with a W combustion chamber in two rows of cylinder holes of the V-shaped cylinder body, an inner cooling oil channel is arranged in the piston, and four ring grooves are formed in the circumferential wall of the piston;
the high-temperature water pump and the low-temperature water pump are arranged on two sides above a crankshaft pulley at the front end of the V-shaped cylinder block, the crankshaft pulley drives the low-temperature water pump and the high-temperature water pump respectively, cooling liquid flowing through the V-shaped cylinder block and the 16 single cylinder heads enters the front-row radiator through a water outlet header pipe, a thermostat is connected between the water outlet header pipe and the front-row radiator, and the thermostat is arranged on the V-shaped cylinder block on the rear side of the engine oil cooler;
the intercooler is a rectangular shell, an air circulation cavity is arranged inside the rectangular shell, a cooling liquid flow channel is arranged in the rectangular shell around the air circulation cavity, and the low-temperature water circulation loop is communicated with the cooling liquid flow channel in the rectangular shell;
the ratio of the stroke to the cylinder diameter of the high-power V-shaped 16-cylinder diesel engine is 1.1-1.3;
the ratio of the center distance of adjacent cylinders to the diameter of the adjacent cylinders of the high-power V-shaped 16-cylinder diesel engine is 1.3-1.45.
Priority Applications (2)
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| CN201810122575.9A CN108194198B (en) | 2018-02-07 | 2018-02-07 | High-power V-shaped 16-cylinder diesel engine |
| PCT/CN2018/083193 WO2019153497A1 (en) | 2018-02-07 | 2018-04-16 | High power v-shaped 16-cylinder diesel engine |
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| CN201810122575.9A CN108194198B (en) | 2018-02-07 | 2018-02-07 | High-power V-shaped 16-cylinder diesel engine |
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| CN108194198B true CN108194198B (en) | 2022-04-12 |
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| CN109611440A (en) * | 2019-02-15 | 2019-04-12 | 广西玉柴机器股份有限公司 | 18 cylinder diesel crankshaft of V-type |
| JP2024087095A (en) * | 2022-12-19 | 2024-07-01 | ヤンマーホールディングス株式会社 | engine |
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| JP2007023871A (en) * | 2005-07-15 | 2007-02-01 | Miura Co Ltd | System for effectively using energy |
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| CN202611847U (en) * | 2012-05-22 | 2012-12-19 | 广西玉柴机器股份有限公司 | Cooling water route distributive device of V-shaped diesel engine |
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|---|---|---|---|---|
| US4480600A (en) * | 1982-05-24 | 1984-11-06 | General Motors Corporation | Compact odd cylinder V-type engine |
| US7895992B2 (en) * | 2007-09-24 | 2011-03-01 | Ford Global Technologies, Llc | Push rod engine with inboard exhaust |
| CN205206948U (en) * | 2015-11-04 | 2016-05-04 | 南车玉柴四川发动机股份有限公司 | Apply to turbocharging system that medium speed diesel went up two boosters of output |
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- 2018-04-16 WO PCT/CN2018/083193 patent/WO2019153497A1/en active Application Filing
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|---|---|---|---|---|
| JP2007023871A (en) * | 2005-07-15 | 2007-02-01 | Miura Co Ltd | System for effectively using energy |
| AU2007229913A1 (en) * | 2006-03-24 | 2007-10-04 | The Scuderi Group, Llc | System and method for split-cycle engine waste heat recovery |
| CN202611847U (en) * | 2012-05-22 | 2012-12-19 | 广西玉柴机器股份有限公司 | Cooling water route distributive device of V-shaped diesel engine |
| CN104832278A (en) * | 2015-05-27 | 2015-08-12 | 无锡开普动力有限公司 | V-shaped engine |
| CN106224094A (en) * | 2016-08-31 | 2016-12-14 | 河北华北柴油机有限责任公司 | 12 cylinder water-cooled Diesel engines |
| CN208040535U (en) * | 2018-02-07 | 2018-11-02 | 广西玉柴机器股份有限公司 | High-power V-shaped 16 cylinder diesel |
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| WO2019153497A1 (en) | 2019-08-15 |
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