WO2023141789A1 - 发动机 - Google Patents

发动机 Download PDF

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Publication number
WO2023141789A1
WO2023141789A1 PCT/CN2022/073888 CN2022073888W WO2023141789A1 WO 2023141789 A1 WO2023141789 A1 WO 2023141789A1 CN 2022073888 W CN2022073888 W CN 2022073888W WO 2023141789 A1 WO2023141789 A1 WO 2023141789A1
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WO
WIPO (PCT)
Prior art keywords
engine
air
equal
hole
channel
Prior art date
Application number
PCT/CN2022/073888
Other languages
English (en)
French (fr)
Inventor
杨景
张亚志
柴兆炬
徐桂林
吕信河
Original Assignee
浙江春风动力股份有限公司
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 浙江春风动力股份有限公司 filed Critical 浙江春风动力股份有限公司
Priority to PCT/CN2022/073888 priority Critical patent/WO2023141789A1/zh
Publication of WO2023141789A1 publication Critical patent/WO2023141789A1/zh

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Classifications

    • 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
    • F01M1/04—Pressure lubrication using pressure in working cylinder or crankcase to operate lubricant feeding devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads

Definitions

  • the present application relates to the field of power systems, in particular to an engine.
  • the throttle mechanism controls the air intake of the engine when the engine is in an idling state by arranging a hose.
  • the idling state refers to the state of the engine running without load, that is, the state where the clutch is in the engaged position, the transmission is in the neutral position, and the accelerator pedal is in the fully released position.
  • the weakening of the sealing performance and other reasons the leakage of the throttle mechanism will be caused.
  • the intake and exhaust mechanism of the engine needs to be set at a reasonable angle to make the intake volume of the engine more reasonable, thereby making the operation of the engine more stable.
  • the oil pump is used to inject the lubricating oil splashed by the balancing mechanism back into the crankcase.
  • the speed of lubricating oil injecting back into the crankcase becomes slower.
  • the oil pump is communicated with the inside of the crankcase through the form of drilling.
  • the oil pressure balance in the crankcase cannot be achieved by drilling holes, thus still causing the problem of water seepage and oil leakage of the engine, and the engine sealing cannot be guaranteed.
  • the present application provides an engine with good sealing effect and compact structure.
  • the present application provides an engine, including: a cylinder head, the cylinder head is formed with a first accommodation space; an intake and exhaust mechanism, the intake and exhaust mechanism is at least partly arranged in the first accommodation space, and the intake and exhaust mechanism includes intake mechanism and exhaust mechanism; cam mechanism, the cam mechanism is at least partly arranged in the first accommodation space for controlling the intake and exhaust mechanism; crankcase, the crankcase forms a second accommodation space; crankshaft linkage mechanism, crankshaft linkage The rod mechanism is at least partially disposed in the second accommodation space; the balance mechanism is at least partially disposed in the second accommodation space and connected to the crankshaft connecting rod mechanism, and the balance mechanism includes a first balance shaft and a second balance shaft; the engine also includes: Throttle mechanism, the throttle mechanism includes: main channel, the main channel is connected to the intake mechanism, and is used to control the air input to the intake mechanism; The through line of itself; the engine also includes a cylinder block, the cylinder block includes a cylinder hole, the cylinder block basically extends along
  • the present application provides an engine, including: a cylinder head, the cylinder head is formed with a first accommodation space; an intake and exhaust mechanism, the intake and exhaust mechanism is at least partly arranged in the first accommodation space, and the intake and exhaust mechanism It includes an intake mechanism and an exhaust mechanism, the intake mechanism is used for intake of the engine, and the exhaust mechanism is used for exhaust of the engine; a cam mechanism, the cam mechanism is at least partly arranged in the first accommodation space, and is used to control the intake and exhaust mechanism; the engine also includes: a throttle mechanism, the throttle mechanism includes: a main channel, the main channel is connected to the intake mechanism, and is used to control air input to the intake mechanism; a throttle channel, the throttle channel and the main channel are integrally formed and at least partially connected aisle.
  • the present application provides an engine, including: a cylinder head, the cylinder head is formed with a first accommodation space; an intake and exhaust mechanism, the intake and exhaust mechanism is at least partly arranged in the first accommodation space, and the intake and exhaust mechanism It includes an intake mechanism and an exhaust mechanism, the intake mechanism is used for intake of the engine, and the exhaust mechanism is used for exhaust of the engine; a cam mechanism, the cam mechanism is at least partly arranged in the first accommodation space, and is used to control the intake and exhaust Mechanism; crankcase, the crankcase is formed with a second accommodation space; crankshaft linkage mechanism, the crankshaft linkage mechanism is at least partly arranged in the second accommodation space; balance mechanism, the balance mechanism is at least partly arranged in the second accommodation space and connected to the crankshaft
  • the connecting rod mechanism the balance mechanism includes a first balance shaft and a second balance shaft; the engine also includes: a throttle mechanism, the throttle mechanism includes: a main channel, the main channel is connected to the intake mechanism, and is used to control air input to the intake
  • the oil drain groove is arranged between the crankcase and the oil pump assembly and communicates with the crankcase and the oil pump assembly; the first passage is arranged between the crankcase and the oil pump assembly Between the crankcase and the oil pump assembly, it is used to balance the oil pressure inside the crankcase; the second channel is set between the crankcase and the oil pump assembly and communicates with the crankcase and the oil pump assembly, and is used to form a channel for lubricating oil .
  • the throttle mechanism can be set as an integral molding, thereby avoiding the risk of leakage caused by poor connection, aging and other problems, and improving the sealing performance of the throttle mechanism; by setting a reasonable angle of the intake and exhaust mechanism, thereby Make the structure of the engine more compact, and make the intake volume and exhaust temperature field distribution of the engine more reasonable; the oil pressure balance inside the crankcase can be realized by setting an oil drain tank between the crankcase and the oil pump assembly, so that Avoid water seepage and oil seepage of the engine, thereby improving the sealing performance of the engine.
  • Fig. 1 is a schematic perspective view of the engine of the present application.
  • Fig. 2 is an exploded view of the overall structure of the engine of the present application.
  • Fig. 3 is a schematic cross-sectional structural view of the engine of the present application.
  • Fig. 4 is a partial structural schematic diagram of the engine of the present application.
  • Fig. 5 is a schematic diagram of the half-section structure of the engine of the present application.
  • Fig. 6 is a schematic structural view of the first angle of the throttle mechanism of the present application.
  • Fig. 7 is a structural schematic diagram of the second angle of the throttle mechanism of the present application.
  • Fig. 8 is a first sectional structural schematic diagram of the cylinder head of the present application.
  • Fig. 9 is a partial enlarged view of A in Fig. 8 of the present application.
  • Fig. 10 is a schematic structural view of the shaft seat of the present application.
  • Fig. 11 is a partial structural schematic view of the shaft seat of the present application.
  • Fig. 12 is a partial enlarged view of B in Fig. 10 of the present application.
  • Fig. 13 is a second sectional structural schematic diagram of the cylinder head of the present application.
  • Fig. 14 is a third sectional structural schematic diagram of the cylinder head of the present application.
  • Fig. 15 is a schematic structural view of the cylinder head cover of the present application.
  • Fig. 16 is a third sectional structural schematic diagram of the cylinder head of the present application.
  • Fig. 17 is a partial enlarged view of position C in Fig. 16 of the present application.
  • Fig. 18 is a partial enlarged view at D in Fig. 16 of the present application.
  • Fig. 19 is a partial structural schematic diagram of the intake and exhaust mechanism of the present application.
  • Fig. 20 is a schematic diagram of the bottom surface structure of the cylinder head of the present application.
  • Fig. 21 is a schematic structural view of the cylinder block of the present application.
  • Fig. 22 is a first sectional structural schematic diagram of the crankcase of the present application.
  • Fig. 23 is a schematic cross-sectional structure diagram at E-E in Fig. 22 of the present application.
  • Fig. 24 is a partial enlarged view at F in Fig. 23 of the present application.
  • an engine 100 includes an outer casing assembly 200
  • the outer casing assembly 200 includes a cylinder head cover 1 , a cylinder head 2 , a cylinder block 3 , a crankcase 4 and an oil pan 5 .
  • side covers 6 are provided on both sides of the crankcase 4 .
  • the cylinder head cover 1 is used to cover and seal the cylinder head 2, keep lubricating oil inside the engine 100, and isolate dirt, moisture, etc. from the outside of the engine 100 at the same time.
  • the cylinder head 2 is connected with the cylinder block 3 to form a substantially airtight sealed space, which is used to seal gas and form a combustion space to withstand high temperature and high pressure gas.
  • the cylinder block 3 and the crankcase 4 are the basic structures of the engine 100 engine.
  • the oil sump 5 is used to close the crankcase 4 and form an oil storage tank after being connected with the crankcase 4 to prevent impurities from entering, and to collect and store lubricating oil free on the friction surfaces of the engine 100 .
  • the engine 100 also includes a cam mechanism 7 , an intake and exhaust mechanism 8 , an ignition mechanism 9 , a piston mechanism 11 , a transmission mechanism 12 , a crankshaft linkage mechanism 13 and a balance mechanism 14 .
  • the outer casing assembly 200 forms an accommodating space 201 , and the cam mechanism 7 , the intake and exhaust mechanism 8 , the ignition mechanism 9 , the piston mechanism 11 , the transmission mechanism 12 , the crankshaft linkage mechanism 13 and the balance mechanism 14 are at least partly disposed in the accommodating space 201 .
  • the accommodation space 201 includes a first accommodation space 2011 , a second accommodation space 2012 and a third accommodation space 2013 .
  • the cylinder head 2 forms a first accommodating space 2011
  • the cam mechanism 7 , the intake and exhaust mechanism 8 and the ignition mechanism 9 are at least partially disposed in the first accommodating space 2011 .
  • the cylinder block 3 forms a second accommodation space 2012
  • the piston mechanism 11 is at least partially disposed in the second accommodation space 2012 .
  • the crankcase 4 forms a third accommodating space 2013
  • the transmission mechanism 12 , the crankshaft linkage mechanism 13 and the balance mechanism 14 are at least partially disposed in the third accommodating space 2013 .
  • the crankshaft linkage mechanism 13 is connected with the cam mechanism 7 , the piston mechanism 11 and the balance mechanism 14 .
  • the cam mechanism 7 contacts the intake and exhaust mechanism 8 .
  • the intake and exhaust mechanism 8 includes an intake mechanism 81 and an exhaust mechanism 82 .
  • the ignition mechanism 9 is provided between the intake mechanism 81 and the exhaust mechanism 82 .
  • the crankshaft-link mechanism 13 includes a crankshaft 131 and a connecting rod 132. One end of the connecting rod 132 is connected to the piston mechanism 11, and the other end of the connecting rod 132 is connected to the crankshaft 131.
  • the crankshaft 131 and the balance mechanism 14 are connected through gear meshing.
  • the piston mechanism 11 includes a piston 111 and a piston pin 112 , and the piston 111 and the connecting rod 132 are connected through the piston pin 112 .
  • a cylinder block 3 is provided near one end of the ignition mechanism 9
  • a cam mechanism 7 is provided near the other end of the ignition mechanism 9 .
  • the cam mechanism 7 includes a camshaft 71 and a shaft seat 72
  • the camshaft 71 includes a first axle 711 and a second axle 712 .
  • the cylinder head cover 1 and the cylinder head 2 are connected by a shaft seat 72 .
  • the crankshaft 131 is connected with the cam mechanism 7 through the valve transmission assembly 15, and the valve transmission assembly 15 is arranged in the accommodation space formed around the cylinder head 2, the cylinder block 3 and the crankcase 4, and the valve transmission assembly 15 includes timing Chain 151 , crankshaft 131 and cam mechanism 7 are connected through timing chain 151 .
  • the transmission mechanism 12 includes a transmission main shaft 121 and a transmission sub-shaft 122 , and the transmission main shaft 121 and the transmission sub-shaft 122 are connected through gear meshing.
  • the crankshaft 131 drives the transmission mechanism 12, and transmits power to the front wheels and/or rear wheels of the vehicle through the transmission mechanism 12, thereby driving the vehicle to run.
  • the space between the ignition mechanism 9 and the cylinder block 3 is the combustion chamber 16 .
  • the combustion chamber 16 is set as the space between the top of the piston 111 and the bottom surface of the cylinder head 2 after the piston 111 reaches the top dead center.
  • the top dead center is the position where the top of the piston 111 is farthest from the rotation center of the crankshaft 131 .
  • the top of the piston 111 refers to the end surface of the piston 111 close to the cylinder head 2
  • the bottom surface of the cylinder head 2 refers to the surface of the cylinder head 2 close to the top of the piston 111 .
  • the piston 111 is driven by the crankshaft-link mechanism 13 , so that the piston 111 makes linear reciprocating motion in the cylinder block 3 .
  • the intake mechanism 81 is used to send fresh air or combustible mixture into the combustion chamber 16, and the ignition mechanism 9 ignites the fresh air or combustible mixture to burn the fresh air or combustible mixture in the combustion chamber 16, and the piston mechanism 11 will
  • the thermal energy is converted into mechanical energy, and the crankshaft 131 is driven to move through the connecting rod 132 .
  • the crankshaft 131 drives the cam mechanism 7 to move through the valve transmission assembly 15 , so that the cam mechanism 7 opens and closes the intake mechanism 81 and the exhaust mechanism 82 .
  • the crankshaft 131 drives the transmission mechanism 12 so that the transmission mechanism 12 transmits power to the vehicle.
  • the exhaust mechanism 82 filters the exhaust gas after combustion, so that the exhaust gas is discharged into the atmosphere.
  • the throttle mechanism 19 is a controllable valve that controls the air to enter the engine 100. After the gas enters the intake mechanism 81, it will mix with gasoline to become a combustible mixture, thereby burning to form work. One end of the throttle mechanism 19 is connected to the air filter, and the other end of the throttle mechanism 19 is connected to the cylinder head 2 .
  • the throttle mechanism 19 is connected with the outer casing assembly 200 .
  • the throttle mechanism 19 is connected with the cylinder head 2 .
  • the intake mechanism 81 includes an intake passage 812 and a first valve mechanism 811, and the throttle mechanism 19 is connected to the intake mechanism 81.
  • the intake and exhaust mechanism 8 The quantity of intake mechanism 81 and exhaust mechanism 82 is two; when engine 100 is a twin-cylinder engine, the quantity of intake and exhaust mechanism 8 is two, and intake mechanism 81 and exhaust mechanism 82 The number is four; that is, one intake and exhaust mechanism 8 includes two intake mechanisms 81 and two exhaust mechanisms 82.
  • the throttle mechanism 19 is at least partly disposed on the intake passage 812, and the throttle mechanism 19 is fixedly connected to the intake passage 812 through threads or the like.
  • the throttle mechanism 19 includes a main channel 191 , a throttle valve body 192 and a valve body motor 193 .
  • One end of the main passage 191 communicates with the outside world, the other end of the main passage 191 communicates with the air inlet 812 , and one end of the main passage 191 connected with the air inlet 812 is provided with threads.
  • the air inlet channel 812 is fixedly connected with the main channel 191 by means of threads or the like.
  • the throttle valve body 192 is arranged on one side of the main passage 191 .
  • the throttle body 192 is at least partly integrally formed with the main channel 191 , thereby avoiding the risk of leakage caused by problems such as poor connection and aging.
  • the valve body motor 193 is used to control the opening and closing of the throttle valve body 192 .
  • the valve body motor 193 controls the throttle valve body 192 to open, and then controls the air input to the intake passage 812 through the throttle valve body 192 .
  • the throttle body 192 includes a gas valve 1921 and a throttle passage 1922 .
  • the throttle channel 1922 is integrally formed with the main channel 191 , which can avoid the risk of leakage caused by problems such as poor connection and aging, thereby making the connection of the throttle mechanism 19 more stable and improving the sealing performance of the throttle mechanism 19 .
  • the throttling passage 1922 is at least partially connected to the main passage 191 , and the throttling passage 1922 supplies air to the intake passage 812 through the main passage 191 .
  • the throttle passage 1922 includes an air inlet 1922a, an air outlet 1922b, a throttle air passage 1922c and an air outlet 1922d.
  • the air intake hole 1922a is integrally formed with the main passage 191, which can improve the airtightness of the throttle passage 1922, so that the air is basically input to the throttle mechanism 19 through the main passage 191, effectively avoiding leakage caused by problems such as poor connection and aging risk.
  • the air outlet hole 1922b is integrally formed with the main channel 191, which can improve the airtightness of the air-saving channel 1922, so that the air is basically input into the air intake channel 812 through the main channel 191, effectively avoiding the risk of leakage caused by problems such as poor connection and aging .
  • the throttle air channel 1922c is integrally formed with the main channel 191, and the throttle air channel 1922c communicates with the air outlet 1922d and the air inlet 1922a. Specifically, the first section of the throttle air passage 1922c is connected to the air outlet 1922d, and the second section of the throttle air passage 1922c is connected to the air inlet 1922a.
  • the air outlet 1922d is arranged on the first section of the throttle air channel 1922c, the air outlet 1922d is arranged between the throttle air channel 1922c and the air outlet hole 1922b, the air outlet 1922d is connected to the throttle air channel 1922c and the air outlet hole 1922b, and the air outlet 1922d is used to
  • the air input from the air intake hole 1922a is input to the air outlet hole 1922b through the throttle air channel 1922c, so that the air is input to the air intake channel 812 through the air outlet hole 1922b.
  • the air outlet 1922d is integrally formed with the main passage 191, which can improve the sealing performance of the air-saving passage 1922, so that the air is basically input into the air inlet 812 through the air outlet 1922b, effectively avoiding leakage caused by poor connection, aging and other problems. leakage risk.
  • the throttle channel 1922 is integrally formed with the main channel 191 .
  • the air inlet 1922a, the air outlet 1922b, the throttle air passage 1922c and the air outlet 1922d are integrally formed with the main channel 191, so that the air can pass through the air inlet 1922a, the throttle air passage 1922c, the air outlet 1922d and the air outlet 1922b in sequence After that, it is input to the main channel 191, so that the air is input into the air intake channel 812 through the main channel 191, which can improve the sealing performance of the throttle channel 1922, so that the air is basically input into the air intake channel 812, effectively avoiding problems caused by poor connection, aging, etc. The risk of leakage caused by the problem.
  • the air valve 1921 controls the degree of opening and closing of the air outlet 1922d through the valve body motor 193, thereby controlling the amount of air entering the air outlet 1922d.
  • the valve body motor 193 may be a stepping motor.
  • Engine 100 includes at least a first state and a second state.
  • the first state that is, when the engine 100 is in an idle state
  • the main channel 191 is closed, and the intake air of the engine 100 is controlled by the throttle body 192 .
  • the idling state refers to the no-load running state of the engine 100 , that is, the state in which the clutch is in the engaged position, the transmission is in the neutral position, and the accelerator pedal is in the fully released position.
  • the valve body motor 193 controls the air outlet 1922d to open, and the air is input from the air inlet 1922a, so that the air passes through the throttle air passage 1922c, the air outlet 1922d,
  • the air outlet 1922b further allows air to be input into the air inlet 812 .
  • the main channel 191 is opened, the air intake of the engine 100 is controlled by the main channel 191 , and the air valve 1921 controls the air outlet 1922d to close.
  • the valve body motor 193 controls the air valve 1921 to close the air outlet 1922d, and the air cannot enter the air outlet 1922b through the air outlet 1922d, so that the air cannot enter the air inlet 812 through the throttle passage 1922.
  • the main channel 191 is opened and closed by a channel valve 194, and the channel valve 194 includes a throttle cable 1941, a valve shaft 1942 and a gas choke 1943, and the throttle cable 1941, the valve shaft 1942 and the gas choke 1943 are sequentially connected.
  • the valve shaft 1942 runs through the main passage 191, and the two ends of the valve shaft 1942 are arranged on both sides of the main passage 191.
  • One end of the valve shaft 1942 is provided with a throttle cable 1941. Enter Main Road 191.
  • the air blocking sheet 1943 is rotatably connected to the valve shaft 1942 .
  • the sealing and fixing at both ends of the valve shaft 1942 can be sealed and fixed by O-rings, and the air blocking piece 1943 can be a circular steel piece.
  • valve shaft 1942 controls the choke piece 1943 through the throttle cable 1941 so that the axis of the choke piece 1943 is basically parallel to the axis of the main channel 191, the choke piece 1943 blocks the main channel 191, thereby closing the main channel 191;
  • valve shaft 1942 Control the choke piece 1943 through the throttle cable 1941, so that when the axis of the choke piece 1943 is substantially perpendicular to the axis of the main channel 191, that is, the choke piece 1943 rotates about 90°, and a gap is formed between the choke piece 1943 and the main channel 191, so that The main channel 191 is open.
  • the two ends of the main channel 191 are channel one end 1911 and channel two ends 1912 respectively.
  • One end of the channel one end 1911 is connected to the air inlet 812, and one end of the channel two ends 1912 is connected to the outside world, so that air can pass through the channel one end 1911 from the channel.
  • the two ends 1912 are input to the air inlet 812 .
  • One end of the air intake hole 1922a is connected to the throttle air channel 1922c, and the other end of the air intake hole 1922a is connected to the other end of the second end of the channel 1912, so that air can be input from the second end of the channel 1912 to the throttle air channel 1922c through the air intake hole 1922a.
  • the throttle valve body 192 can be connected with the main channel 191 , so that the throttle valve body 192 and the throttle mechanism 19 can be integrally formed, thereby avoiding the risk of leakage caused by problems such as poor connection and aging.
  • the throttle mechanism 19 includes a first main channel 1911 , a second main channel 1912 , a throttle valve body 192 and a valve body motor 193 .
  • the first main channel 1911 and the second main channel 1912 are arranged substantially in parallel.
  • the throttle valve body 192 is at least partially disposed between the first main passage 1911 and the second main passage 1912 , the throttle valve body 192 is at least partly integrally formed with the first main passage 1911 , and the throttle valve body 192 is at least partially integrally formed with the second main passage 1912 molding, thereby avoiding the risk of leakage caused by problems such as poor connection and aging, and improving the sealing performance of the throttle mechanism 19 .
  • the throttle body 192 includes a throttle passage 1922 and a gas valve 1921 .
  • the throttle channel 1922 is at least partially disposed between the first main channel 1911 and the second main channel 1912, the throttle channel 1922 is integrally formed with the first main channel 1911, and the throttle channel 1922 is integrally formed with the second main channel 1912, thereby avoiding the The risk of leakage caused by problems such as defects and aging improves the sealing performance of the throttle mechanism 19 .
  • the throttle channel 1922 includes an air outlet 1922d, two air inlet holes 1922a, two air outlet holes 1922b, and a throttle air channel 1922c.
  • the air outlet 1922d is disposed between the first main channel 1911 and the second main channel 1912 , the air outlet 1922d is integrally formed with the first main channel 1911 , and the air outlet 1922d is integrally formed with the second main channel 1912 .
  • Two air intake holes 1922a are arranged between the first main channel 1911 and the second main channel 1912, the two air intake holes 1922a are integrally formed with the first main channel 1911, and the two air intake holes 1922a are integrally formed with the second main channel 1912 forming.
  • Two air outlet holes 1922b are disposed between the first main channel 1911 and the second main channel 1912 , the two air outlet holes 1922b are integrally formed with the first main channel 1911 , and the two air outlet holes 1922b are integrally formed with the second main channel 1912 .
  • the throttle air channel 1922c is disposed between the first main channel 1911 and the second main channel 1912 , the throttle air channel 1922c is integrally formed with the first main channel 1911 , and the throttle air channel 1922c is integrally formed with the second main channel 1912 .
  • the air outlet 1922d, two air inlets 1922a, two air outlets 1922b, and throttle airway 1922c are integrally formed with the first main channel 1911, and the air outlet 1922d, two air inlets 1922a, two Both the air outlet hole 1922b and the throttle air channel 1922c are integrally formed with the second main channel 1912 , thus avoiding the leakage risk caused by problems such as poor connection and aging, and improving the sealing performance of the throttle mechanism 19 .
  • the throttle air channel 1922c is basically arranged parallel to the first main channel 1911
  • the throttle air channel 1922c is basically arranged parallel to the second main channel 1912 .
  • a connecting portion 196 is provided between the first main channel 1911 and the second main channel 1912, the connecting portion 196 is integrally formed with the first main channel 1911, and the connecting portion 196 is integrally formed with the second main channel 1912, thereby avoiding problems caused by poor connection, The risk of leakage caused by problems such as aging improves the sealing performance of the throttle mechanism 19 .
  • the throttle valve body 192 is at least partially disposed on the connecting portion 196 , and the valve body motor 193 is at least partially disposed on the connecting portion 196 .
  • the throttle valve body 192 may be disposed along the extending direction of the connecting portion 196 . Wherein, the extending direction of the connecting portion 196 refers to a direction parallel to the axis of the main channel 191 .
  • the access valve 194 includes an accelerator cable 1941, a valve shaft 1942, a first choke piece 1943a and a second choke piece 1943b.
  • the valve shaft 1942 runs through the first main channel 1911 and the second main channel 1912, the axis of the valve shaft 1942 is basically perpendicular to the axis of the first main channel 1911, the axis of the valve shaft 1942 is basically perpendicular to the axis of the second main channel 1912, and the two ends of the valve shaft 1942 are arranged On the opposite sides of the first main channel 1911 and the second main channel 1912 , that is, the two ends of the valve shaft 1942 pass through the first main channel 1911 , the connecting portion 196 and the second main channel 1912 in sequence.
  • valve shaft 1942 One end of the valve shaft 1942 is provided with an accelerator pull wire 1941, and both ends of the valve shaft 1942 are sealed and fixed.
  • the first baffle piece 1943a is rotatably connected to the valve shaft 1942 and is located in the first main channel 1911
  • the second baffle piece 1943b is rotatably connected to the valve shaft 1942 and is located in the second main channel 1912, so that the first baffle piece 1943a controls the opening and closing of the first main channel 1911
  • the second air blocking sheet 1943b controls the opening and closing of the second main channel 1912 .
  • the first baffle piece 1943a rotates with the rotation of the valve shaft 1942, thereby controlling the opening and closing of the first main channel 1911 through the rotation of the first baffle piece 1943a; the second baffle piece 1943b rotates with the valve shaft 1942 is rotated to control the opening and closing of the second main channel 1912 through the rotation of the second baffle piece 1943b.
  • the valve body motor 193 is arranged near one end 1911 of the channel, so that the valve body motor 193 controls the air valve 1921 to open and close the air outlet 1922d.
  • the connecting portion 196 is provided with a valve slot 1961 , and an air valve 1921 is arranged in the valve slot 1961 , and the air valve 1921 is connected with the valve body motor 193 .
  • the throttling air passage 1922c can be arranged along the extending direction of the connecting portion 196, and this arrangement can make the throttling air passage 1922c substantially parallel to the main passage 191, so that the air inlet hole 1922a can communicate with the throttling air passage 1922c and the main passage 191, which is convenient.
  • the air outlet 1922b communicates with the air outlet 1922d and the main channel 191 , so that the air can be input into the air inlet 812 more smoothly.
  • the two air intake holes 1922a are arranged symmetrically about the axis of the throttle air passage 1922c.
  • the first main passage 1911 communicates with one end of one air intake hole 1922a
  • the second main passage 1912 communicates with one end of the other air intake hole 1922a
  • the throttle air passages 1922c communicate with each other.
  • the two air outlets 1922b are arranged symmetrically about the axis of the throttle air channel 1922c.
  • the first main channel 1911 communicates with one end of one air outlet 1922b
  • the second main channel 1912 communicates with one end of the other air outlet 1922b
  • the air outlets 1922d communicate with the two air outlets respectively.
  • the center of the air outlet 1922d is basically on the axis of the air-saving air passage 1922c
  • the air outlet 1922d is arranged on the side wall of the air-saving air passage 1922c, so that air can be evenly input into the two air outlets 1922b through the air outlet 1922d.
  • the air outlet 1922d Through the arrangement of the air outlet 1922d, two air inlets 1922a, and two air outlets 1922b, the air outlet 1922d, the air inlet 1922a, and the air outlet 1922b are reasonably arranged in the throttle mechanism 19, which is convenient to improve the air inlet 1922a.
  • the axis of the valve shaft 1942 is substantially perpendicular to the axis of the first main passage 1911
  • the axis of the valve shaft 1942 is substantially perpendicular to the axis of the second main passage 1912 .
  • One side of the axis of the valve shaft 1942 is provided with a throttle air passage 1922c
  • the other side of the axis of the valve shaft 1942 is provided with a valve body motor 193 .
  • There is a gap between the valve shaft 1942 and the throttle air passage 1922c that is, there is no connection between the valve shaft 1942 and the throttle air passage 1922c, so as to prevent air from entering the throttle air passage 1922c through the valve shaft 1942, and facilitate the sealing of the throttle mechanism 19 .
  • the gas valve 1921 includes a valve head 1921a and a valve body 1921b, and the valve head 1921a and the valve body 1921b are integrally formed.
  • the valve body 1921b is connected to the valve body motor 193, and the valve head 1921a is used to open and close the air outlet 1922d.
  • the valve body motor 193 controls the valve body 1921b to push and/or pull the valve head 1921a, so that the valve head 1921a closes and/or opens the air outlet 1922d.
  • the first plug 195 is provided on the valve head 1921a, and the first plug 195 is used to fill the gap between the air valve 1921 and other components, so as to facilitate the improvement of the throttle mechanism 19 during the use of the throttle mechanism 19. 19 tightness.
  • the shape of the first plug 195 is bowl-shaped, which can facilitate the first plug 195 to better fill the gap between the air valve 1921 and other components, thereby improving the sealing performance of the throttle mechanism 19 .
  • the cam mechanism 7 includes a camshaft 71 and a shaft seat 72 , the shaft seat 72 is at least partially connected to the cylinder head 2 , and the shaft seat 72 is used to support and lubricate the camshaft 71 .
  • an ignition mechanism 9 is arranged near one end of the camshaft 71, and a shaft seat 72 is arranged near the other end of the camshaft 71.
  • the ignition mechanism 9 and the shaft seat 72 are basically symmetrically distributed about the axis of the camshaft 71. .
  • the surface of the shaft seat 72 away from the camshaft 71 is the upper surface
  • the upper surface of the shaft seat 72 basically extends along the second straight line 300
  • the upper surface of the shaft seat 72 is provided with a first symmetrical plane 600
  • the first The symmetrical plane 600 is a symmetrical plane perpendicular to the second straight line 300
  • the two ends of the shaft seat 72 along the direction of the second straight line 300 are the two ends of the shaft seat 72
  • the two sides of the shaft seat 72 perpendicular to the direction of the second straight line 300 are the shaft seats 72 on both sides.
  • the shaft seat 72 is provided with several shaft seat installation holes 722 and several cover installation holes 724, and several shaft seat installation holes 722 are evenly distributed at the edge of the shaft seat 72, and several cover installation holes 724 are uniformly arranged at both ends of the shaft seat 72 .
  • the shaft seat installation hole 722 is used to fix the shaft seat 72 on the cylinder head 2
  • the cover installation hole 724 is used to install the cylinder head cover 1 on the shaft seat 72 .
  • One of the shaft seat installation holes 722 can also be used as the installation hole of the valve transmission assembly 15.
  • the shaft seat installation hole 722 is specifically a bolt stud hole, and the bolt stud hole is arranged at the junction of two adjacent sides on the shaft seat 72 upper surface. .
  • the junction of two adjacent sides on the upper surface of the shaft seat 72 refers to the junction of one end of the shaft seat 72 and one side of the shaft seat 72 .
  • the number of shaft seat installation holes 722 is six, and four shaft seat installation holes 722 are respectively arranged at the intersection of two adjacent sides on the upper surface of the shaft seat 72, and the other two shaft seat installation holes 722 are located at the junction of two adjacent sides of the shaft seat 72.
  • the edge of the seat 72 is located on the first symmetry plane 600 ; the number of cover installation holes 724 is two, and the cover installation holes 724 are located at the edge of the shaft seat 72 and located on the center line of the shaft seat 72 .
  • the cover installation hole 724 comprises a first installation hole 7241 and a second installation hole 7242, the first installation hole 7241 is located at one end of the bolt stud hole, the second installation hole 7242 is located at the other end of the shaft seat 72, the first installation hole There is a certain distance between 7241 and the edge of the shaft seat 72 .
  • several convex edges 725 are provided at the edge of the upper surface of the shaft seat 72, and several convex edges 725 extend toward the direction facing away from the upper surface of the shaft seat 72.
  • Several shaft seat installation holes 722 are arranged on several convex edges 725, and several The cover installation holes 724 are provided on several convex edges 725 , and the several shaft seat installation holes 722 and the several cover installation holes 724 all pass through the several convex edges 725 .
  • the cylinder head 2 is provided with a through-line 29 penetrating itself
  • the second straight line 300 is a straight line perpendicular to the through-line 29
  • the centerline of the axle seat 72 refers to the centerline of the axle seat 72 parallel to the second straight line 300 .
  • the shaft seat 72 includes a shaft limiting mechanism 726 (as shown in FIGS. 8 and 9 ), an oil collection structure 727 and an oil through hole 728.
  • the shaft limiting mechanism 726 is located near the first mounting hole 7241. At one end, the shaft limit mechanism 726 cooperates with the camshaft 71 to realize the displacement of the camshaft 71 , and the oil collecting structure 727 and the oil through hole 728 cooperate with the camshaft 71 to realize the lubrication of the camshaft 71 .
  • the shaft seat 72 uses splash lubrication to lubricate the camshaft 71 .
  • the oil collecting structure 727 is used to collect and store splashed lubricating oil, increase the amount of lubricating oil, and provide a good lubricating effect for the camshaft 71 .
  • the oil through hole 728 runs through the shaft seat 72, and the oil through hole 728 communicates with the camshaft 71, and is used to inject the lubricating oil collected by the oil collecting structure 727 onto the camshaft 71, thereby avoiding the The wear caused by the axial movement increases too fast.
  • the splashed lubricating oil refers to the lubricating oil splashed out from the balance mechanism 14 .
  • the oil collecting structure 727 is arranged on the end of the shaft seat 72 close to the first mounting hole 7241, which is convenient to cooperate with the camshaft 71 and better improves the lubricating effect of the camshaft 71.
  • the oil collection structure 727 is arranged around the oil passage hole 728, so that the splashed lubricating oil can be collected in the oil collection structure 727 effectively, and injected onto the camshaft 71 through the oil passage hole 728, thereby improving the camshaft 71 and the shaft limit mechanism. Lubrication effect between 726.
  • the oil collecting structure 727 includes an oil collecting groove 7271 and an oil collecting baffle 7272, the oil collecting groove 7271 and the first installation hole 7241 are arranged at the same end of the shaft seat 72, the oil collecting groove 7271 and the first A mounting hole 7241 is arranged substantially symmetrically with respect to the center line of the shaft seat 72 .
  • the oil collecting groove 7271 is basically arranged parallel to the camshaft 71.
  • the oil collecting baffle 7272 includes a first baffle 7272a and a second baffle 7272b connected to each other.
  • first baffle 7272a One end of the first baffle 7272a is connected to a bolt stud hole, and the first baffle 7272a
  • the other end of the second baffle plate 7272b is connected to one end of the second baffle plate 7272b, the other end of the second baffle plate 7272b is connected to the first mounting hole 7241, the inner surface of the second baffle plate 7272b is the first surface 7272d, and the oil collection groove 7271 is close to the second baffle plate 7272b
  • the inner side surface of is the second surface 7271a, and the first surface 7272d and the second surface 7271a are substantially in the same plane.
  • This setting method can better collect and store the splashed lubricating oil, thereby increasing the amount of lubricating oil and effectively improving the lubricating effect.
  • the first surface 7272d is closer to the first installation hole 7241 than the second surface 7271a.
  • the connection mode between the second baffle plate 7272b and the first baffle plate 7272a may be a circular arc connection, so that lubricating oil can be stored in the oil collecting baffle plate 7272 more smoothly during the splashing process.
  • the first installation hole 7241 is provided with a bending part 721 near the center of the shaft seat 72.
  • the bending part 721 is arranged with one high and one low.
  • the higher side of the bending part 721 is the first plane 7211.
  • the bending part 721 The lower side is the second plane 7212, the junction of the first plane 7211 and the second plane 7212 is the first vertical plane 7213, the first baffle plate 7272a is connected to the side of the bolt stud hole near the edge of the shaft seat 72, and the second The outer surface of the baffle 7272b is connected to the first installation hole 7241 , and the other end of the second baffle 7272b extends to the first vertical surface 7213 . Both the oil collecting groove 7271 and the oil collecting baffle 7272 are arranged on the second plane 7212 . Wherein, the inner side surface of the second baffle plate 7272b is a surface away from the first installation hole 7241 .
  • the oil collecting groove 7271 includes a first groove edge 7271c and a second groove edge 7271d.
  • the first groove edge 7271c and the second groove edge 7271d may be arranged at the same height.
  • the first groove edge 7271c and the second groove edge 7271d can also be arranged one high and one low, the higher groove edge is the first groove edge 7271c, and the first groove edge 7271c is arranged On the lower side of the bottom surface of the oil collecting groove 7271, the groove edge on the lower side is the second groove edge 7271d, and the second groove edge 7271d is arranged on the higher side of the bottom surface of the oil collecting groove 7271, so that after the engine 100 is installed, the As much lubricating oil as possible is kept in the oil sump 7271, increasing the amount of lubricating oil.
  • the first groove edge 7271c refers to the edge of the oil collecting groove 7271 near the first installation hole 7241
  • the second groove edge 7271d refers to the edge of the groove opposite to the first groove edge 7271c.
  • the oil collecting baffle 7272 has a semi-enclosed shape, which can avoid the problem of less oil collection caused by the lubricating oil being blocked by the oil collecting baffle 7272; it can also reduce material waste and reduce Difficulty in processing; it can also collect the lubricating oil overflowed in the oil collecting groove 7271, thereby increasing the lubricating oil storage capacity and providing a good lubricating effect for the camshaft 71.
  • the heights of the first baffle plate 7272a and the second baffle plate 7272b can be consistent or inconsistent
  • the oil collecting baffle plate 7272 is arranged on the upper surface of the shaft seat 72, and the first baffle plate 7272a and the second baffle plate 7272b are connected and surrounded
  • At least part of the oil collecting groove 7271 the inner surface of the first baffle 7272a is the third surface 7272c
  • the inner surface of the oil collecting groove 7271 close to the first baffle 7272a is the fourth surface 7271b
  • the third surface 7272c and the fourth surface 7271b can be basically It is arranged on the same plane
  • the third surface 7272c can also be closer to the bolt stud hole than the fourth surface 7271b, that is, the third surface 7272c can also be farther away from the oil hole 728 than the fourth surface 7271b, so that more oil can be collected and stored.
  • Lubricating oil provides good lubricating effect for the camshaft 71, which is convenient to reduce the wear of the camshaft
  • the shaft limiting mechanism 726 also includes a shaft groove 7261 ; the camshaft 71 is provided with an annular protrusion 713 .
  • the shaft groove 7261 is provided on the lower surface of the shaft seat 72 for cooperating with the annular protrusion 713 provided on the camshaft 71 to realize the limiting effect of the shaft groove 7261 on the camshaft 71 .
  • the center of the oil hole 728 is basically on the same plane as the axis of the shaft groove 7261, and the oil hole 728 communicates with the shaft groove 7261, so that the collected lubricating oil flows into the shaft groove 7261 through the oil hole 728, so that the camshaft 71 and the The lubricating effect between the shaft grooves 7261 is better, reducing the wear between the camshaft 71 and the shaft grooves 7261, and preventing the axial movement from increasing too fast.
  • the oil collecting groove 7271 is arranged around the oil through hole 728 , so that the oil collecting groove 7271 surrounds the oil through hole 728 , so that lubricating oil flows into the oil through hole 728 smoothly, and provides good lubricating effect for the camshaft 71 .
  • the lower surface of the shaft seat 72 is the surface opposite to the upper surface of the shaft seat 72 .
  • the position of the oil through hole 728 can be located at any position on the bottom surface of the oil collecting groove 7271, so that the lubricating oil stored in the oil collecting groove 7271 and the oil collecting baffle 7272 flows into the shaft groove 7261 through the oil through hole 728, It is convenient to improve the lubrication effect between the camshaft 71 and the shaft groove 7261, reduce the wear between the camshaft 71 and the shaft groove 7261, and improve the service life of the camshaft 71 and the shaft groove 7261.
  • the position of the oil through hole 728 is set on the lower side of the bottom surface of the oil collecting groove 7271 to facilitate the flow of lubricating oil into the oil through hole 728 .
  • the oil through hole 728, the oil collecting groove 7271 and the oil collecting baffle 7272 can be arranged on any side of the axis of the camshaft 71, so that lubricating oil can enter the shaft groove 7261.
  • the rotation direction of the camshaft 71 includes at least a first direction and a second direction, the first direction refers to the clockwise rotation of the camshaft 71 , and the second direction refers to the counterclockwise rotation of the camshaft 71 .
  • the oil hole 728, the oil collecting groove 7271 and the oil collecting baffle 7272 are set according to the direction of rotation of the camshaft 71.
  • the specific setting method is: when the rotation direction of the camshaft 71 is the first direction, the oil hole 728, the oil collecting groove 7271
  • the oil collecting baffle 7272 is arranged on the side opposite to the rotation direction of the camshaft 71, that is, the positions of the oil through hole 728, the oil collecting groove 7271 and the oil collecting baffle 7272 can change with the rotation direction of the camshaft 71, Therefore, the demand for lubricating oil during the rotation of the camshaft 71 is met.
  • the lubricating oil flowing into the oil passage hole 728 can be driven during the rotation of the camshaft 71, so that the lubricating oil flows along the camshaft 71 The direction of rotation is moved, so that the lubricating effect between the camshaft 71 and the shaft groove 7261 is better.
  • the oil passage hole 728, the oil collection groove 7271 and the oil collection baffle plate 7272 are arranged on the side opposite to the rotation direction of the camshaft 71, that is, the oil passage hole 728,
  • the positions of the oil collecting groove 7271 and the oil collecting baffle 7272 can change along with the rotation direction of the camshaft 71 , so as to meet the demand for lubricating oil during the rotation of the camshaft 71 .
  • the lubricating oil flowing into the oil passage hole 728 can be driven during the rotation of the camshaft 71, so that the lubricating oil flows along the camshaft 71 The direction of rotation is moved, so that the lubricating effect between the camshaft 71 and the shaft groove 7261 is better.
  • a cooling mechanism 21 is also provided in the cylinder head 2.
  • the cooling mechanism 21 includes a cooling water channel 211 for cooling the ignition mechanism 9.
  • the cooling water channel 211 is distributed around the ignition mechanism 9, which is convenient for the ignition mechanism. 9 for cooling to improve the heat dissipation effect of the ignition mechanism 9.
  • An ignition hole 22 is provided at the through line 29, the ignition hole 22 runs through the cylinder head 2, one end of the ignition hole 22 communicates with the cylinder head cover 1, the other end of the ignition hole 22 communicates with the combustion chamber 16, and the ignition hole 22 communicates with one end of the cylinder head cover 1 is the first communication hole 221 , and the end of the ignition hole 22 connected to the combustion chamber 16 is the second communication hole 222 .
  • the first communication hole 221 and the second communication hole 222 communicate with each other.
  • An ignition mechanism 9 is arranged in the ignition hole 22 , and the center line of the ignition hole 22 is basically coincident with the through line 29 , so that the ignition mechanism 9 is located at the center of the cylinder head 2 , which facilitates the installation of the ignition mechanism 9 in the cylinder head 2 .
  • the ignition mechanism 9 includes a spark plug 901 and an ignition coil 902 , one end of the spark plug 901 is at least partially disposed in the ignition coil 902 , and the other end of the spark plug 901 is at least partially disposed at the second communicating hole 222 .
  • the air in the ignition hole 22 will expand, so that the ignition coil 902 is pushed out, resulting in interruption of ignition.
  • the cylinder head cover 1 is provided with a vent hole 23, the vent hole 23 communicates with the ignition hole 22 and runs through the cylinder head cover 1, and the vent hole 23 communicates with the cylinder head cover 1 through the cylinder head cover 1.
  • the outer surface of the cylinder head cover 1 that is, the vent hole 23 communicates to the outside of the cylinder head cover 1 through the cylinder head cover 1 .
  • One end of the air hole 23 is connected to the ignition hole 22, and the other end of the air hole 23 passes through the cylinder head cover 1 to communicate with the outside world, and is used to discharge the air and water in the ignition hole 22 to the outside of the ignition hole 22, thereby balancing the air pressure in the ignition hole 22 And outside air pressure, make ignition mechanism 9 work stably, avoid ignition interruption.
  • the structures of the ignition hole 22 and the ignition mechanism 9 are also adjusted so that a cooling mechanism 21 with a larger cross-sectional area can be arranged around the ignition hole 22 and the ignition mechanism 9, thereby facilitating the cooling of the ignition hole 22 and the ignition mechanism 9, and preventing The ignition coil 902 is ejected to avoid interruption of ignition.
  • the cooling water channel 211 can extend to the second communication hole 222 , so as to increase the volume of the cooling water channel 211 at the spark plug 901 and realize effective cooling of the spark plug 901 .
  • one end of the vent hole 23 communicates with the ignition hole 22, and the other end of the vent hole 23 communicates with the outside world.
  • the fourth communication hole 232 is at least partly arranged on the cylinder head cover 1 and communicates with the outer surface of the cylinder head cover 1, so that the fourth communication hole 232 can communicate with the outside world, thereby balancing the air pressure between the ignition hole 22 and the outside world.
  • the third communication hole 231 and the fourth communication hole 232 communicate with each other.
  • the outer surface of the cylinder head cover 1 is the surface of the cylinder head cover 1 in contact with the outside world.
  • the outer surface of the cylinder head cover 1 is provided with several mounting bolt through holes 101, an oil-gas separation area 102, a secondary gas supply area 103 and a first transmission cavity area 104, and several mounting bolt through holes 101 are used to connect the cylinder head 2 and
  • the secondary air supplement area 103 corresponds to the installation area of the secondary air supplement valve
  • the first transmission chamber area 104 corresponds to the installation area of the valve transmission assembly 15 .
  • the ignition hole 22 runs through the cylinder head cover 1 to communicate with the outside world.
  • the first communication hole 221 is set on the cylinder head cover 1.
  • the oil-gas separation area 102, the secondary air supply area 103 and the first transmission cavity area 104 are distributed around the first communication hole 221.
  • the first communication hole 221 is located between the oil-gas separation area 102 and the secondary gas supply area 103
  • the center point of the first communication hole 221 is basically in the same line as the center point of the first transmission cavity area 104
  • the center point of the first communication hole 221 Basically on the radial centerline of the cylinder head cover 1 .
  • the outer surface of the cylinder head cover 1 basically extends along the third straight line 400
  • the radial centerline of the cylinder head cover 1 refers to the radial centerline parallel to the third straight line 400 .
  • the engine 100 is a two-cylinder engine, that is, when the number of ignition mechanisms 9 is two, the number of ignition holes 22 is two, and the ignition holes 22 include a first ignition hole 223 and a second ignition hole 224 , the center of the first ignition hole 223 and the center of the second ignition hole 224 are both substantially on the radial centerline of the cylinder head cover 1 .
  • there are at least two ventilation holes 23 and the ventilation holes 23 include a first ventilation hole 233 and a second ventilation hole 234 .
  • the first air hole 233 communicates with the first ignition hole 223 and runs through the cylinder head cover 1 , the first air hole 233 communicates with the outer surface of the cylinder head cover 1 through the cylinder head cover 1 , that is, the first air hole 233 passes through the cylinder head cover 1 Connected to the outside of the cylinder head cover 1, so as to discharge the air and water in the first ignition hole 223 to the outside of the first ignition hole 223, and then balance the air pressure in the first ignition hole 223 and the external air pressure, so that the ignition mechanism 9 Stable work to avoid ignition interruption.
  • the second air hole 234 communicates with the second ignition hole 224 and runs through the cylinder head cover 1 , the second air hole 234 communicates with the outer surface of the cylinder head cover 1 through the cylinder head cover 1 , that is, the second air hole 234 communicates through the cylinder head cover 1 to the outside of the cylinder head cover 1, so as to discharge the air and water in the second ignition hole 224 to the outside of the second ignition hole 224, and then balance the air pressure in the second ignition hole 224 and the external air pressure, so that the ignition mechanism 9 can work stably. Avoid ignition interruption.
  • the engine 100 is a single-cylinder engine, that is, when the number of the ignition mechanism 9 is one, the number of the ignition hole 22 is one. At this time, the center of the ignition hole 22 basically coincides with the center of the cylinder head cover 1 .
  • the third straight line 400 is parallel to the second straight line 300 .
  • the orientation of the vent hole 23 is enough to meet the exhaust requirements, and there is no need for a specific orientation of the vent hole 23; the position of the vent hole 23 is sufficient to communicate with the outside world and the ignition hole 22 That is, the position of the vent hole 23 does not need to be specified.
  • the setting direction of the vent hole 23 is: after the engine 100 is installed, the end connected to the ignition hole 22 is lower than the end connected to the outside world, that is, the distance between the third communication hole 231 and the second communication hole 222 is lower than that of the fourth communication hole 222 .
  • the distance between the hole 232 and the second communication hole 222 is short.
  • the spark plug 901 includes a mounting bolt 9011 , a tightening hexagon 9012 and an electrode 9013 .
  • the spark plug 901 is used to discharge the pulsed high-voltage electricity sent by the high-voltage wire, and the pulsed high-voltage electricity breaks down the air between the two electrodes 9013 of the spark plug 901, thereby generating electric sparks and igniting the mixed gas in the combustion chamber 16.
  • the mounting bolt 9011 is used for assembling with the cylinder block 3
  • the tightening hexagon 9012 is used for tightening or unscrewing the spark plug 901
  • the electrode 9013 is used for releasing the pulse high voltage.
  • the length of the mounting bolt 9011 is shorter, the structures such as the hexagon 9012 and the electrode 9013 will be closer to the combustion chamber 16 after tightening, so more heat will be generated, which will affect the heat dissipation effect of the ignition mechanism 9 .
  • the length of the mounting bolt 9011 is short, the cooling effect of the spark plug 901 will be poor, and the temperature of the ignition mechanism 9 will be high, thereby affecting the service life of the ignition mechanism 9 .
  • the air hole 23 is provided on the cylinder head cover 1, and the ignition hole 22 and the ignition
  • the structure of the mechanism 9 is adjusted so that a cooling mechanism 21 with a larger cross-sectional area can be arranged around the ignition hole 22 and the ignition mechanism 9, thereby facilitating the cooling of the ignition hole 22 and the ignition mechanism 9, and preventing the ignition coil 902 from being pushed out, avoiding Ignition interrupted.
  • the cooling water channel 211 can extend to the second communication hole 222 , thereby increasing the volume of the cooling water channel 211 at the spark plug 901 , so that the overall structure of the spark plug 901 is basically within the cooling range of the cooling water channel 211 .
  • the installation bolt 9011 is arranged in the second communication hole 222, the length of the second communication hole 222 and the length of the installation bolt 9011 increase, and the length of the second communication hole 222 and the diameter of the installation bolt 9011 decrease, so that the cooling channel 211 may extend to the second communication hole 222, which improves the cooling effect of the cooling water channel 211 on the spark plug 901.
  • the overall structure of the tightening hexagon 9012 and the electrode 9013 of the spark plug 901 is far away from the second communication hole 222, that is, the overall structure of the tightening hexagon 9012 and the electrode 9013 of the spark plug 901 is far away from the combustion chamber 16, and due to cooling
  • the water channel 211 extends to the second communication hole 222 , therefore, the cooling water channel 211 has a better cooling effect on the ignition mechanism 9 and facilitates the heat dissipation of the ignition mechanism 9 .
  • the cooling water channel 211 includes: the space formed between the top of the combustion chamber 16 wall, the wall of the intake and exhaust mechanism 8, and the wall of the ignition hole 22. The volume and shape of the cooling water channel 211 all depend on the intake and exhaust mechanism 8, the combustion chamber 16. The installation situation of the ignition mechanism 9.
  • the volume of the cooling water channel 211 can be increased by setting the air hole 23 communicating with the ignition hole 22 and the outside world in the cylinder head cover 1, increasing the length of the mounting bolt 9011, etc., so that the cooling water channel 211 is within the maximum range.
  • the ignition mechanism 9 is surrounded, the cooling effect of the ignition mechanism 9 is improved, and the service life of the ignition mechanism 9 is further improved.
  • vent hole 23 discharges the air and water in the ignition hole 22 to the outside of the ignition hole 22, which can balance the air pressure in the ignition hole 22 and the external air pressure, make the ignition mechanism 9 work stably, avoid ignition interruption, and can pass air and The discharge of water takes away part of the heat in the ignition hole 22 , effectively preventing the ignition coil 902 from being pushed out due to the rapid expansion of the air in the ignition hole 22 .
  • the intake and exhaust mechanism 8 is at least partly arranged in the first accommodation space 2011, the intake and exhaust mechanism 8 is used to send fresh air or combustible mixture into the combustion chamber 16, and then The combustion exhaust is vented into the atmosphere.
  • the intake and exhaust mechanism 8 includes an intake mechanism 81 and an exhaust mechanism 82.
  • the intake mechanism 81 and the exhaust mechanism 82 are distributed on both sides of the cylinder head 2, that is, the intake mechanism 81 is distributed on one side of the cylinder head 2.
  • the exhaust mechanism 82 is distributed on the other side inside the cylinder head 2 .
  • the air intake mechanism 81 and the exhaust mechanism 82 are substantially symmetrically distributed with respect to the through line 29 .
  • the intake mechanism 81 is used to introduce air or mixed gas into the cylinder block 3, and the exhaust mechanism 82 is used to collect, purify and discharge exhaust gas.
  • the intake mechanism 81 includes an intake port 812 and a first valve train 811
  • the exhaust mechanism 82 includes an exhaust port 822 and a second valve train 821.
  • the intake port 812 and the exhaust port 822 are substantially symmetrical. Distributed on both sides of the through-line 29, a first valve mechanism 811 is provided between the intake passage 812 and the through-line 29, a second valve mechanism 821 is provided between the exhaust passage 822 and the through-line 29, and the intake passage 812 One end and one end of the exhaust channel 822 are both connected to the outside world.
  • one end of the intake passage 812 communicates with the outside world
  • the other end of the intake passage 812 communicates with the cylinder block 3
  • one end of the exhaust passage 822 communicates with the outside world
  • the other end of the exhaust passage 822 communicates with the cylinder block 3, which is convenient for the cylinder block 3
  • the gas is exchanged with the outside gas.
  • the cylinder head 2 is provided with a first limit mechanism 24 on the side close to the intake passage 812 .
  • the first limiting mechanism 24 is used to limit the first valve mechanism 811 .
  • the first limit mechanism 24 sequentially includes a first tappet hole 241, a first conduit hole 242 and a first seat ring hole 243, and the first valve mechanism 811 sequentially includes a first tappet 8111, a first valve spring 8112, a first valve One end of the first tappet 8111 of the conduit 8113 and the intake valve 8114 is disposed in the first tappet hole 241 , and one end of the first valve spring 8112 is also disposed in the first tappet hole 241 .
  • the other end of the first valve spring 8112 is arranged at the first outer edge 2421 of the first guide hole 242, one end of the first valve guide 8113 is arranged in the first guide hole 242, and the other end of the first valve guide 8113 is arranged at the first guide hole 242.
  • one end of the intake valve 8114 passes through the first valve guide 8113 and the first valve spring 8112 respectively and connects to the first tappet 8111, and the other end of the intake valve 8114 is the intake disc 8114a, the intake disc 8114a is in the shape of a disk, and the outer contour of the intake disk 8114a is basically consistent with the contour of the cylinder head 2, which is convenient for the intake valve 8114 to introduce air or mixed gas into the cylinder block 3.
  • the top of the first tappet 8111 is provided with a first axle 711, and the first axle 711 is provided with a plurality of first cams 73 for controlling the first tappet 8111, and the first tappet 8111 is used to transmit the thrust of the first axle 711 to the first tappet 8111.
  • intake valve 8114 and bear the lateral force applied when the first wheel shaft 711 rotates.
  • the first tappet 8111 is equipped with an adjusting screw at the top, which is used for adjusting the gap of the intake valve 8114.
  • the first outer edge 2421 refers to the edge formed around the surface of the first conduit hole 242 .
  • the first limiting mechanism 24 also includes a first spring seat 244 , and the first spring seat 244 is arranged at the first outer edge 2421 .
  • One end of the first valve spring 8112 is disposed in the first tappet hole 241 , and the other end of the first valve spring 8112 is disposed on the first spring seat 244 .
  • the cylinder head 2 is provided with a second limit mechanism 25 on the side close to the exhaust passage 822 .
  • the second limiting mechanism 25 is used to limit the second valve mechanism 821 .
  • the second limit mechanism 25 includes a second tappet hole 251, a second conduit hole 252 and a second seat ring hole 253 in turn, and the second valve mechanism 821 includes a second tappet 8211, a second valve spring 8212, and a second valve spring 8212 in sequence.
  • one end of the second tappet 8211 is disposed in the second tappet hole 251
  • one end of the second valve spring 8212 is also disposed in the second tappet hole 251 .
  • the other end of the second valve spring 8212 is arranged at the second outer edge 2521 of the second guide hole 252, one end of the second valve guide 8213 is arranged in the second guide hole 252, and the other end of the second valve guide 8213 is arranged at the second guide hole 252.
  • one end of the exhaust valve 8214 passes through the second valve guide 8213 and the second valve spring 8212 respectively and then connects to the second tappet 8211, and the other end of the exhaust valve 8214 is the exhaust disc 8214a, the exhaust disc 8214a is in the shape of a disk, and the outer contour of the exhaust disk 8214a is basically consistent with the contour of the cylinder head 2, which is convenient for the exhaust valve 8214 to collect, purify and discharge the exhaust gas generated.
  • the top of the second tappet 8211 is provided with a second axle 712, and the second axle 712 is provided with several second cams 74 for controlling the second tappet 8211.
  • the second tappet 8211 is used to transmit the thrust of the second axle 712 to Exhaust valve 8214, and bear the lateral force applied when the second axle 712 rotates.
  • the second tappet 8211 is equipped with an adjusting screw at the top, which is used for adjusting the gap of the exhaust valve 8214.
  • the second outer edge 2521 refers to the edge formed around the surface of the second conduit hole 252 .
  • the second limiting mechanism 25 also includes a second spring seat 254 , and the second spring seat 254 is arranged at the second outer edge 2521 .
  • One end of the second valve spring 8212 is disposed in the second tappet hole 251 , and the other end of the second valve spring 8212 is disposed on the second spring seat 254 .
  • the first valve guide 8113 is used to guide the movement of the intake valve 8114 to ensure that the intake valve 8114 makes a reciprocating linear motion and transfer the heat of the intake valve 8114 to the cylinder head 2;
  • the second valve guide 8213 is used to The exhaust valve 8214 is motion-guided to ensure that the exhaust valve 8214 makes a reciprocating linear motion and transfers the heat of the exhaust valve 8214 to the cylinder head 2 .
  • the first valve guide 8113 is pressed into the first guide hole 242 on the cylinder head 2 through an interference fit, and the second valve guide 8213 is pressed into the second guide hole 252 on the cylinder head 2 through an interference fit, thereby preventing the first Valve guide 8113 and second valve guide 8213 fall off.
  • the crankshaft 131 controls the rotation of the first wheel shaft 711 through the valve transmission assembly 15 (as shown in FIG. 8 ), thereby controlling several first cams 73 to drive the intake valve 8114 to open or close. And ensure that the opening and closing action of the intake valve 8114 is synchronized with the crank connecting rod 132 mechanism; the crankshaft 131 controls the rotation of the second wheel shaft 712 through the valve drive assembly 15, thereby controlling several second cams 74 to drive the exhaust valve 8214 to open, and ensuring that the exhaust valve 8214 is opened. The opening and closing action of the valve 8214 is synchronized with the crank.
  • the valve transmission assembly 15 includes a timing chain 151 , and the timing chain 151 is respectively connected to the crankshaft 131 , the first wheel shaft 711 and the second wheel shaft 712 .
  • the crankshaft 131, the first axle 711 and the second axle 712 are connected by the timing chain 151, so that the crankshaft 131 can drive the first axle 711 and the second axle 712 to rotate, and the first axle 711 drives the first cam 73 to drive the intake valve 8114 to open Or closed, the second axle 712 drives the exhaust valve 8214 to open or close, thereby ensuring that the opening and closing actions of the intake valve 8114 and the exhaust valve 8214 are synchronized with the crank.
  • the camshaft 71 includes a first axle 711 and a second axle 712 .
  • the timing chain 151 connects the crankshaft 131 , the first wheel shaft 711 and the second wheel shaft 712 , that is, the timing chain 151 connects the crankshaft 131 and the camshaft 71 . Since several first cams 73 are arranged in different directions on the first wheel shaft 711, and several second cams 74 are arranged in different directions on the second wheel shaft 712, therefore, the crankshaft 131 can be reasonably controlled by driving the camshaft 71. The opening and closing of valve 8114 and exhaust valve 8214.
  • the first limiting mechanism 24 also includes an intake seat ring 245
  • the second limiting mechanism 25 also includes an exhaust seat ring 255 .
  • the intake seat ring 245 is arranged at the place where the other end of the intake passage 812 communicates with the cylinder block 3 .
  • the intake seat ring 245 is fixed in the first seat ring hole 243 through an interference fit with the first seat ring hole 243 .
  • the exhaust seat ring 255 is arranged at the place where the other end of the exhaust passage 822 communicates with the cylinder block 3 .
  • the exhaust seat ring 255 is fixed in the second seat ring hole 253 through an interference fit with the second seat ring hole 253 .
  • the axis of the intake valve 8114 and the axis of the exhaust valve 8214 are basically on the same plane, so that the intake and exhaust of the engine 100 are synchronized, and the control of the intake and exhaust of the engine 100 can be realized more smoothly. Gas, so that there is enough air pressure in the cylinder when engine 100 is working.
  • the intake mechanism 81 basically extends along the direction of the fourth straight line 700
  • the exhaust mechanism 82 basically extends along the direction of the fifth straight line 800
  • the first valve mechanism 811 basically extends along the direction of the fourth straight line 700
  • the intake valve 8114 basically extends along the direction of the fourth straight line 700
  • the second valve mechanism 821 extends substantially along the direction of the fifth straight line 800
  • the exhaust valve 8214 substantially extends along the direction of the fifth straight line 800 .
  • the engine 100 includes a projection plane 900 perpendicular to the axis of the crankshaft 131 (as shown in FIG. 3 ). As shown in FIG.
  • the cylinder block 3 basically extends along the direction of the first straight line 500 , and the cylinder block 3 is arranged substantially symmetrically with respect to the first straight line 500 .
  • the fourth straight line 700 is perpendicular to the first straight line 500
  • the fifth straight line 800 is perpendicular to the second straight line 500
  • the projection plane 900 is substantially perpendicular to the first straight line 500 .
  • the projection of the fourth straight line 700 on the projection plane 900 is the first projection line
  • the projection of the fifth straight line 800 on the projection plane 900 is the second projection line
  • the projection of the through line 29 on the projection plane 900 is third projection line.
  • the acute angle formed by the first projection line and the third projection line is a first included angle ⁇
  • the acute angle formed by the second projection line and the third projection line is a second included angle ⁇ .
  • the intake mechanism 81 has a center line extending substantially along the direction of the fourth straight line 700
  • the first valve mechanism 811 has a center line substantially extending along the direction of the fourth straight line 700
  • the intake valve 8114 has a center line substantially extending along the direction of the fourth straight line 700.
  • the projection of the centerline of the intake mechanism 81 on the projection plane 900 basically coincides with the first projection line
  • the projection of the centerline of the first valve mechanism 811 on the projection plane 900 basically coincides with the first projection line
  • the projection of the axis of the intake valve 8114 on the projection plane 900 basically coincides with the first projection line.
  • the exhaust mechanism 82 has a centerline extending substantially along the fifth straight line 800
  • the second valve mechanism 821 has a centerline extending substantially along the fifth straight line 800
  • the exhaust valve 8214 has a centerline substantially extending along the fifth straight line 800.
  • the projection of the centerline of the exhaust mechanism 82 on the projection plane 900 basically coincides with the second projection line
  • the projection of the centerline of the second valve mechanism 821 on the projection plane 900 basically coincides with the second projection line
  • the projection of the axis of the exhaust valve 8214 on the projection plane 900 basically coincides with the second projection line.
  • the angle formed by the projection of the first projection line and the third projection line on the projection plane 900 is the first angle ⁇ , that is, the center line of the air intake mechanism 81 and
  • the included angle formed by the projection of the penetrating line 29 on the projection plane 900 is the first included angle ⁇
  • the included angle formed by the centerline of the first valve mechanism 811 and the projection of the penetrating line 29 on the projection plane 900 is the first included angle ⁇
  • the angle formed by the axis of the intake valve 8114 and the projection of the penetration line 29 on the projection plane 900 is the first angle ⁇ .
  • the angle formed by the projection of the second projection line and the third projection line on the projection plane 900 is the second angle ⁇ , that is, the central line of the exhaust mechanism 82 and the through-line 29 on the projection plane
  • the included angle formed by the projection of 900 is the second included angle ⁇
  • the included angle formed by the projection of the center line of the second valve mechanism 821 and the through line 29 on the projection plane 900 is the second included angle ⁇
  • the included angle formed by the axis and the projection of the penetrating line 29 on the projection plane 900 is the second included angle ⁇ .
  • the angles of the first included angle ⁇ and the second included angle ⁇ may be substantially the same, that is, the first projection line and the second projection line are substantially symmetrically arranged with respect to the third projection line.
  • the cylinder block 3 includes a cylinder bore 301 .
  • the diameter of the cylinder bore 301 is greater than or equal to 70mm and less than or equal to 74mm
  • the first included angle ⁇ is greater than or equal to 11° and less than or equal to 15°
  • the second included angle ⁇ is greater than or equal to 11° and less than or equal to 15° .
  • the diameter of the cylinder bore 301 refers to the diameter of the cylinder bore 301 of the cylinder block 3 .
  • the included angle between the centerline of the intake mechanism 81 and the projection of the penetration line 29 on the projection plane 900 is Greater than or equal to 11° and less than or equal to 15°
  • the angle formed by the centerline of the first valve mechanism 811 and the projection of the through line 29 on the projection plane 900 is greater than or equal to 11° and less than or equal to 15°
  • the axis of the intake valve 8114 The included angle formed by the projection of the through line 29 on the projection plane 900 is greater than or equal to 11° and less than or equal to 15°.
  • the included angle formed by the projection of the central line of the exhaust mechanism 82 and the penetration line 29 on the projection plane 900 is greater than or equal to 11 ° and less than or equal to 15°
  • the angle formed by the centerline of the second valve mechanism 821 and the projection of the through-line 29 on the projection plane 900 is greater than or equal to 11° and less than or equal to 15°
  • the axis of the exhaust valve 8214 and the through-line is greater than or equal to 11° and less than or equal to 15°.
  • a reasonable arrangement angle is adopted, which can make the intake volume of the engine 100 more reasonable, thereby making the operation of the engine 100 more stable and improving the service life of the engine 100;
  • the distribution of the exhaust temperature field of the engine 100 is reasonable, so that the heat dissipation effect of the engine 100 during exhaust can be improved, the cooling of the engine 100 is facilitated, and the balance between the intake and exhaust of the engine 100 is realized, and the heat dissipation effect and the use of the engine 100 are improved. life.
  • the first included angle ⁇ is greater than or equal to 12° and less than or equal to 14°
  • the second included angle ⁇ is greater than or equal to 12° and less than or equal to equal to 14°
  • the included angle between the center line of the intake mechanism 81 and the projection of the penetration line 29 on the projection plane 900 is Greater than or equal to 12° and less than or equal to 14°
  • the angle formed by the centerline of the first valve mechanism 811 and the projection of the through line 29 on the projection plane 900 is greater than or equal to 12° and less than or equal to 14°
  • the axis of the intake valve 8114 The included angle formed by the projection of the through line 29 on the projection plane 900 is greater than or equal to 12° and less than or equal to 14°.
  • the included angle formed by the center line of the exhaust mechanism 82 and the projection of the through line 29 on the projection plane 900 is greater than or equal to 12 ° and less than or equal to 14°
  • the angle formed by the centerline of the second valve mechanism 821 and the projection of the through-line 29 on the projection plane 900 is greater than or equal to 12° and less than or equal to 14°
  • the included angle formed by the projection of 29 on the projection plane 900 is greater than or equal to 12° and less than or equal to 14°.
  • the first included angle ⁇ is 13°
  • the second included angle ⁇ is 13°.
  • the diameter of the cylinder bore 301 is 72 mm
  • the angle formed by the center line of the intake mechanism 81 and the projection of the through line 29 on the projection plane 900 is 13°
  • the first valve The angle formed by the centerline of the mechanism 811 and the projection of the penetration line 29 on the projection plane 900 is 13°
  • the angle formed by the axis of the intake valve 8114 and the projection of the penetration line 29 on the projection plane 900 is 13°.
  • the included angle formed by the center line of the exhaust mechanism 82 and the projection of the penetration line 29 on the projection plane 900 is 13°
  • the second valve mechanism 821 The angle formed by the projection of the central line and the penetration line 29 on the projection plane 900 is 13°
  • the angle formed by the axis of the exhaust valve 8214 and the projection of the penetration line 29 on the projection plane 900 is 13°.
  • the intake volume of the engine 100 can be made more reasonable, thereby making the operation of the engine 100 more stable; and the distribution of the exhaust temperature field of the engine 100 can be made more reasonable, thereby The cooling effect of the engine 100 during exhaust can be improved, and the cooling of the engine 100 is facilitated.
  • the first limiting mechanism 24 further includes a first locking seat 246 .
  • the first locking seat 246 is at least partially disposed between the first tappet 8111 and the first valve spring 8112 .
  • One end of the first valve spring 8112 is set on the first spring seat 244 , and the other end of the first valve spring 8112 is set on the first lock seat 246 .
  • the first lock seat 246 is used to fix one end of the first valve spring 8112 .
  • the first lock seat 246 is provided with a first lock clip 247, and the first lock clip 247 is used to limit the radial movement of the first valve spring 8112 and the intake valve 8114, that is, the first valve spring 8112 and the intake valve 8114 only moves in the direction of the fourth straight line 700 so that the intake mechanism 81 can introduce air or mixed gas into the cylinder block 3 .
  • the second limiting mechanism 25 also includes a second locking seat 256 .
  • the second lock seat 256 is at least partially disposed between the second tappet 8211 and the second valve spring 8212 .
  • One end of the second valve spring 8212 is arranged on the second spring seat 254 , and the other end of the second valve spring 8212 is arranged on the second lock seat 256 .
  • the second lock seat 256 is used to fix one end of the second valve spring 8212 .
  • the second lock seat 256 is provided with a second lock clip 257, and the second lock clip 257 is used to limit the movement of the second valve spring 8212 and the exhaust valve 8214 in the radial direction, that is, to make the second valve spring 8212 and the exhaust valve 8214 only moves in the direction of the fifth straight line 800 so that the exhaust mechanism 82 collects, purifies and discharges the generated exhaust gas.
  • the end of the intake valve 8114 close to the first tappet 8111 is an intake rod 8114b
  • the end of the exhaust valve 8214 close to the second tappet 8211 is an exhaust rod 8214b.
  • the first lock clip 247 locks the first valve spring 8112 and the intake rod 8114b
  • the second lock clip 257 locks the first valve spring 8114b
  • Two valve springs 8212 and exhaust lever 8214b are locked.
  • the intake rod 8114b is integrated with the intake disc 8114a, and the intake rod 8114b passes through the first valve guide 8113 and the first valve spring 8112 in sequence and connects to the first tappet 8111.
  • the exhaust rod 8214b is integrated with the exhaust disk 8214a, and the exhaust rod 8214b passes through the second valve duct and the second valve spring 8212 in turn and connects to the second tappet 8211.
  • the intake rod 8114b has an axis extending along the direction of the fourth straight line 700
  • the exhaust rod 8214b has an axis extending along the direction of the fifth straight line 800 .
  • the projection of the axis of the intake rod 8114b on the projection plane 900 basically coincides with the first projection line
  • the projection of the axis of the exhaust rod 8214b on the projection plane 900 basically coincides with the second projection line.
  • the angle formed by the axis of the intake rod 8114b and the projection of the penetration line 29 on the projection plane 900 is greater than or equal to It is equal to 11° and less than or equal to 15°
  • the included angle between the axis of the exhaust rod 8214b and the projection of the through line 29 on the projection plane 900 is greater than or equal to 11° and less than or equal to 15°.
  • the angle formed by the axis of the intake rod 8114b and the projection of the penetration line 29 on the projection plane 900 is 13 °
  • the angle formed by the axis of the exhaust rod 8214b and the projection of the penetration line 29 on the projection plane 900 is 13°.
  • the angle formed by the axis of the intake rod 8114b and the projection of the penetration line 29 on the projection plane 900 is greater than or equal to It is equal to 12° and less than or equal to 14°
  • the included angle between the axis of the exhaust rod 8214b and the projection of the through line 29 on the projection plane 900 is greater than or equal to 12° and less than or equal to 14°.
  • the included angle formed by the axis of the intake rod 8114b and the projection of the penetration line 29 on the projection plane 900 is 13°.
  • the included angle formed by the axis of the gas rod 8214b and the projection of the penetration line 29 on the projection plane 900 is 13°.
  • a reasonable arrangement angle is adopted, which can make the intake volume of the engine 100 more reasonable, thereby making the operation of the engine 100 more stable and improving the service life of the engine 100 can make the exhaust temperature field distribution of engine 100 more reasonable again, thereby can improve the cooling effect of engine 100 when exhausting, be convenient to the cooling of engine 100, and then realize the balance between engine 100 air intake and exhaust, improve The cooling effect and service life of the engine 100.
  • the cylinder head 2 is fixedly connected to the cylinder block 3, and the fixed connection between the cylinder head 2 and the cylinder block 3 is the first fixed portion 307 (as shown in FIG. 5 ), and the cylinder head 2 is close to the first fixed portion 307.
  • One side is the bottom of the cylinder head 2
  • the surface of the cylinder head 2 close to the first fixing portion 307 is the bottom surface of the cylinder head 2 .
  • the cylinder block 3 includes a cylinder hole 301, and the bottom of the cylinder head 2 is provided with several cylinder ports 26, each cylinder port 26 is all communicated with a cylinder hole 301, and several cylinder ports 26 are distributed around A cooling mechanism 21 is provided.
  • the cooling mechanism 21 includes several cooling water passages 211, and the several cooling water passages 211 surround several cylinder ports 26, so as to improve the cooling effect of the cylinder head 2, so that each component in the cylinder head 2 can be better cooled, which is beneficial to improve the cooling effect of the cylinder head 2. service life of the engine 100.
  • the bottom of the cylinder head 2 is also provided with a first hole assembly 27 and a second transmission cavity area 28 .
  • the first hole assembly 27 includes several cylinder head bolt through holes 271 and a first oil return hole 272
  • the several cylinder head bolt through holes 271 include several cylinder head bolt large holes 2711 and several cylinder head bolt small holes 2712 .
  • a number of cylinder head bolt large holes 2711 are evenly distributed around the cylinder port 26, which facilitates the fixing of the cylinder head 2 and the cylinder block 3 during the installation process, and improves the connection stability between the cylinder head 2 and the cylinder block 3.
  • the cylinder head 2 is arranged substantially symmetrically with respect to the through-line 29 .
  • the second transmission cavity area 28 is located on one side of the cylinder port 26, and the center of the second transmission cavity area 28 and the center of the cylinder port 26 are basically on the through line 29, that is, the center of the second transmission cavity area 28 and the cylinder port.
  • the centers of 26 are basically on the same straight line.
  • the second transmission cavity area 28 is used for setting the valve transmission assembly 15, which is convenient for the valve transmission assembly 15 to pass through the cylinder head 2, so that the valve transmission assembly 15 is respectively connected to the crankshaft 131 and the cam mechanism 7 to realize the driving effect of the crankshaft 131 on the cam mechanism 7 .
  • a number of cylinder head bolt holes 2712 are evenly distributed around the second transmission cavity area 28, which can not only realize the function of fixing the cylinder head 2 and the cylinder block 3, but also fix the second transmission cavity area 28 on the cylinder block 3, thereby A stable connection between the cylinder head 2 and the cylinder block 3 is realized.
  • the first oil return hole 272 is arranged around several cylinder head bolt passing holes 271.
  • the first oil return hole 272 is the flow channel of the lubricating oil inside the engine 100, which is beneficial to the circulation flow of the lubricating oil in the engine 100, thereby improving the engine 100. Lubrication between internal parts, thereby increasing the service life of the engine 100 .
  • the number of the intake and exhaust mechanism 8 is one, and the number of the intake mechanism 81 and the exhaust mechanism 82 are two; when the engine 100 is a two-cylinder engine, the intake and exhaust mechanism 8
  • the number of mechanisms 8 is two, and the number of intake mechanisms 81 and exhaust mechanisms 82 are four; that is, one intake and exhaust mechanism 8 includes two intake mechanisms 81 and two exhaust mechanisms 82 .
  • one cylinder port 26 is provided with two intake mechanisms 81 and two exhaust mechanisms 82, the two intake mechanisms 81 include a first intake mechanism 813 and a second intake mechanism 814, and the two exhaust mechanisms 82 includes a first exhaust mechanism 823 and a second exhaust mechanism 824 .
  • the center distance between the first air intake mechanism 813 and the second air intake mechanism 814 is the first center distance J
  • the center distance between the first exhaust mechanism 823 and the second air intake mechanism 824 is the second center distance J.
  • Center distance K is the center distance between the first air intake mechanism 813 and the second air intake mechanism 814
  • the first exhaust mechanism 823 refers to the shortest distance between the center of the first exhaust mechanism 823 and the center of the second intake mechanism 824 .
  • two intake seat rings 245 and two exhaust seat rings 255 are provided at the cylinder port 26 .
  • the intake seat ring 245 is arranged on the side close to the intake mechanism 81 , and is used to cooperate with the intake valve 8114 so that the intake mechanism 81 can introduce air or mixed gas into the cylinder block 3 .
  • the exhaust seat ring 255 is arranged on the side close to the exhaust mechanism 82, and is used to cooperate with the exhaust valve 8214 to realize the collection, purification and discharge of the exhaust gas generated by the exhaust mechanism 82.
  • the two intake seat rings 245 are symmetrically distributed with respect to the radial centerline of the cylinder port 26
  • the two exhaust seat rings 255 are symmetrically distributed with respect to the radial centerline of the cylinder port 26 .
  • the radial centerline of the cylinder port 26 refers to the radial centerline of the cylinder port 26 along the direction from the intake passage 812 to the exhaust passage 822 .
  • the diameter of the cylinder bore 301 is 72mm, by adopting a reasonable spacing between the intake and exhaust valves 8214, the engine 100 is smaller in size and lighter in weight, and the heat dissipation and heat dissipation of the cylinder head 2 are improved.
  • the temperature field distribution is more reasonable.
  • the diameter of the cylinder bore 301 refers to the diameter of the cylinder bore 301 of the cylinder block 3 .
  • the first intake mechanism 813 includes a first intake valve
  • the second intake mechanism 814 includes a second intake valve
  • the center distance between the first intake valve and the second intake valve is 32.2mm, that is The center distance between the first intake valve and the second intake valve is substantially the first center distance J.
  • the first exhaust mechanism 823 includes a first exhaust valve
  • the second intake mechanism 824 includes a second exhaust valve.
  • the center distance between the first exhaust valve and the second exhaust valve is 29.1mm, that is, the first row
  • the center distance between the valve and the second exhaust valve is substantially the second center distance K.
  • the center distance between the first intake valve and the second intake valve refers to the shortest distance between the center of the first intake valve and the center of the second intake valve
  • the distance between the first exhaust valve and the second exhaust valve Center distance refers to the shortest distance between the center of the first exhaust valve and the center of the second exhaust valve
  • a reasonable arrangement distance is adopted, which can make the intake volume of the engine 100 more reasonable, thereby making the operation of the engine 100 more stable and improving the service life of the engine 100 can make the exhaust temperature field distribution of engine 100 more reasonable again, thereby can improve the cooling effect of engine 100 when exhausting, be convenient to the cooling of engine 100, and then realize the balance between engine 100 air intake and exhaust, improve The cooling effect and service life of the engine 100.
  • the structure of the engine 100 is made more compact, the space utilization rate of the engine 100 is improved, and the waste of resources is reduced, so that the intake mechanism 81 and the exhaust mechanism 82 The structure is more reasonable, and the service life of the intake and exhaust mechanism 8 is improved, thereby improving the service life of the engine 100.
  • the center distance between the first intake valve and the second intake valve is calculated by parameters such as the disc diameter of the intake disc 8114a, the thickness of the nose bridge, and the wall thickness between the first intake valve and the second intake valve;
  • the center distance between the first exhaust valve and the second exhaust valve is calculated by parameters such as the disk diameter of the exhaust disc 8214a, the thickness of the nose bridge, the wall thickness between the first exhaust valve and the second exhaust valve, and the thickness of the nose bridge Refers to the wall thickness between the adjacent intake valve 8114 and exhaust valve 8214.
  • the first center distance J can be adjusted by a distance of 1 to 2 mm, that is, the first center distance J can be greater than or equal to 30.2 mm and less than or equal to 34.2 mm
  • the center distance between the first air intake mechanism 813 and the second air intake mechanism 814 may be greater than or equal to 30.2mm and less than or equal to 34.2mm, so as to adapt to the overall structure of the engine 100;
  • the second center distance K can be adjusted by a distance of 1 to 2mm, that is, the second center distance K can be greater than or equal to 27.1mm and less than or equal to 31.1mm
  • the first exhaust mechanism 823 and the second air intake mechanism 824 The center-to-center distance may be greater than or equal to 27.1 mm and less than or equal to 31.1
  • the center distance between the first intake valve and the second intake valve can be adjusted by 1 to 2 mm, that is, the distance between the first intake valve and the second intake valve
  • the center distance of the door can be greater than or equal to 30.2mm and less than or equal to 34.2mm to adapt to the overall structure of the engine 100;
  • the first exhaust valve and the second exhaust valve The center distance of the doors can be adjusted by 1-2 mm, that is, the center distance between the first exhaust valve and the second exhaust valve can be greater than or equal to 27.1 mm and less than or equal to 31.1 mm, so as to adapt to the overall structure of the engine 100 .
  • the center distance between the first intake valve and the second intake valve refers to the shortest distance between the center of the first intake valve and the center of the second intake valve, specifically refers to the distance between the centers of the two intake discs 8114a shortest distance.
  • the center distance between the first exhaust valve and the second exhaust valve refers to the shortest distance between the center of the first exhaust valve and the center of the second exhaust valve, specifically the shortest distance between the centers of two exhaust discs 8214a .
  • the distance adjustment of 1 ⁇ 2mm refers to: adjust the distance between the original center distance of the first intake valve and the second intake valve by 1 ⁇ 2mm before and after, or adjust the original center distance of the first exhaust valve and the second exhaust valve. Adjust the distance value by 1 ⁇ 2mm before and after, or adjust the original center distance value of the first intake valve and the second intake valve, and the original center distance value of the first exhaust valve and the second exhaust valve before and after. ⁇ 2mm distance adjustment.
  • the first intake valve includes a first intake disk
  • the second intake valve includes a second intake disk
  • the first exhaust valve includes a first exhaust disk
  • the second exhaust valve includes a second exhaust pan.
  • the center distance between the first air intake disk and the second air intake disk can be greater than or equal to 30.2mm and less than or equal to 34.2mm, that is, the first air intake disk and the second air intake disk
  • the center distance between the two intake disks is basically the first center distance J, so as to adapt to the overall structure of the engine 100;
  • the center distance between the first exhaust disk and the second exhaust disk can be greater than or equal to 27.1mm and less than or equal to 31.1mm, that is
  • the center distance between the first exhaust pan and the second exhaust pan is basically the second center distance K, so as to adapt to the overall structure of the engine 100 .
  • the center-to-center distance between the first air intake disk and the second air intake disk refers to the shortest distance between the center of the first air intake disk and the center of the second air intake disk;
  • the center distance refers to the shortest distance between the center of the first exhaust disk and the center of the second exhaust disk.
  • the first center distance J may be greater than or equal to 31.2 mm and less than or equal to 33.2 mm
  • the first air intake mechanism 813 and the second air intake mechanism The center distance between the mechanisms 814 may be greater than or equal to 31.2 mm and less than or equal to 33.2 mm
  • the second center distance K may be greater than or equal to 28.1 mm and less than or equal to 30.1 mm
  • the first exhaust mechanism 823 and the second air intake mechanism 824 The center distance may be greater than or equal to 28.1 mm and less than or equal to 30.1 mm, so as to adapt to the overall structure of the engine 100 .
  • the center distance between the first intake valve and the second intake valve may be greater than or equal to 31.2mm and less than or equal to 33.2mm, and the first exhaust valve The distance between the centers of the second exhaust valve and the second exhaust valve may be greater than or equal to 28.1 mm and less than or equal to 30.1 mm, so as to adapt to the overall structure of the engine 100 .
  • the center distance between the first air intake disk and the second air intake disk may be greater than or equal to 31.2mm and less than or equal to 33.2mm
  • the first The center distance between the exhaust disk and the second exhaust disk may be greater than or equal to 28.1 mm and less than or equal to 30.1 mm, so as to adapt to the overall structure of the engine 100 .
  • the cylinder block 3 is provided with a cylinder hole 301 and a third transmission cavity area 303, and the center of the cylinder hole 301 and the center of the third transmission cavity area 303 are basically on the center line of the cylinder block 3, that is, the third The center of the transmission cavity area 303 and the center of the cylinder bore 301 are basically on the same straight line.
  • the center line of the cylinder block 3 refers to the center line of the cylinder block 3 along the direction of the first straight line 500, and the center line of the cylinder block 3 basically coincides with the first straight line 500, and the first straight line 500 and the second straight line 300, Three straight lines 400 parallel.
  • the quantity of the cylinder bore 301 is one, and the distribution direction of the cylinder bore 301 and the third transmission cavity area 303 is along the direction of the first straight line 500;
  • the cylinder bore The number of 301 is two, and the cylinder bore 301 includes a first cylinder bore 3011 and a second cylinder bore 3012 .
  • the first cylinder hole 3011 and the second cylinder hole 3012 are not connected to each other, and the diameter of the first cylinder hole 3011 is basically the same as that of the second cylinder hole 3012 .
  • the bore diameter of the first cylinder hole 3011 refers to the diameter of the first cylinder bore 3011
  • the bore diameter of the second cylinder bore 3012 refers to the diameter of the second cylinder bore 3012
  • the distribution direction of the first cylinder hole 3011, the second cylinder hole 3012 and the third transmission cavity area 303 is along the direction of the first straight line 500, the arrangement of the first cylinder hole 3011, the second cylinder hole 3012 and the third transmission cavity area 303 These are the first cylinder bore 3011, the second cylinder bore 3012, and the third transmission chamber area 303 in sequence.
  • the third transmission cavity area 303 is used for setting the valve transmission assembly 15, which is convenient for the valve transmission assembly 15 to pass through the cylinder block 3, so that the valve transmission assembly 15 is respectively connected to the crankshaft 131 and the cam mechanism 7 to realize the driving effect of the crankshaft 131 on the cam mechanism 7 .
  • the cylinder block 3 is provided with several first fixing holes 304 and second oil return holes 305, and the several first fixing holes 304 are evenly distributed around the cylinder hole 301, so that the cylinder head 2 and the cylinder block 3 can be connected easily during the fixing process.
  • the fixing is not only conducive to improving the connection stability between the cylinder head 2 and the cylinder block 3, but also conducive to improving the connection stability between the cylinder block 3 and the crankcase 4.
  • the second oil return hole 305 is arranged around several first fixing holes 304, and cooperates with the first oil return hole 272 to form a flow passage of lubricating oil inside the engine 100, which is beneficial to the circulating flow of lubricating oil in the engine 100, thereby improving
  • the lubricating effect between the internal parts of the engine 100 further improves the service life of the engine 100 .
  • the cylinder block 3 is provided with a cylinder block edge 306, and the cylinder block edge 306 is arranged around the cylinder block 3, and several first fixing holes 304 and second oil return holes 305 are all arranged on the cylinder block edge 306, and several first Both the fixing hole 304 and the second oil return hole 305 pass through the edge of the cylinder block 306, which is convenient for connecting the cylinder block 3 and the cylinder head 2 through several first fixing holes 304, and is convenient for connecting the cylinder block 3 through several first fixing holes 304 and crankcase 4.
  • a cooling water jacket 302 is provided in the cylinder block 3, and the cooling water jacket 302 is evenly distributed around the cylinder bore 301, so that the cooling water jacket 302 surrounds the cylinder bore 301, thereby improving the cooling effect of the cooling water jacket 302 on the cylinder bore 301, and further Increase the service life of the engine 100 .
  • the cooling water jacket 302 surrounds the cylinder bore 301, and the inner contour of the cooling water jacket 302 is basically the same as the outer contour of the cylinder bore 301, so that the cooling water jacket 302 can better cool the cylinder bore 301. , thereby improving the cooling effect on the piston mechanism 11 , and further improving the cooling effect of the engine 100 .
  • the cooling water jacket 302 surrounds the first cylinder hole 3011 and the second cylinder hole 3012, and the combination of the first cylinder hole 3011 and the second cylinder hole 3012 forms a first outer contour, and the cooling water jacket 302
  • the inner contour of the cooling water jacket 302 is basically the same as the first outer contour, and the cooling water jacket 302 surrounds the first cylinder bore 3011 and the second cylinder bore 3012 in an "8" shape, so that the cooling water jacket 302 can better cool the cylinder bore 301, thereby improving the The cooling effect of the piston mechanism 11 further improves the cooling effect of the engine 100 .
  • the inner contour of the cooling water jacket 302 refers to the contour close to the cylinder bore 301
  • the outer contour of the cylinder bore 301 refers to the contour near the cooling water jacket 302
  • the first outer contour refers to the first cylinder bore 3011 and the second cylinder bore 3012 arranged on After the cylinder block 3 is centered, the first cylinder hole 3011 and the second cylinder hole 3012 form a substantially "8"-shaped outer contour.
  • the piston mechanism 11 is arranged in the cylinder hole 301, and the number of the piston mechanism 11 is consistent with the number of the cylinder hole 301, which facilitates the reciprocating movement of the piston mechanism 11 in the cylinder hole 301, and the piston mechanism can be limited by the cylinder hole 301.
  • the position of the mechanism 11 also enables the cooling water jacket 302 to cool the piston mechanism 11 through the cylinder hole 301 , so as to improve the heat dissipation effect of the piston mechanism 11 .
  • cooling liquid is provided in the cooling water jacket 302 , and the cooling liquid can flow in the cooling water jacket 302 , so as to realize cooling of the piston mechanism 11 through the cylinder hole 301 . As shown in FIG.
  • the piston mechanism 11 includes a piston 111 and a piston pin 112 , and the piston 111 and the connecting rod 132 are connected through the piston pin 112 .
  • the number of pistons 111 is consistent with the number of cylinder holes 301, which facilitates the reciprocating movement of the pistons 111 in the cylinder holes 301.
  • the position of the pistons 111 can be limited by the cylinder holes 301, and the cooling water jacket 302 can pass through the cylinder holes 301 to cool the pistons 111 , so as to improve the cooling effect of the piston 111.
  • the distance between the cylinder centers of the first cylinder bore 3011 and the second cylinder bore 3012 is the cylinder center distance L
  • the cylinder center distance L passes through the
  • the wall thickness between the first cylinder bore 3011 and the second cylinder bore 3012 and the bore diameter of the cylinder bore 301 are calculated to facilitate the best cylinder center distance of the twin-cylinder engine, so that the engine 100 has a smaller overall size and lighter weight, and can be fully utilized
  • the space of the cylinder block 3 is increased, so that the heat dissipation and temperature field distribution of the cylinder block 3 are more reasonable, thereby improving the heat dissipation effect of the cylinder block 3 and the piston mechanism 11, improving the service life of the cylinder block 3 and the piston mechanism 11, and then improving the engine 100.
  • the wall thickness between the first cylinder hole 3011 and the second cylinder hole 3012 is the wall thickness between cylinders
  • the cylinder center distance L refers to the center of the first cylinder hole 3011 and the center of the second cylinder hole 3012.
  • the distance between the centers; the bore diameter of the cylinder bore 301 refers to the diameter of the cylinder bore 301 of the cylinder block 3 .
  • the factor affecting the cylinder center distance L is the wall thickness between cylinders.
  • the wall thickness between the cylinders is too thick, the lateral dimension of the engine 100 will be increased, which is not conducive to the cooling of the engine 100 .
  • the inter-cylinder wall thickness of 7 mm is already a relatively excellent level, therefore, the cylinder center distance L can be obtained by adding the inter-cylinder wall thickness and the diameter of the cylinder bore 301 .
  • the engine 100 when the engine 100 is a two-cylinder engine and the bore diameter of the cylinder bore 301 is greater than or equal to 70mm and less than or equal to 74mm, it can be obtained by calculating the inter-cylinder wall thickness and the bore diameter of the cylinder bore 301, the first cylinder bore 3011 and the second cylinder bore
  • the cylinder center distance L of 3012 is greater than or equal to 76mm and less than or equal to 82mm.
  • the external dimension of engine 100 is smaller, lighter in weight, and overall structure is comparatively compact, makes full use of the space of cylinder block 3, makes the heat radiation of cylinder block 3 and temperature field distribution more reasonable, thereby improves cylinder block 3 and piston mechanism.
  • 11 improves the service life of the cylinder block 3 and the piston mechanism 11, thereby improving the heat dissipation effect and service life of the engine 100.
  • the distance L between the cylinder centers of the first cylinder bore 3011 and the second cylinder bore 3012 is greater than or equal to 78 mm and Less than or equal to 80mm.
  • the engine 100 has a smaller external dimension, a lighter weight, and a more compact overall structure.
  • the present application aims at the twin-cylinder engine whose bore diameter of the cylinder hole 301 is 72mm, according to structural parameters such as the center distance between the first intake valve and the second intake valve, the center distance between the first exhaust valve and the second exhaust valve, through
  • the cylinder center distance L calculation method obtains the optimal cylinder center distance L of the first cylinder hole 3011 and the second cylinder hole 3012, that is, the cylinder center distance L of the first cylinder hole 3011 and the second cylinder hole 3012 is 79 mm.
  • the intake volume of the engine 100 is relatively reasonable, and the exhaust temperature field distribution is reasonable, so as to achieve a balance between the intake and exhaust of the engine 100 and improve the cooling effect of the engine 100 .
  • the intake and exhaust volumetric efficiency of the engine 100 is more reasonable, so that the assembly of various components of the engine 100 is more reasonable, and then the overall structure of the engine 100 is more compact, and the working efficiency and service life of the engine 100 are improved.
  • the cylinder center distance L of the first cylinder bore 3011 and the second cylinder bore 3012 can be greater than or equal to 78 mm and less than or equal to Equal to 80mm.
  • the distance L between the first cylinder bore 3011 and the second cylinder bore 3012 can be greater than or equal to 76mm and less than or equal to 82mm.
  • the movement speed of the piston 111 is very fast, and the speed is very uneven.
  • the speed of the piston 111 is zero; at the middle position of the top and bottom dead centers, the speed of the piston 111 reaches the highest.
  • the counterweight disposed on the connecting rod 132 can effectively balance these inertial forces. But only a part of the moving mass of the counterweight on the connecting rod 132 participates in linear motion, and another part of the counterweight on the connecting rod 132 participates in rotational motion.
  • the top dead center is the farthest position from the top of the piston 111 to the rotation center of the crankshaft 131
  • the bottom dead center is the closest position from the top of the piston 111 to the rotation center of the crankshaft 131.
  • the vibration frequency of the engine 100 is related to the speed of the engine 100 .
  • vibration theory multiple harmonic vibrations are often used to describe the vibration of the engine.
  • the vibration frequency is the same as the engine speed is called the first-order vibration
  • the frequency is twice the engine speed is called the second-order vibration, and so on, and there are third-order vibrations.
  • fourth-order vibration the higher the vibration frequency, the smaller the amplitude, and it can be ignored above the second order.
  • the first-order vibration accounts for more than 70% of the whole vibration and is the main source of vibration.
  • the commonly used method on the motorcycle engine is to add a balance mechanism to solve it.
  • the balance mechanism 14 includes an eccentric weight 141 and a shaft that rotates synchronously with the crankshaft 131. Using the reverse vibration force generated by the eccentric weight 141, the engine 100 can obtain a good balance effect, and the engine 100 can be lowered. vibration.
  • the balance mechanism 14 cooperates with the crankshaft 131 to realize the synchronous rotation of the balance mechanism 14 and the crankshaft 131 .
  • the balance mechanism 14 includes a first balance shaft 142 , a first shaft gear 143 , a second balance shaft 144 , a second shaft gear 145 and a drive shaft gear 146 .
  • the crankcase 4 is provided with several pairwise corresponding fixed shaft holes 401, the first balance shaft 142, the second balance shaft 14, the transmission main shaft 121, the transmission countershaft 122 and the crankshaft 131 are all arranged in the fixed shaft holes 401, and the second balance shaft 142 is arranged in the fixed shaft holes 401.
  • a balance shaft 142 , the second balance shaft 14 , the transmission main shaft 121 , the transmission counter shaft 122 and the crankshaft 131 are basically arranged in parallel.
  • the first shaft gear 143 is arranged on the first balance shaft 142
  • the second shaft gear 145 is arranged on the second balance shaft 144
  • the driving shaft gear 146 is arranged on the crankshaft 131
  • the driving shaft gear 146 is respectively connected with the first shaft gear 143
  • the second shaft gear 145 meshes.
  • the balance mechanism 14 adopts a double balance shaft mode, wherein the first balance shaft 142 and the second balance shaft 144 are arranged angularly symmetrically with respect to the center line of the crankshaft 131, and the first balance shaft 142 is relative to the direction of rotation of the crankshaft 131 and the second balance shaft 144 is relative to the crankshaft.
  • the rotation direction of 131 is opposite, the rotation speed of the first balance shaft 142 is the same as that of the crankshaft 131, and the rotation speed of the second balance shaft 144 is the same as that of the crankshaft 131, so as to balance the first-order reciprocating inertial force of the engine 100, thereby reducing the vibration of the engine 100 , reduce the noise of the engine 100, prolong the service life of the engine 100, and improve the comfort of the driver and passengers.
  • the first balance shaft 142, the second balance shaft 144 and the crankshaft 131 are parallel to each other, the first shaft gear 143 is arranged on one end of the first balance shaft 142, the second shaft gear 145 is arranged on one end of the second balance shaft 144, and the drive shaft gear 146 is provided at one end of the crankshaft 131 .
  • the first shaft gear 143, the second shaft gear 145 and the drive shaft gear 146 are at least partly distributed in the same plane, realizing the engagement between the first shaft gear 143 and the drive shaft gear 146, the second shaft gear 145 and the drive shaft gear 146 The engagement between them facilitates the crankshaft 131 to transmit the rotational motion to the first balance shaft 142 and the second balance shaft 144 .
  • first shaft gear 143 and the first balance shaft 142 are fixed through an existing fixed connection
  • first shaft gear 143 and the first balance shaft 142 are fixed through an existing fixed connection
  • the drive shaft gear 146 and the crankshaft 131 are fixed through an existing fixed connection.
  • the fixed connection is fixed.
  • the center distance between the first balance shaft 142 and the crankshaft 131 is greater than or equal to 72mm and less than or equal to 76mm
  • the center distance between the second balance shaft 144 and the crankshaft 131 is greater than or equal to 72mm and less than or equal to 76mm
  • the center distance between the first balance shaft 142 and the crankshaft 131 is The first center distance H
  • the center distance between the second balance shaft 144 and the crankshaft 131 is the second center distance G
  • the first center distance H and the second center distance G both pass through the envelope line 133 movement track of the connecting rod 132
  • the first The strength of the balance shaft 142 and the second balance shaft 144 is determined.
  • the first center distance H is set to 73 mm
  • the second center distance G is set to 73 mm, so as to achieve Weight reduction of the engine 100 .
  • the first center distance H and the second center distance G refer to the shortest distance between the centers of the two shafts
  • the first center distance H is the shortest distance between the center of the first balance shaft 142 and the center of the crankshaft 131
  • the second center distance G is the shortest distance between the center of the second balance shaft 144 and the center of the crankshaft 131 .
  • the crankcase 4 includes a first horizontal plane perpendicular to the through line 29 , the first horizontal plane is perpendicular to the projection plane 900 , and the axis of the crankshaft 131 is on the first horizontal plane.
  • the projection of the axis of the first balance shaft 142 on the projection plane 900 is the first projection point
  • the projection of the axis of the second balance axis 144 on the projection plane 900 is the second projection point.
  • the crankshaft 131 The projection of the axis on the projection plane 900 is the third projection point, the projection of the first horizontal plane on the projection plane 900 is the fourth projection line, the connecting line between the first projection point and the third projection point is the fifth projection line, and the second The line connecting the projection point and the third projection point is the sixth projection line.
  • the acute angle formed by the fifth projection line and the fourth projection line is the third included angle ⁇ , and the acute angle formed by the sixth projection line and the fourth projection line is the fourth included angle ⁇ .
  • the acute angle formed by the projection of the axis center of the first balance shaft 142 and the axis center of the crankshaft 131 on the projection plane 900 and the projection of the first horizontal plane on the projection plane 900 is the third included angle ⁇
  • the second balance The acute angle formed by the projection of the axis center of the shaft 144 and the axis center of the crankshaft 131 on the projection plane 900 and the projection of the first horizontal plane on the projection plane 900 is the fourth included angle ⁇ .
  • the third included angle ⁇ is greater than or equal to 0° and less than or equal to 20°
  • the fourth included angle ⁇ is greater than or equal to 0° and less than or equal to 20°.
  • the overall vibration frequency and amplitude of the engine 100 can be minimized.
  • the overall design of the engine 100 can be made smaller in appearance and lighter in weight, thereby making the structure of the engine 100 more compact, improving the space utilization rate of the engine 100, making the engine 100 run more smoothly, and further improving the service life of the engine 100 .
  • the first projection point, the second projection point and the third projection point are basically on the same straight line, that is, the axis of the first balance axis 142
  • the projection of the center on the projection plane 900 , the projection of the axis of the second balance shaft 144 on the projection plane 900 , and the projection of the axis of the crankshaft 131 on the projection plane 900 are basically on the same straight line.
  • the third included angle ⁇ is set to 20°
  • the fourth included angle ⁇ is set to 20°.
  • the included angle between the fifth projection line and the sixth projection line is 140°
  • the first center distance H is The shortest center distance is 73mm
  • the second center distance G is the shortest center distance 73mm.
  • the first balance shaft 142 and the second balance shaft 144 will be in contact with the internal structure (such as the connecting rod 132, etc.) collide, thereby affecting the overall operation of the engine 100.
  • the envelope 133 of the connecting rod 132 refers to the geometric shape formed by the movement track of the connecting rod 132 .
  • the third included angle ⁇ and the fourth included angle ⁇ may be arranged substantially symmetrically with respect to the through line 29 , that is, the angles of the two included angles are substantially the same.
  • the third included angle ⁇ is greater than or equal to 0° and less than or equal to 20°
  • the first The four included angles ⁇ are greater than or equal to 0° and less than or equal to 20°.
  • the fifth projection line and the fourth The angle formed by the projection lines is greater than or equal to 0° and less than or equal to 20°
  • the angle formed by the sixth projection line and the fourth projection line is greater than or equal to 0° and less than or equal to 20°.
  • the vibration frequency and amplitude of the whole machine of the engine 100 can be reduced to a smaller size, and the overall design of the engine 100 can be made smaller and lighter in weight, so that the structure of the engine 100 is more compact, and the light weight of the engine 100 can be realized.
  • improve the space utilization rate of the engine 100 make the engine 100 run more smoothly, and further increase the service life of the engine 100 .
  • the third included angle ⁇ is greater than or equal to 0° and less than or equal to 20°
  • the fourth included angle ⁇ is equal to or greater than 0° and equal to or less than 20°.
  • the fifth projection line The angle formed with the fourth projection line is greater than or equal to 0° and less than or equal to 20°, and the angle formed between the sixth projection line and the fourth projection line is greater than or equal to 0° and less than or equal to 20°.
  • the vibration frequency and amplitude of the whole machine of the engine 100 can be reduced to a smaller size, and the overall design of the engine 100 can be made smaller and lighter in weight, so that the structure of the engine 100 is more compact, and the light weight of the engine 100 can be realized.
  • improve the space utilization rate of the engine 100 make the engine 100 run more smoothly, and further increase the service life of the engine 100 .
  • the third included angle ⁇ is greater than or equal to 10° and less than or equal to 20°
  • the fourth included angle ⁇ is equal to or greater than 10° and equal to or less than 20°.
  • the fifth projection line The angle formed with the fourth projection line is greater than or equal to 10° and less than or equal to 20°, and the angle formed between the sixth projection line and the fourth projection line is greater than or equal to 10° and less than or equal to 20°.
  • the vibration frequency and amplitude of the whole machine of the engine 100 can be reduced to a smaller size, and the overall design of the engine 100 can be made smaller and lighter in weight, so that the structure of the engine 100 is more compact, and the light weight of the engine 100 can be realized.
  • improve the space utilization rate of the engine 100 make the engine 100 run more smoothly, and further increase the service life of the engine 100 .
  • the third included angle ⁇ is greater than or equal to 10° and less than or equal to 20°
  • the fourth included angle The angle ⁇ is equal to or greater than 10° and equal to or less than 20°.
  • the fifth projection line and the fourth The angle formed by the projection lines is greater than or equal to 10° and less than or equal to 20°
  • the angle formed by the sixth projection line and the fourth projection line is greater than or equal to 10° and less than or equal to 20°.
  • the third included angle ⁇ is greater than or equal to 0° and less than or equal to 20°
  • the fourth included angle ⁇ is greater than or equal to 0° and less than or equal to 20° .
  • the included angle formed by the fifth projection line and the fourth projection line is It is greater than or equal to 0° and less than or equal to 20°, and the included angle formed by the sixth projection line and the fourth projection line is greater than or equal to 0° and less than or equal to 20°.
  • the vibration frequency and amplitude of the whole machine of the engine 100 can be reduced to a smaller size, and the overall design of the engine 100 can be made smaller and lighter in weight, so that the structure of the engine 100 is more compact, and the light weight of the engine 100 can be realized.
  • improve the space utilization rate of the engine 100 make the engine 100 run more smoothly, and further increase the service life of the engine 100 .
  • the third included angle ⁇ is 20°
  • the fourth included angle ⁇ is 20°
  • the included angle formed by the fifth projection line and the fourth projection line is is 20°
  • the included angle formed by the sixth projection line and the fourth projection line is 20°.
  • the overall vibration frequency and amplitude of the engine 100 can be minimized, and the overall design of the engine 100 can be made smaller and lighter in weight, thereby making the structure of the engine 100 more compact and reducing the weight of the engine 100 , improve the space utilization rate of the engine 100 , make the engine 100 run more smoothly, and further increase the service life of the engine 100 .
  • the crankcase 4 is also provided with an oil pump assembly 17, the oil pump assembly 17 is connected to the balance mechanism 14, and the balance mechanism 14 includes a first balance shaft 142, a first shaft gear 143 , second balance shaft 144 , second shaft gear 145 and driving shaft gear 146 .
  • the first shaft gear 143 is arranged on the first balance shaft 142
  • the second shaft gear 145 is arranged on the second balance shaft 144
  • the driving shaft gear 146 is arranged on the crankshaft 131
  • the driving shaft gear 146 is respectively connected with the first shaft gear 143
  • the second shaft gear 145 meshes.
  • the first balance shaft 142, the second balance shaft 144 and the crankshaft 131 are parallel to each other, the first shaft gear 143 is arranged on the first end 1421 of the first balance shaft 142, and the second shaft gear 145 is arranged on one end of the second balance shaft 144,
  • the driving shaft gear 146 is arranged on one end of the crankshaft 131;
  • the oil pump assembly 17 is connected to the second end 1422 of the first balance shaft 142, and the crankcase 4 is provided with a balance bearing 147 near the second end 1422, and the balance bearing 147 is arranged on the fixed shaft In the hole 401 , the second end 1422 is disposed in the balance bearing bush 147 .
  • a flat square connection hole 1423 is provided on the end surface of the second end 1422, and a connecting piece 171 is provided on the end surface of the oil pump assembly 17 close to the second end 1422.
  • the oil pump assembly 17 is connected to the first balance shaft 142 so that the first balance shaft 142 drives the oil pump assembly 17 .
  • the oil pump assembly 17 is used to inject the lubricating oil splashed by the balance mechanism 14 back into the crankcase 4 .
  • the speed at which the lubricating oil is injected back into the crankcase 4 slows down.
  • the oil pump assembly 17 reaches a certain amount, it is easy to cause engine 100 Water seepage and oil seepage problem.
  • the oil pump assembly and the inside of the crankcase are connected through drilling.
  • the present application sets an oil drain groove 18 on the crankcase 4 .
  • the oil drain groove 18 can be integrally formed with the crankcase 4 by casting etc., so as to facilitate the processing of the oil drain groove 18 and improve production efficiency. Specifically, when the lubricating oil splashed by the balance mechanism 14 enters the oil pump assembly 17, the oil pump assembly 17 injects the lubricating oil into the oil drain groove 18.
  • the oil drain groove 18 is an oil drain channel.
  • the lubricating oil will be in a part of the space of the drain groove 18 .
  • the excessive oil pressure will enter the other part of the space of the oil drain groove 18, which will not affect the delivery of lubricating oil to the inside of the crankcase 4 through the oil drain groove 18, thereby realizing the oil in the crankcase 4.
  • Pressure balance effectively solving the problem of water seepage and oil seepage caused by excessive oil pressure in the crankcase 4.
  • the oil drain groove 18 includes a first channel 181 and a second channel 182 .
  • the first channel 181 and the second channel 182 may overlap and communicate with each other, the first channel 181 is part of the space where the oil pressure enters, and the second channel 182 is another part of the space where the lubricating oil enters.
  • the oil pump assembly 17 injects the lubricating oil into the oil drain groove 18.
  • the oil drain groove 18 is an oil drain channel, and the lubricating oil will In the second channel 182, at this time, when the oil pressure increases, the excessive oil pressure will enter the first channel 181, so that it will not affect the delivery of lubricating oil to the inside of the crankcase 4 through the oil drain groove 18, and then realize the crankshaft.
  • the oil pressure balance in the box 4 effectively solves the problem of water seepage and oil seepage caused by the excessive pressure of the crankcase 4.
  • the first channel 181 is used to balance the oil pressure in the crankcase 4 , effectively solving the problem of water seepage and oil leakage caused by the excessive pressure of the crankcase 4 .
  • the second channel 182 is used to form a channel for lubricating oil, so that the lubricating oil can be delivered from the oil pump assembly 17 to the crankcase 4 through the oil drain groove 18 .
  • the first channel 181 and the second channel 182 overlap and communicate with each other, which can facilitate the integral formation of the oil drain groove 18 and the crankcase 4 , facilitate the processing of the oil drain groove 18 and improve production efficiency.
  • the first channel 181 and the second channel 182 can be set independently and not communicated with each other.
  • the first channel 181 is part of the space where the oil pressure enters
  • the second channel 182 is another part of the space where the lubricating oil enters.
  • the oil drain groove 18 is an oil drain channel, and the lubricating oil will In the second channel 182, at this time, when the oil pressure increases, the excessive oil pressure will enter the first channel 181, so that it will not affect the delivery of lubricating oil to the inside of the crankcase 4 through the oil drain groove 18, and then realize the crankshaft.
  • the oil pressure balance in the box 4 effectively solves the problem of water seepage and oil seepage caused by the excessive pressure of the crankcase 4.
  • the first channel 181 is used to balance the oil pressure in the crankcase 4 , effectively solving the problem of water seepage and oil leakage caused by the excessive pressure of the crankcase 4 .
  • the second channel 182 is used to form a channel for lubricating oil, so that the lubricating oil can be delivered from the oil pump assembly 17 to the crankcase 4 through the oil drain groove 18 .
  • the first channel 181 and the second channel 182 can be set independently of each other and not communicated with each other, and can also facilitate the integral formation of the oil drain groove 18 and the crankcase 4, which facilitates the processing of the oil drain groove 18 and improves production efficiency.
  • the oil drain groove 18 is at least partially disposed in the third accommodation space 2013 , the oil drain groove 18 is disposed between the crankcase 4 and the oil pump assembly 17 , and the oil drain groove 18 communicates with the crankcase 4 and the oil pump assembly 17 .
  • the first passage 181 is at least partially disposed in the third accommodation space 2013 , the first passage 181 is disposed between the crankcase 4 and the oil pump assembly 17 , and the first passage 181 communicates with the crankcase 4 and the oil pump assembly 17 .
  • the second passage 182 is at least partially disposed in the third accommodation space 2013 , the second passage 182 is disposed between the crankcase 4 and the oil pump assembly 17 , and the second passage 182 communicates with the crankcase 4 and the oil pump assembly 17 .
  • the first channel 181 and the second channel 182 are arranged substantially in parallel.
  • the oil pump assembly 17 includes an oil pump shaft 172, an oil pump body 173, and an oil pump cover 174 in sequence, and the oil pump shaft 172, the oil pump body 173, and the oil pump cover 174 are fixedly connected in turn by bolts or other fixing methods.
  • the oil pump body 173 forms the accommodation space of the oil pump body 173
  • the oil pump shaft 172 is at least partially disposed in the accommodation space of the oil pump body 173
  • the oil pump cover 174 forms the accommodation space of the oil pump cover 174
  • the oil pump impeller 175 is at least partially disposed in the accommodation space of the oil pump cover 174.
  • One end of the oil pump shaft 172 is provided with a connecting piece 171 for connecting the oil pump shaft 172 with the first balance shaft 142 so that the first balance shaft 142 drives the oil pump assembly 17 .
  • the other end of the oil pump shaft 172 is provided with an oil pump impeller 175 , which is threadedly connected between the oil pump shaft 172 and the oil pump impeller 175 , and the oil pump shaft 172 is rotatably connected with the crankcase 4 through a bearing 176 .
  • the bearing 176 is disposed at one end close to the connecting member 171 , and an oil drain groove 18 is disposed between the bearing 176 and the end surface of the second end 1422 .
  • An oil seal 177 is arranged between the oil pump impeller 175 and the bearing 176, and the oil seal 177 is used to seal the lubricating oil to prevent the lubricating oil from leaking.
  • a water seal 178 is provided between the oil seal 177 and the oil pump impeller 175 , and the water seal 178 is used to prevent external water and other liquids from entering the engine 100 , so as to avoid malfunctions caused by water entering the engine 100 .
  • the oil pump shaft 172 realizes the connection between the oil pump assembly 17 and the first balance shaft 142
  • the oil pump body 173 realizes the connection between the oil pump assembly 17 and the crankcase 4 , thereby realizing the fixing and rotation of the oil pump assembly 17 .
  • the oil drain groove 18 communicates with the oil pump body 173 and the interior of the crankcase 4 , so that the oil pump assembly 17 can circulate lubricating oil in the oil pump body 173 and the interior of the crankcase 4 , so that the lubricating oil can circulate in the engine 100 .
  • the water seal 178 is arranged close to the oil pump impeller 175 so that the water seal 178 can better seal when the oil pump impeller 175 rotates.
  • the oil seal 177 is close to the bearing 176, which can ensure that the lubricating oil lubricates the bearing 176, thereby reducing the friction between the oil pump shaft 172 and the bearing 176, and can seal the lubricating oil inside the engine 100, thereby facilitating the lubricating oil in the engine 100 to loop.
  • the number of bearing 176 is at least one, so as to ensure the rotational connection between the oil pump shaft 172 and the crankcase 4 .

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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  • Combustion & Propulsion (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Abstract

一种发动机（100），包括：气缸盖（2），形成有第一容纳空间（2011）；进排气机构（8），包括进气机构（81）和排气机构（82）；凸轮机构（7），至少部分设置在第一容纳空间（2011）中；曲轴箱（4），形成有第二容纳空间（2012）；曲轴连杆机构（13），至少部分设置在第二容纳空间（2012）中；平衡机构（14），包括第一平衡轴（142）和第二平衡轴（144）；发动机（100）还包括：节气门机构（19），包括：主通道（191），主通道（191）连接进气机构（81）；节气通道（1922），与主通道（191）一体成型并至少部分连通主通道（191）；轴座（72）包括：通油孔（728），通油孔（728）贯穿轴座（72）并连通至凸轮轴（71）；集油结构（727），集油结构（727）包括集油槽（7271）和集油挡板（7272），集油挡板（7272）半包围集油槽（7271），通油孔（728）至少部分设置在集油槽（7271）中。该发动机能避免因为连接不良、老化等带来的渗漏风险，为凸轮轴提供良好的润滑效果。

Description

发动机 技术领域
本申请涉及动力***领域，尤其是指一种发动机。
背景技术
在现有技术中，节气门机构通过设置软管的方式，在发动机处于怠速状态时，控制发动机的进气。其中，怠速状态指发动机无负载运转状态，即离合器处于结合位置、变速器处于空挡位置、油门踏板处于完全松开位置的状态。但在实际过程中，由于软管的老化、密封性减弱等原因，会造成节气门机构的渗漏问题。
在现有技术中，发动机的进排气机构设置需要设置合理的角度，使发动机的进气容积较为合理，从而使发动机的运行更加稳定。此外，还需要使发动机的排气温度场分布合理，从而可以提高发动机在排气时的散热效果，便于发动机的冷却，进而实现发动机进气和排气之间的平衡，提高发动机的散热效果和使用寿命。同时，在满足上述要求的情况下，还需要使发动机的结构紧凑。
在现有技术中，油泵用于将平衡机构飞溅的润滑油注回曲轴箱内部。但在润滑油注回曲轴箱内部的过程中，由于油压增大，润滑油注回曲轴箱的速度变慢，当油泵中润滑油达到一定量时，容易造成发动机的渗水渗油问题。在现有的设计中，通过打孔的形式连通油泵与曲轴箱内部。但在实际过程中，由于曲轴箱内部油压过大的原因，通过打孔的形式无法实现曲轴箱中的油压平衡，因而仍旧会造成发动机的渗水渗油问题，不能保证发动机密封性。
发明内容
为了解决发动机内部的密封不良和进排气机构的结构不紧凑的问题，本申请提供了一种密封效果好且结构紧凑的发动机。
为了实现上述目的，本申请提供一种发动机，包括：气缸盖，气缸盖形成有第一容纳空间；进排气机构，进排气机构至少部分设置在第一容纳空间中，进排气机构包括进气机构和排气机构；凸轮机构，凸轮机构至少部分设置在第一容纳空间中，用于控制进排气机构；曲轴箱，曲轴箱形成有第二容纳空间；曲轴连杆机构，曲轴连杆机构至少部分设置在第二容纳空间中；平衡机构，平衡机构至少部分设置在第二容纳空间中并连接曲轴连杆机构，平衡机构包括第一平衡轴和第二平衡轴；发动机还包括：节气门机构，节气门 机构包括：主通道，主通道连接进气机构，用于控制空气输入至进气机构；节气通道，节气通道与主通道一体成型并至少部分连通主通道；气缸盖包括贯穿自身的贯穿线；发动机还包括气缸体，气缸体包括气缸孔，气缸体基本沿第一直线延伸且关于第一直线基本对称设置；进气机构基本沿第二直线方向延伸，第二直线与第一直线垂直；在一个垂直于第一直线的投影平面内，第二直线沿第一直线方向在投影平面上的投影为第一投影线；排气机构基本沿第三直线方向延伸，第三直线与第一直线垂直；第三直线沿第一直线方向在投影平面上的投影为第二投影线；贯穿线沿第一直线方向在投影平面上的投影为第三投影线；当气缸孔的直径大于等于70mm且小于等于74mm时，第一投影线与第三投影线的夹角大于等于11°且小于等于15°，第二投影线与第三投影线的夹角大于等于11°且小于等于15°。
为了实现上述目的，本申请提供了一种发动机，包括：气缸盖，气缸盖形成有第一容纳空间；进排气机构，进排气机构至少部分设置在第一容纳空间中，进排气机构包括进气机构和排气机构，进气机构用于发动机的进气，排气机构用于发动机的排气；凸轮机构，凸轮机构至少部分设置在第一容纳空间中，用于控制进排气机构；发动机还包括：节气门机构，节气门机构包括：主通道，主通道连接进气机构，用于控制空气输入至进气机构；节气通道，节气通道与主通道一体成型并至少部分连通主通道。
为了实现上述目的，本申请提供了一种发动机，包括：气缸盖，气缸盖形成有第一容纳空间；进排气机构，进排气机构至少部分设置在第一容纳空间中，进排气机构包括进气机构和排气机构，进气机构用于发动机的进气，排气机构用于发动机的排气；凸轮机构，凸轮机构至少部分设置在第一容纳空间中，用于控制进排气机构；曲轴箱，曲轴箱形成有第二容纳空间；曲轴连杆机构，曲轴连杆机构至少部分设置在第二容纳空间中；平衡机构，平衡机构至少部分设置在第二容纳空间中并连接曲轴连杆机构，平衡机构包括第一平衡轴和第二平衡轴；发动机还包括：节气门机构，节气门机构包括：主通道，主通道连接进气机构，用于控制空气输入至进气机构；节气通道，节气通道与主通道一体成型并至少部分连通主通道；油泵总成，油泵总成连接平衡机构和曲轴箱，油泵总成至少部分设置在第二容纳空间中；泄油槽，泄油槽至少部分设置在第二容纳空间中且包括第一通道和第二通道，泄油槽设置在曲轴箱和油泵总成之间并连通曲轴箱和油泵总成；第一通道设置在曲轴 箱和油泵总成之间并连通曲轴箱和油泵总成，用于平衡曲轴箱内部的油压；第二通道设置在曲轴箱和油泵总成之间并连通曲轴箱和油泵总成，用于形成润滑油的通道。
与现有技术相比，本申请至少具有以下有益效果：
可以通过将节气门机构设置为一体成型件，从而避免了因为连接不良、老化等问题带来的渗漏风险，提高节气门机构的密封性；可以通过设置合理的进排气机构的角度，从而使发动机的结构更加紧凑，并使发动机的进气容积和排气温度场分布较为合理；可以通过在曲轴箱和油泵总成之间设置泄油槽的形式，实现曲轴箱内部的油压平衡，从而避免发动机的渗水渗油，进而提高发动机的密封性。
附图说明
图1是本申请的发动机的立体结构示意图。
图2是本申请的发动机整体结构的***图。
图3是本申请的发动机的剖视结构示意图。
图4是本申请的发动机的部分结构示意图。
图5是本申请的发动机的半剖结构示意图。
图6是本申请的节气门机构第一角度的结构示意图。
图7是本申请的节气门机构第二角度的结构示意图。
图8是本申请的气缸盖的第一剖视结构示意图。
图9是本申请的图8中A处的局部放大图。
图10是本申请的轴座的结构示意图。
图11是本申请的轴座的部分结构示意图。
图12是本申请的图10中B处的局部放大图。
图13是本申请的气缸盖的第二剖视结构示意图。
图14是本申请的气缸盖的第三剖视结构示意图。
图15是本申请的气缸盖罩的结构示意图。
图16是本申请的气缸盖的第三剖视结构示意图。
图17是本申请的图16中C处的局部放大图。
图18是本申请的图16中D处的局部放大图。
图19是本申请的进排气机构的部分结构示意图。
图20是本申请的气缸盖的底面结构示意图。
图21是本申请的气缸体的结构示意图。
图22是本申请的曲轴箱的第一剖视结构示意图。
图23是本申请的图22中E-E处的剖视结构示意图。
图24是本申请的图23中F处的局部放大图。
具体实施方式
为了使本领域的人员更好地理解本申请方案，下面将结合本申请实施方式中的附图，对本申请具体实施方式中的技术方案进行清楚、完整地描述。
如图1至图3所示，一种发动机100，包括外壳体组件200，外壳体组件200包括气缸盖罩1、气缸盖2、气缸体3、曲轴箱4和油底壳5。其中，曲轴箱4两侧设有侧盖6。气缸盖罩1用于遮盖并密封气缸盖2,将润滑油保持在发动机100内部,同时将污垢和湿气等隔绝在发动机100外部。气缸盖2与气缸体3连接形成一个基本密封的密封空间，该密封空间用于密封气体并构成燃烧空间，以承受高温高压燃气。气缸体3和曲轴箱4是发动机100引擎的基本结构。油底壳5用于封闭曲轴箱4，并在与曲轴箱4连接后构成贮油槽，以防止杂质进入，并收集和储存游离在发动机100各摩擦表面的润滑油。
如图2至图5所示，发动机100还包括凸轮机构7、进排气机构8、点火机构9、活塞机构11、传动机构12、曲轴连杆机构13和平衡机构14。外壳体组件200形成容纳空间201，凸轮机构7、进排气机构8、点火机构9、活塞机构11、传动机构12、曲轴连杆机构13和平衡机构14至少部分设置在容纳空间201中。在本实施方式中，容纳空间201包括第一容纳空间2011、第二容纳空间2012和第三容纳空间2013。
其中，气缸盖2形成第一容纳空间2011，凸轮机构7、进排气机构8和点火机构9至少部分设置在第一容纳空间2011中。气缸体3形成第二容纳空间2012，活塞机构11至少部分设置在第二容纳空间2012中。曲轴箱4形成第三容纳空间2013，传动机构12、曲轴连杆机构13和平衡机构14至少部分设置在第三容纳空间2013中。曲轴连杆机构13连接凸轮机构7、活塞机构11和平衡机构14。凸轮机构7接触进排气机构8。
如图4和图5所示，进排气机构8包括进气机构81和排气机构82。点火机构9设在进气机构81和排气机构82之间。曲轴连杆机构13包括曲轴131和连杆132，连杆132的一端连接活塞机构11，连杆132的另一端连接曲轴131，曲轴131和平衡机构14通过齿轮啮合连接。活塞机构11包括活塞111 和活塞销112，活塞111和连杆132之间通过活塞销112连接。沿点火机构9的轴向方向，靠近点火机构9的一端设置有气缸体3，靠近点火机构9的另一端设置有凸轮机构7。凸轮机构7包括凸轮轴71和轴座72，凸轮轴71包括第一轮轴711和第二轮轴712。气缸盖罩1和气缸盖2通过轴座72连接。如图8所示，曲轴131与凸轮机构7通过气门传动组件15连接，气门传动组件15设置在气缸盖2、气缸体3和曲轴箱4围绕形成的容纳空间中，气门传动组件15包括正时链条151，曲轴131与凸轮机构7通过正时链条151连接。如图2至图4所示，传动机构12包括传动主轴121和传动副轴122，传动主轴121和传动副轴122之间通过齿轮啮合连接。曲轴131驱动传动机构12，将动力通过传动机构12传递给车辆前轮和/或后轮，从而驱动车辆行驶。
如图5所示，点火机构9与气缸体3之间的空间为燃烧室16。燃烧室16设置为活塞111到达上止点后，活塞111顶部与气缸盖2底面之间的空间。其中，上止点为活塞111顶部距离曲轴131旋转中心最远的位置。活塞111顶部指活塞111靠近气缸盖2的端面，气缸盖2底面指气缸盖2靠近活塞111顶部的表面。
活塞111通过曲轴连杆机构13驱动，从而使活塞111在气缸体3中做直线往复运动。
进气机构81用于将新鲜空气或可燃混合气送入燃烧室16，点火机构9将新鲜空气或可燃混合气点燃，使新鲜空气或可燃混合气在燃烧室16燃烧，活塞机构11将燃烧后的热能转换成机械能，通过连杆132驱动曲轴131运动。曲轴131通过气门传动组件15，驱动凸轮机构7运动，从而使凸轮机构7开闭进气机构81和排气机构82。同时，曲轴131驱动传动机构12，使传动机构12将动力传递给车辆。排气机构82又将燃烧后的废气进行过滤，使废气排到大气中。
节气门机构19是控制空气进入发动机100的一道可控阀门，气体进入进气机构81后会和汽油混合变成可燃混合气，从而燃烧形成做功。节气门机构19的一端连接空气滤清器，节气门机构19的另一端连接气缸盖2。
如图3所示，作为一种实现方式，节气门机构19与外壳体组件200连接。具体的，节气门机构19与气缸盖2连接。如图3和图5所示，进气机构81包括进气道812和第一气门机构811，节气门机构19与进气机构81连接，当发动机100为单缸发动机时，进排气机构8的数量为一个，进气机构81和 排气机构82的数量均为两个；当发动机100为双缸发动机时，进排气机构8的数量为两个，进气机构81和排气机构82的数量均为四个；即一个进排气机构8包括两个进气机构81和两个排气机构82。
具体的，节气门机构19至少部分设在进气道812上，节气门机构19与进气道812通过螺纹等方式固定连接。如图6和图7所示，节气门机构19包括主通道191、节气门阀体192和阀体电机193。主通道191的一端连通外界，主通道191的另一端连通进气道812，主通道191连通进气道812的一端设有螺纹。进气道812与主通道191通过螺纹等方式固定连接。节气门阀体192设在主通道191一侧。节气门阀体192至少部分与主通道191一体成型，从而避免了由于连接不良、老化等问题带来的渗漏风险。阀体电机193用于控制节气门阀体192的开闭，在主通道191关闭时，阀体电机193控制节气门阀体192打开，进而通过节气门阀体192控制空气输入至进气道812。节气门阀体192包括气阀1921和节气通道1922。节气通道1922与主通道191一体成型，可以避免了由于连接不良、老化等问题带来的渗漏风险，从而使节气门机构19的连接更加稳固，提高了节气门机构19的密封性。节气通道1922至少部分连通主通道191，节气通道1922通过主通道191将空气输入至进气道812。节气通道1922包括进气孔1922a、出气孔1922b、节气气道1922c和出气口1922d。进气孔1922a与主通道191一体成型，可以提高节气通道1922的密封性，从而通过主通道191将空气基本输入至节气门机构19，有效避免了由于连接不良、老化等问题带来的渗漏风险。出气孔1922b与主通道191一体成型，可以提高节气通道1922的密封性，从而通过主通道191将空气基本输入至进气道812，有效避免了由于连接不良、老化等问题带来的渗漏风险。节气气道1922c与主通道191一体成型，节气气道1922c连通出气口1922d和进气孔1922a。具体的，节气气道1922c的第一段连通出气口1922d，节气气道1922c的第二段连通进气孔1922a。出气口1922d设在节气气道1922c的第一段上，出气口1922d设置在节气气道1922c和出气孔1922b之间，出气口1922d连通节气气道1922c和出气孔1922b，出气口1922d用于将进气孔1922a输入的空气通过节气气道1922c输入至出气孔1922b，从而将空气通过出气孔1922b输入至进气道812。其中，出气口1922d与主通道191一体成型，可以提高节气通道1922的密封性，从而通过出气孔1922b将空气基本输入至进气道812，有效避免了由于连接不良、老化等问题带来的 渗漏风险。在本实施方式中，节气通道1922与主通道191一体成型。具体的，进气孔1922a、出气孔1922b、节气气道1922c和出气口1922d均与主通道191一体成型，可以使空气依次通过进气孔1922a、节气气道1922c、出气口1922d和出气孔1922b后输入至主通道191，从而使空气通过主通道191输入至进气道812，可以提高节气通道1922的密封性，从而将空气基本输入至进气道812，有效避免了由于连接不良、老化等问题带来的渗漏风险。气阀1921通过阀体电机193控制出气口1922d的开闭程度，从而控制进入出气口1922d中的空气量。其中，阀体电机193可以是步进电机。
发动机100至少包括第一状态和第二状态。当发动机100处于第一状态时，即当发动机100处于怠速状态时，主通道191关闭，发动机100的进气由节气门阀体192控制。其中，怠速状态指发动机100无负载运转状态，即离合器处于结合位置、变速器处于空挡位置、油门踏板处于完全松开位置的状态。具体的，当发动机100处于第一状态时，主通道191关闭，阀体电机193控制出气口1922d打开，空气从进气孔1922a输入，从而使空气依次穿过节气气道1922c、出气口1922d、出气孔1922b，进而使空气输入至进气道812。当发动机100处于第二状态时，即当发动机100处于非怠速状态时，主通道191打开，发动机100的进气由主通道191控制，气阀1921控制出气口1922d关闭。此时，阀体电机193控制气阀1921，使出气口1922d关闭，空气无法通过出气口1922d输入至出气孔1922b，从而使空气无法通过节气通道1922进入进气道812中。其中，主通道191通过通道阀194控制开闭，通道阀194包括油门拉线1941、阀轴1942和阻气片1943，油门拉线1941、阀轴1942和阻气片1943依次连接。阀轴1942贯穿主通道191，阀轴1942两端设在主通道191两侧，阀轴1942的一端设有油门拉线1941，阀轴1942两端均为密封固定，从而防止空气从阀轴1942处进入主通道191。阻气片1943转动连接在阀轴1942上。其中，阀轴1942两端的密封固定可以为O型圈密封固定，阻气片1943可以为圆形钢片。
当阀轴1942通过油门拉线1941控制阻气片1943，使阻气片1943轴线与主通道191轴线基本平行时，阻气片1943将主通道191堵塞，从而使主通道191关闭；当阀轴1942通过油门拉线1941控制阻气片1943，使阻气片1943轴线与主通道191轴线基本垂直时，即阻气片1943旋转90°左右，阻气片1943与主通道191之间形成空隙，从而使主通道191打开。
在本实施方式中，主通道191两端分别为通道一端1911和通道二端1912，通道一端1911的一端连通进气道812，通道二端1912的一端连通外界，便于空气通过通道一端1911从通道二端1912输入至进气道812。进气孔1922a的一端连通节气气道1922c，进气孔1922a的另一端连通通道二端1912的另一端，便于空气通过进气孔1922a从通道二端1912输入至节气气道1922c。出气孔1922b的一端连通出气口1922d，出气孔1922b的另一端连通通道一端1911的另一端，便于空气通过出气孔1922b从出气口1922d输入至通道一端1911，从而使空气输入至进气道812。通过上述设置方式，可以将节气门阀体192与主通道191贯通，便于节气门阀体192与节气门机构19一体成型，从而避免了由于连接不良、老化等问题带来的渗漏风险。
当发动机100为双缸发动机时，节气门机构19包括第一主通道1911、第二主通道1912、节气门阀体192和阀体电机193。第一主通道1911和第二主通道1912基本平行设置。节气门阀体192至少部分设置在第一主通道1911和第二主通道1912之间，节气门阀体192至少部分与第一主通道1911一体成型，节气门阀体192至少部分与第二主通道1912一体成型，从而避免了由于连接不良、老化等问题带来的渗漏风险，提高了节气门机构19的密封性。节气门阀体192包括节气通道1922和气阀1921。节气通道1922至少部分设置在第一主通道1911和第二主通道1912之间，节气通道1922与第一主通道1911一体成型，节气通道1922与第二主通道1912一体成型，从而避免了由于连接不良、老化等问题带来的渗漏风险，提高了节气门机构19的密封性。节气通道1922包括出气口1922d、两个进气孔1922a、两个出气孔1922b、节气气道1922c。出气口1922d设置在第一主通道1911和第二主通道1912之间，出气口1922d与第一主通道1911一体成型，出气口1922d与第二主通道1912一体成型。两个进气孔1922a设置在第一主通道1911和第二主通道1912之间，两个进气孔1922a与第一主通道1911一体成型，两个进气孔1922a与第二主通道1912一体成型。两个出气孔1922b设置在第一主通道1911和第二主通道1912之间，两个出气孔1922b与第一主通道1911一体成型，两个出气孔1922b与第二主通道1912一体成型。节气气道1922c设置在第一主通道1911和第二主通道1912之间，节气气道1922c与第一主通道1911一体成型，节气气道1922c与第二主通道1912一体成型。通过上述设置方式，使出气口1922d、两个进气孔1922a、两个出气孔1922b、节气气 道1922c均与第一主通道1911一体成型，出气口1922d、两个进气孔1922a、两个出气孔1922b、节气气道1922c均与第二主通道1912一体成型，从而避免了由于连接不良、老化等问题带来的渗漏风险，提高了节气门机构19的密封性。节气气道1922c基本与第一主通道1911平行设置，节气气道1922c基本与第二主通道1912平行设置。第一主通道1911和第二主通道1912之间设有连接部196，连接部196与第一主通道1911一体成型，连接部196与第二主通道1912一体成型，从而避免了由于连接不良、老化等问题带来的渗漏风险，提高了节气门机构19的密封性。节气门阀体192至少部分设在连接部196上，阀体电机193至少部分设在连接部196上。节气门阀体192可以沿连接部196延伸方向设置。其中，连接部196延伸方向指与主通道191轴线平行方向。通道阀194包括油门拉线1941、阀轴1942、第一阻气片1943a和第二阻气片1943b。阀轴1942贯穿第一主通道1911和第二主通道1912，阀轴1942轴线基本与第一主通道1911轴线垂直，阀轴1942轴线基本与第二主通道1912轴线垂直，阀轴1942两端设在第一主通道1911和第二主通道1912相对的两侧，即阀轴1942两端依次穿过第一主通道1911、连接部196和第二主通道1912。阀轴1942的一端设有油门拉线1941，阀轴1942两端均为密封固定。第一阻气片1943a转动连接在阀轴1942上且位于第一主通道1911中，第二阻气片1943b转动连接在阀轴1942上且位于第二主通道1912中，便于第一阻气片1943a控制第一主通道1911的开闭，第二阻气片1943b控制第二主通道1912的开闭。具体的，第一阻气片1943a随着阀轴1942的转动而转动，从而通过第一阻气片1943a的旋转，控制第一主通道1911的开闭；第二阻气片1943b随着阀轴1942的转动而转动，从而通过第二阻气片1943b的旋转，控制第二主通道1912的开闭。
阀体电机193设置在靠近通道一端1911处，便于阀体电机193控制气阀1921开闭出气口1922d。连接部196设有阀槽1961，阀槽1961中设有气阀1921，气阀1921与阀体电机193连接。具体的，节气气道1922c可以沿连接部196延伸方向设置，这种设置方式可以使节气气道1922c与主通道191基本平行，从而便于进气孔1922a连通节气气道1922c和主通道191，便于出气孔1922b连通出气口1922d和主通道191，使空气可以更加顺利地输入至进气道812。两个进气孔1922a关于节气气道1922c轴线对称设置，第一主通道1911连通一个进气孔1922a的一端，第二主通道1912连通另一个进气孔 1922a的一端，节气气道1922c分别连通两个进气孔1922a的另一端。两个出气孔1922b关于节气气道1922c轴线对称设置，第一主通道1911连通一个出气孔1922b的一端，第二主通道1912连通另一个出气孔1922b的一端，出气口1922d分别连通两个出气孔1922b的另一端。出气口1922d的中心基本处于节气气道1922c的轴线上，且出气口1922d设在节气气道1922c的侧壁上，便于空气通过出气口1922d均匀地输入至两个出气孔1922b。通过出气口1922d、两个进气孔1922a、两个出气孔1922b的设置方式，将出气口1922d、进气孔1922a和出气孔1922b合理布置在节气门机构19中，便于提高进气孔1922a的进气效率和出气孔1922b的出气效率。
具体的，阀轴1942轴线基本与第一主通道1911的轴线垂直，阀轴1942轴线基本与第二主通道1912的轴线垂直。阀轴1942轴线的一侧设有节气气道1922c，阀轴1942轴线的另一侧设有阀体电机193。阀轴1942和节气气道1922c之间存在间隔，即阀轴1942和节气气道1922c之间不存在连通处，从而防止空气通过阀轴1942进入节气气道1922c中，便于节气门机构19的密封。
此外，气阀1921包括阀头1921a和阀身1921b，阀头1921a和阀身1921b为一体成型件。阀身1921b与阀体电机193连接，阀头1921a用于打开和关闭出气口1922d。具体的，阀体电机193控制阀身1921b推动和/或拉动阀头1921a，从而使阀头1921a关闭和/或打开出气口1922d。
在本实施方式中，阀头1921a上设有第一塞195，第一塞195用于填补气阀1921与其他零部件之间的空隙，便于在节气门机构19使用过程中，提高节气门机构19的密封性。具体的，第一塞195的形状为碗型，可以便于第一塞195更好地填补气阀1921与其他零部件之间的空隙，从而使节气门机构19的密封性能更优。
如图8和图9所示，凸轮机构7包括凸轮轴71和轴座72，轴座72至少部分连接在气缸盖2上，轴座72用于支撑并润滑凸轮轴71。沿凸轮轴71的径向方向，靠近凸轮轴71的一端设置有点火机构9，靠近凸轮轴71的另一端设置有轴座72，点火机构9和轴座72关于凸轮轴71轴线基本呈对称分布。如图8和图10所示，轴座72远离凸轮轴71的表面为上表面，轴座72上表面基本沿第二直线300延伸，轴座72上表面设有第一对称面600，第一对称面600为与第二直线300垂直的对称面，轴座72沿第二直线300方向的两端 为轴座72的两端，轴座72垂直第二直线300方向的两侧为轴座72的两侧。如图10所示，轴座72上设有若干个轴座安装孔722和若干个盖罩安装孔724，若干个轴座安装孔722均匀分布在轴座72边缘处，若干个盖罩安装孔724均匀设在轴座72的两端。轴座安装孔722用于将轴座72固定在气缸盖2上，盖罩安装孔724用于将气缸盖罩1安装在轴座72上。其中一个轴座安装孔722还可以作为气门传动组件15的安装孔，该轴座安装孔722具体为螺栓螺柱孔，螺栓螺柱孔设在轴座72上表面相邻两条边的交接处。其中，轴座72上表面相邻两条边的交接处指轴座72的一端和轴座72的一侧的交接处。具体的，轴座安装孔722的数量为六个，其中四个轴座安装孔722分别设在轴座72上表面相邻两条边的交接处，另外两个轴座安装孔722设在轴座72边缘处且位于第一对称面600上；盖罩安装孔724的数量为两个，盖罩安装孔724设在轴座72边缘处且位于轴座72中心线上。盖罩安装孔724包括第一安装孔7241和第二安装孔7242，第一安装孔7241设在螺栓螺柱孔的一端，第二安装孔7242设在轴座72的另一端，第一安装孔7241与轴座72边缘处具有一定距离。此外，轴座72上表面边缘处设有若干个凸沿725，若干个凸沿725向背对轴座72上表面方向延伸，若干个轴座安装孔722设在若干个凸沿725上，若干个盖罩安装孔724设在若干个凸沿725上，若干个轴座安装孔722和若干个盖罩安装孔724均贯穿若干个凸沿725。其中，气缸盖2设置有贯穿自身的贯穿线29，第二直线300是与贯穿线29垂直的直线，轴座72中心线指与第二直线300平行的轴座72中心线。
作为一种实现方式，轴座72包括轴限位机构726(如图8和图9所示)、集油结构727和通油孔728，轴限位机构726设在靠近第一安装孔7241的一端，轴限位机构726与凸轮轴71配合，实现对凸轮轴71的限位，集油结构727和通油孔728与凸轮轴71配合，实现对凸轮轴71的润滑作用。在现有技术中，轴座72对凸轮轴71的润滑采用飞溅润滑，由于轴座72缺乏集油能力，部分时候会造成润滑油量不足，从而会产生润滑不良的情况。为避免润滑不良的情况发生，集油结构727用于将飞溅的润滑油收集并存储，增加润滑油量，为凸轮轴71提供良好的润滑效果。通油孔728贯穿轴座72，通油孔728连通凸轮轴71，用于将集油结构727收集的润滑油注入至凸轮轴71上，从而避免由于凸轮轴71和轴限位机构726之间的磨损导致轴向窜动量增加过快的现象发生。其中，飞溅的润滑油是指平衡机构14飞溅而出的润滑油。集油 结构727设置在轴座72靠近第一安装孔7241的一端，便于与凸轮轴71配合，更好地提高了凸轮轴71的润滑效果。集油结构727围绕通油孔728设置，从而有效地使飞溅的润滑油可以收集在集油结构727中，并通过通油孔728注入至凸轮轴71上，提高凸轮轴71和轴限位机构726之间的润滑效果。
如图10至图12所示，具体的，集油结构727包括集油槽7271和集油挡板7272，集油槽7271与第一安装孔7241设在轴座72的同一端，集油槽7271与第一安装孔7241关于轴座72中心线基本对称设置。集油槽7271与凸轮轴71基本平行设置，集油挡板7272包括相互连接的第一挡板7272a和第二挡板7272b，第一挡板7272a的一端连接螺栓螺柱孔，第一挡板7272a的另一端连接第二挡板7272b的一端，第二挡板7272b的另一端连接第一安装孔7241，第二挡板7272b的内侧表面为第一表面7272d，集油槽7271靠近第二挡板7272b的内侧表面为第二表面7271a，第一表面7272d和第二表面7271a基本处于同一平面。这种设置方式可以更好的收集并存储飞溅的润滑油，从而增加润滑油量，进而有效地提高润滑效果。第一表面7272d比第二表面7271a更靠近第一安装孔7241。第二挡板7272b和第一挡板7272a的连接方式可以是圆弧连接，便于润滑油在飞溅的过程中可以更顺利地存储在集油挡板7272中。其中，第一安装孔7241靠近轴座72中心处设有弯折部721，弯折部721呈一高一低设置，弯折部721较高的一侧为第一平面7211，弯折部721较低的一侧为第二平面7212，第一平面7211和第二平面7212连接处为第一竖面7213，第一挡板7272a连接螺栓螺柱孔靠近轴座72边缘的一侧，第二挡板7272b外侧表面连接第一安装孔7241，第二挡板7272b的另一端延伸至第一竖面7213。集油槽7271和集油挡板7272均设置在第二平面7212上。其中，第二挡板7272b的内侧表面为远离第一安装孔7241的表面。
集油槽7271的四周内陷于轴座72的表面，形成凹槽。由于在发动机100安装后，轴限位机构726处于倾斜状态，即集油槽7271底面为斜面，因此，集油槽7271包括第一槽沿7271c和第二槽沿7271d。沿贯穿线29的延伸方向，第一槽沿7271c和第二槽沿7271d可以呈相同高度布置。此外，沿贯穿线29的延伸方向，第一槽沿7271c和第二槽沿7271d还可以呈一高一低布置，较高的一侧槽沿为第一槽沿7271c，第一槽沿7271c设在集油槽7271底面较低的一侧，较低的一侧槽沿为第二槽沿7271d，第二槽沿7271d设在集油槽7271底面较高的一侧，从而在发动机100安装后，使尽可能多的润滑 油保存在集油槽7271中，增加润滑油量。其中，第一槽沿7271c指集油槽7271靠近第一安装孔7241一侧槽沿，第二槽沿7271d是指与第一槽沿7271c相对的一侧槽沿。
又由于轴限位机构726处于倾斜状态，因此集油挡板7272为半包围形状，既可以避免润滑油被集油挡板7272挡住而造成集油较少的问题；又可以减少材料浪费以及降低加工难度；还可以收集集油槽7271中溢出的润滑油，从而增加润滑油存储量，为凸轮轴71提供良好的润滑效果。
具体的，第一挡板7272a和第二挡板7272b的高度可以一致，也可以不一致，集油挡板7272设置于轴座72上表面，第一挡板7272a和第二挡板7272b连接并包围至少部分集油槽7271，第一挡板7272a的内侧表面为第三表面7272c，集油槽7271靠近第一挡板7272a的内侧表面为第四表面7271b，第三表面7272c和第四表面7271b既可以基本呈同一平面设置；第三表面7272c也可以比第四表面7271b更靠近螺栓螺柱孔，即第三表面7272c也可以比第四表面7271b更远离通油孔728，从而可以收集并存储更多的润滑油，为凸轮轴71提供良好的润滑效果，便于减少凸轮轴71的磨损，提高凸轮轴71的使用寿命。
轴限位机构726还包括轴槽7261；凸轮轴71上设置有环形凸起713。轴槽7261设在轴座72的下表面上，用于和凸轮轴71上设置的环形凸起713配合，实现轴槽7261对凸轮轴71的限位作用。通油孔728的中心与轴槽7261的轴线基本处于同一平面，通油孔728与轴槽7261连通，便于使收集的润滑油通过通油孔728流入轴槽7261中，从而使凸轮轴71和轴槽7261之间的润滑效果更好，减少凸轮轴71和轴槽7261之间的磨损，防止轴向窜动量增加过快。集油槽7271设置在通油孔728的周围，使集油槽7271环绕通油孔728，从而使润滑油顺利地流入通油孔728，为凸轮轴71提供良好的润滑效果。其中，轴座72的下表面为与轴座72上表面相反的表面。
在本实施方式中，通油孔728的位置可以位于集油槽7271底面的任意位置，从而使存储在集油槽7271和集油挡板7272中的润滑油通过通油孔728流入轴槽7261中，便于提高凸轮轴71和轴槽7261之间的润滑效果，减少凸轮轴71和轴槽7261之间的磨损，提高凸轮轴71和轴槽7261的使用寿命。通油孔728的位置设置在偏向于集油槽7271底面较低的一侧，便于润滑油流入通油孔728中。
此外，通油孔728、集油槽7271和集油挡板7272可以设置在凸轮轴71轴线两侧的任意侧，便于润滑油进入轴槽7261。凸轮轴71的转动方向至少包括第一方向和第二方向，第一方向指凸轮轴71顺时针转动，第二方向指凸轮轴71逆时针转动。通油孔728、集油槽7271和集油挡板7272根据凸轮轴71转动的方向进行位置设置，具体设置方式为：当凸轮轴71转动方向为第一方向时，通油孔728、集油槽7271和集油挡板7272设置在偏向于凸轮轴71转动方向相反的一侧，即通油孔728、集油槽7271和集油挡板7272的位置可以随着凸轮轴71的转动方向而发生改变，从而适应凸轮轴71转动过程中对润滑油的需求。通过上述设置方式设置通油孔728、集油槽7271和集油挡板7272的位置，可以在凸轮轴71转动的过程中，带动流入通油孔728的润滑油，使润滑油沿着凸轮轴71转动方向进行移动，从而使凸轮轴71和轴槽7261之间的润滑效果更好。
可以理解的，当凸轮轴71转动方向为第二方向时，通油孔728、集油槽7271和集油挡板7272设置在偏向于凸轮轴71转动方向相反的一侧，即通油孔728、集油槽7271和集油挡板7272的位置可以随着凸轮轴71的转动方向而发生改变，从而适应凸轮轴71转动过程中对润滑油的需求。通过上述设置方式设置通油孔728、集油槽7271和集油挡板7272的位置，可以在凸轮轴71转动的过程中，带动流入通油孔728的润滑油，使润滑油沿着凸轮轴71转动方向进行移动，从而使凸轮轴71和轴槽7261之间的润滑效果更好。
如图13至图14所示，气缸盖2中还设有冷却机构21，冷却机构21包括用于冷却点火机构9的冷却水道211，冷却水道211分布在点火机构9的周围，便于对点火机构9进行冷却，提高点火机构9的散热效果。
贯穿线29处设有点火孔22，点火孔22贯穿气缸盖2，点火孔22的一端连通气缸盖罩1，点火孔22的另一端连通燃烧室16，点火孔22连通气缸盖罩1的一端为第一连通孔221，点火孔22连通燃烧室16的一端为第二连通孔222。第一连通孔221和第二连通孔222互相连通。点火孔22中设有点火机构9，点火孔22的中心线与贯穿线29基本重合，从而使点火机构9位于气缸盖2的中心处，便于在气缸盖2中安装点火机构9。点火机构9包括火花塞901和点火线圈902，火花塞901的一端至少部分设在点火线圈902中，火花塞901的另一端至少部分设在第二连通孔222处。在点火机构9运行过程中， 由于点火孔22中的温度上升，会导致点火孔22中的空气膨胀，从而使点火线圈902被顶出，导致点火中断。
如图13至图15所示，作为一种实现方式，气缸盖罩1上设置有通气孔23，通气孔23连通点火孔22并贯穿气缸盖罩1，通气孔23通过气缸盖罩1连通至气缸盖罩1的外表面，即通气孔23通过气缸盖罩1连通至气缸盖罩1的外部。通气孔23的一端连通点火孔22，通气孔23的另一端贯穿气缸盖罩1连通外界，用于将点火孔22中的空气和水排出至点火孔22外，从而平衡点火孔22中的气压和外界气压，使点火机构9稳定工作，避免点火中断。此外，点火孔22和点火机构9的结构也进行调整，使点火孔22和点火机构9周围可以设置横截面面积更大的冷却机构21，从而便于点火孔22和点火机构9进行冷却，可以防止点火线圈902被顶出，避免点火中断。具体的，冷却水道211可以延伸至第二连通孔222处，从而增加火花塞901处的冷却水道211的体积，实现对火花塞901的有效冷却。
在本实施方式中，通气孔23的一端连通点火孔22，通气孔23的另一端连通外界，通气孔23连通点火孔22的一端为第三连通孔231，通气孔23连通外界的一端为第四连通孔232，第四连通孔232至少部分设置在气缸盖罩1上并连通气缸盖罩1的外表面，便于第四连通孔232连通外界，从而平衡点火孔22与外界的气压。第三连通孔231和第四连通孔232互相连通。通过这种设置方式，既可以平衡点火孔22中的气压，又可以将点火孔22中的水通过水蒸气的方式排出，从而有利于点火机构9的稳定运行。其中气缸盖罩1外表面为气缸盖罩1与外界接触的表面。气缸盖罩1外表面上设有若干个安装螺栓过孔101、油气分离区102、二次补气区103和第一传动腔区104，若干个安装螺栓过孔101用于连接气缸盖2和气缸盖罩1，二次补气区103对应二次补气阀安装区，第一传动腔区104对应气门传动组件15的安装区。点火孔22贯穿气缸盖罩1连通外界，第一连通孔221设在气缸盖罩1上，油气分离区102、二次补气区103和第一传动腔区104分布在第一连通孔221周围，第一连通孔221设在油气分离区102和二次补气区103之间，第一连通孔221中心点与第一传动腔区104中心点基本呈同一直线，第一连通孔221中心点基本处于气缸盖罩1径向中心线上。其中，气缸盖罩1外表面基本沿第三直线400延伸，气缸盖罩1径向中心线指平行于第三直线400的径向中心线。
在本实施方式中，当发动机100为双缸发动机时，即点火机构9数量为两个时，点火孔22的数量为两个，点火孔22包括第一点火孔223和第二点火孔224，第一点火孔223的中心和第二点火孔224的中心均基本处于气缸盖罩1径向中心线上。此时，通气孔23至少有两个，通气孔23包括第一通气孔233和第二通气孔234。第一通气孔233连通第一点火孔223并贯穿气缸盖罩1，第一通气孔233通过气缸盖罩1连通至气缸盖罩1的外表面，即第一通气孔233通过气缸盖罩1连通至气缸盖罩1的外部，从而将第一点火孔223中的空气和水排出至第一点火孔223外，进而平衡第一点火孔223中的气压和外界气压，使点火机构9稳定工作，避免点火中断。第二通气孔234连通第二点火孔224并贯穿气缸盖罩1，第二通气孔234通过气缸盖罩1连通至气缸盖罩1的外表面，即第二通气孔234通过气缸盖罩1连通至气缸盖罩1的外部，从而将第二点火孔224中的空气和水排出至第二点火孔224外，进而平衡第二点火孔224中的气压和外界气压，使点火机构9稳定工作，避免点火中断。
当发动机100为单缸发动机时，即点火机构9数量为一个时，点火孔22的数量为一个，此时，点火孔22的中心基本与气缸盖罩1的中心重合。其中，第三直线400与第二直线300平行。
作为一种实现方式，连通点火孔22的通气孔23至少有一个，通气孔23的朝向满足排气需求即可，无需特定通气孔23的朝向；通气孔23的位置满足连通外界和点火孔22即可，无需特定通气孔23的位置。一般情况下，通气孔23的设置方向为：在发动机100安装完成后，连通点火孔22的一端比连通外界的一端低，即第三连通孔231与第二连通孔222的距离比第四连通孔232与第二连通孔222的距离短。这种设置方式可以提高通气孔23排气的效果，有利于平衡点火孔22与外界的气压。
如图13和图14所示，火花塞901包括安装螺栓9011、拧紧六角9012和电极9013。火花塞901用于将高压导线送来的脉冲高压电放出，脉冲高压电击穿火花塞901两电极9013间空气，从而产生电火花，引燃燃烧室16中的混合气体。安装螺栓9011用于与气缸体3装配，拧紧六角9012用于拧紧或拧出火花塞901，电极9013用于释放脉冲高压电。若安装螺栓9011的长度较短，拧紧六角9012和电极9013等结构离燃烧室16更近，因此会产生更多的热量，影响点火机构9的散热效果。此时，火花塞901只有较少部分的 结构处于冷却水道211的冷却范围中。因此若安装螺栓9011的长度较短，会导致火花塞901的冷却效果较差，会导致点火机构9的温度较高，从而影响点火机构9的使用寿命。
如图13和图14所示，作为一种实现方式，为了提高点火机构9在实际运行过程中的冷却效果，通过在气缸盖罩1上设置通气孔23的方式，并对点火孔22和点火机构9的结构进行调整，使点火孔22和点火机构9周围可以设置横截面面积更大的冷却机构21，从而便于点火孔22和点火机构9进行冷却，可以防止点火线圈902被顶出，避免点火中断。冷却水道211可以延伸至第二连通孔222处，从而增加火花塞901处的冷却水道211的体积，使火花塞901整体结构基本处于冷却水道211的冷却范围内。具体的，安装螺栓9011设在第二连通孔222中，第二连通孔222的长度和安装螺栓9011的长度增加，第二连通孔222的长度和安装螺栓9011的直径减小，从而使冷却水道211可以延伸至第二连通孔222处，提高了冷却水道211对火花塞901的冷却效果。在本实施方式中，火花塞901的拧紧六角9012和电极9013等结构整体离第二连通孔222较远，即火花塞901的拧紧六角9012和电极9013等结构整体离燃烧室16较远，又由于冷却水道211延伸至第二连通孔222处，因此，冷却水道211对点火机构9的冷却效果更好，便于点火机构9的散热。一般情况下，冷却水道211包括：燃烧室16壁顶部、进排气机构8壁与点火孔22壁之间形成的空间，冷却水道211的体积、形状均取决于进排气机构8、燃烧室16、点火机构9的安装情况。
在本实施方式中，通过在气缸盖罩1中设置连通点火孔22和外界的通气孔23、增加安装螺栓9011长度等均可以使冷却水道211的体积增加，从而使冷却水道211在最大范围内包围点火机构9，提高点火机构9的冷却效果，进而提高点火机构9的使用寿命。此外，通气孔23将点火孔22中的空气和水排出至点火孔22外，既可以平衡点火孔22中的气压和外界气压，使点火机构9稳定工作，避免点火中断，又可以通过空气和水的排出带走点火孔22中的部分热量，有效防止由于点火孔22中的空气快速膨胀导致点火线圈902被顶出。
如图16所示，作为一种实现方式，进排气机构8至少部分设置在第一容纳空间2011中，进排气机构8用于将新鲜空气或可燃混合气送入燃烧室16，又将燃烧后的废气排到大气中。进排气机构8包括进气机构81和排气机构82， 进气机构81和排气机构82分布于气缸盖2内部的两侧，即进气机构81分布于气缸盖2内部的一侧，排气机构82分布于气缸盖2内部的另一侧。在本实施方式中，进气机构81和排气机构82关于贯穿线29基本呈对称分布。进气机构81用于将空气或混合气导入气缸体3，排气机构82用于收集、净化并且排放废气。
如图16所示，进气机构81包括进气道812和第一气门机构811，排气机构82包括排气道822和第二气门机构821，进气道812和排气道822基本对称的分布在贯穿线29的两侧，进气道812和贯穿线29之间设有第一气门机构811，排气道822和贯穿线29之间设有第二气门机构821，进气道812的一端和排气道822的一端均连通外界。通过上述设置方式，便于发动机100通过进气机构81将空气或混合气导入气缸体3，同时通过排气机构82将产生的废气收集、净化并且排放，从而实现控制发动机100的进气和排气的时间，以让发动机100在工作时气缸里有足够的气压。
具体的，进气道812的一端连通外界，进气道812的另一端连通气缸体3，排气道822的一端连通外界，排气道822的另一端连通气缸体3，便于气缸体3中的气体与外界气体进行交换。
如图16、图17和图19所示，气缸盖2中靠近进气道812侧设有第一限位机构24。第一限位机构24用于对第一气门机构811进行限位。第一限位机构24依次包括第一挺柱孔241、第一导管孔242和第一座圈孔243，第一气门机构811依次包括第一挺柱8111、第一气门弹簧8112、第一气门导管8113和进气门8114，第一挺柱8111的一端设在第一挺柱孔241中，第一气门弹簧8112的一端也设在第一挺柱孔241中。第一气门弹簧8112的另一端设在第一导管孔242的第一外沿2421处，第一气门导管8113的一端设在第一导管孔242内，第一气门导管8113的另一端设在第一气门弹簧8112中，进气门8114的一端分别穿过第一气门导管8113和第一气门弹簧8112后连接第一挺柱8111，进气门8114的另一端为进气盘8114a，进气盘8114a呈圆盘状，进气盘8114a的外轮廓与气缸盖2的轮廓基本一致，便于进气门8114将空气或混合气导入气缸体3。第一挺柱8111上方设有第一轮轴711，第一轮轴711上设有若干个控制第一挺柱8111的第一凸轮73，第一挺柱8111用于将第一轮轴711的推力传给进气门8114，并承受第一轮轴711旋转时所施加的侧向力。第一挺柱8111在顶部装有调节螺钉，用来调节进气门8114的间 隙。其中，第一外沿2421指围绕第一导管孔242的表面形成的边沿。第一限位机构24还包括第一弹簧座244，第一弹簧座244设在第一外沿2421处。第一气门弹簧8112的一端设在第一挺柱孔241中，第一气门弹簧8112的另一端设在第一弹簧座244上。
如图16、图18和图19所示，气缸盖2中靠近排气道822侧设有第二限位机构25。第二限位机构25用于对第二气门机构821进行限位。第二限位机构25依次包括第二挺柱孔251、第二导管孔252和第二座圈孔253，第二气门机构821依次包括第二挺柱8211、第二气门弹簧8212、第二气门导管8213和排气门8214，第二挺柱8211的一端设在第二挺柱孔251中，第二气门弹簧8212的一端也设在第二挺柱孔251中。第二气门弹簧8212的另一端设在第二导管孔252的第二外沿2521处，第二气门导管8213的一端设在第二导管孔252内，第二气门导管8213的另一端设在第二气门弹簧8212中，排气门8214的一端分别穿过第二气门导管8213和第二气门弹簧8212后连接第二挺柱8211，排气门8214的另一端为排气盘8214a，排气盘8214a呈圆盘状，排气盘8214a的外轮廓与气缸盖2的轮廓基本一致，便于排气门8214将产生的废气收集、净化并且排放。第二挺柱8211上方设有第二轮轴712，第二轮轴712上设有若干个控制第二挺柱8211的第二凸轮74，第二挺柱8211用于将第二轮轴712的推力传给排气门8214，并承受第二轮轴712旋转时所施加的侧向力。第二挺柱8211在顶部装有调节螺钉，用来调节排气门8214的间隙。其中，第二外沿2521指围绕第二导管孔252的表面所形成的边沿。第二限位机构25还包括第二弹簧座254，第二弹簧座254设在第二外沿2521处。第二气门弹簧8212的一端设在第二挺柱孔251中，第二气门弹簧8212的另一端设在第二弹簧座254上。
具体的，第一气门导管8113用于对进气门8114进行运动导向，保证进气门8114做往复直线运动，并将进气门8114的热量传给气缸盖2；第二气门导管8213用于对排气门8214进行运动导向，保证排气门8214做往复直线运动，并将排气门8214的热量传给气缸盖2。
第一气门导管8113通过过盈配合压入气缸盖2上的第一导管孔242中，第二气门导管8213通过过盈配合压入气缸盖2上的第二导管孔252中，从而防止第一气门导管8113和第二气门导管8213脱落。
如图16所示，在本实施方式中，曲轴131通过气门传动组件15(如图8所示)控制第一轮轴711转动，从而控制若干个第一凸轮73驱动进气门8114打开或关闭，且保证进气门8114的开闭动作与曲柄连杆132机构同步；曲轴131通过气门传动组件15控制第二轮轴712转动，从而控制若干个第二凸轮74驱动排气门8214打开，且保证排气门8214的开闭动作与曲柄同步。具体的，由于若干个第一凸轮73的设置方向不同，若干个第二凸轮74的设置方向不同，因此可以合理地控制进气门8114和排气门8214的开闭。气门传动组件15包括正时链条151，正时链条151分别连接曲轴131、第一轮轴711和第二轮轴712。通过正时链条151连接曲轴131、第一轮轴711和第二轮轴712，可以使曲轴131带动第一轮轴711和第二轮轴712转动，第一轮轴711驱动第一凸轮73驱动进气门8114打开或闭合，第二轮轴712驱动排气门8214打开或闭合，从而保证进气门8114和排气门8214的开闭动作与曲柄同步。其中，凸轮轴71包括第一轮轴711和第二轮轴712。正时链条151连接曲轴131、第一轮轴711和第二轮轴712，即正时链条151连接曲轴131和凸轮轴71。由于若干个第一凸轮73在第一轮轴711上的设置方向不同，若干个第二凸轮74在第二轮轴712上的设置方向不同，因此，曲轴131通过驱动凸轮轴71即可合理地控制进气门8114和排气门8214的开闭。
此外，第一限位机构24还包括进气座圈245，第二限位机构25还包括排气座圈255。进气座圈245设在进气道812的另一端连通气缸体3处。安装进气座圈245时，通过与第一座圈孔243的过盈配合，从而将进气座圈245固定在第一座圈孔243中。排气座圈255设在排气道822的另一端连通气缸体3处。安装排气座圈255时，通过与第二座圈孔253的过盈配合，从而将排气座圈255固定在第二座圈孔253中。
在本实施方式中，进气门8114的轴线与排气门8214的轴线基本处于同一平面上，从而使发动机100的进气和排气同步，可以更加顺畅地实现控制发动机100的进气和排气，以让发动机100在工作时气缸里有足够的气压。
作为一种实现方式，进气机构81基本沿第四直线700方向延伸，排气机构82基本沿第五直线800方向延伸。具体的，第一气门机构811基本沿第四直线700方向延伸，进气门8114基本沿第四直线700方向延伸。第二气门机构821基本沿第五直线800方向延伸，排气门8214基本沿第五直线800方向延伸。发动机100包括垂直于曲轴131的轴心线的投影平面900(如图3所 示)。如图21所示，气缸体3基本沿第一直线500方向延伸，气缸体3关于第一直线500基本对称设置。第四直线700与第一直线500垂直，第五直线800与第二直线500垂直，投影平面900基本与第一直线500垂直。沿第一直线500方向，第四直线700在投影平面900的投影为第一投影线，第五直线800在投影平面900的投影为第二投影线，贯穿线29在投影平面900的投影为第三投影线。第一投影线与第三投影线所成的锐角为第一夹角α，第二投影线与第三投影线所成的锐角为第二夹角β。具体的，进气机构81具有基本沿第四直线700方向延伸的中心线，第一气门机构811具有基本沿第四直线700方向延伸的中心线，进气门8114具有基本沿第四直线700方向延伸的轴线。沿第一直线500方向，进气机构81的中心线在投影平面900的投影基本与第一投影线重合，第一气门机构811的中心线在投影平面900的投影基本与第一投影线重合，进气门8114的轴线在投影平面900的投影基本与第一投影线重合。具体的，排气机构82具有基本沿第五直线800方向延伸的中心线，第二气门机构821具有基本沿第五直线800方向延伸的中心线，排气门8214具有基本沿第五直线800方向延伸的轴线。沿第一直线500方向，排气机构82的中心线在投影平面900的投影基本与第二投影线重合，第二气门机构821的中心线在投影平面900的投影基本与第二投影线重合，排气门8214的轴线在投影平面900的投影基本与第二投影线重合。在本实施方式中，沿第一直线500方向，第一投影线与第三投影线在投影平面900的投影所成的夹角为第一夹角α，即进气机构81的中心线与贯穿线29在投影平面900的投影所成的夹角为第一夹角α，第一气门机构811的中心线与贯穿线29在投影平面900的投影所成的夹角为第一夹角α，进气门8114的轴线与贯穿线29在投影平面900的投影所成的夹角为第一夹角α。沿第一直线500方向，第二投影线与第三投影线在投影平面900的投影所成的夹角为第二夹角β，即排气机构82的中心线与贯穿线29在投影平面900的投影所成的夹角为第二夹角β，第二气门机构821的中心线与贯穿线29在投影平面900的投影所成的夹角为第二夹角β，排气门8214的轴线与贯穿线29在投影平面900的投影所成的夹角为第二夹角β。在本实施方式中，第一夹角α和第二夹角β的角度可以基本一致，即第一投影线和第二投影线关于第三投影线基本对称设置。
作为一种实现方式，如图21所示，气缸体3包括气缸孔301。具体的，当气缸孔301的孔径为大于等于70mm且小于等于74mm时，第一夹角α为大于等于11°且小于等于15°，第二夹角β为大于等于11°且小于等于15°。其中，气缸孔301的孔径指气缸体3的气缸孔301的直径。具体的，当气缸孔301的孔径为大于等于70mm且小于等于74mm时，沿第一直线500方向，进气机构81的中心线与贯穿线29在投影平面900的投影所成的夹角为大于等于11°且小于等于15°，第一气门机构811的中心线与贯穿线29在投影平面900的投影所成的夹角为大于等于11°且小于等于15°，进气门8114的轴线与贯穿线29在投影平面900的投影所成的夹角为大于等于11°且小于等于15°。当气缸孔301的孔径为大于等于70mm且小于等于74mm时，沿第一直线500方向，排气机构82的中心线与贯穿线29在投影平面900的投影所成的夹角为大于等于11°且小于等于15°，第二气门机构821的中心线与贯穿线29在投影平面900的投影所成的夹角为大于等于11°且小于等于15°，排气门8214的轴线与贯穿线29在投影平面900的投影所成的夹角为大于等于11°且小于等于15°。通过上述对进排气机构8的设置方式，采用了合理布置角度，既可以使发动机100的进气容积较为合理，从而使发动机100的运行更加稳定，提高发动机100的使用寿命；又可以使发动机100的排气温度场分布合理，从而可以提高发动机100在排气时的散热效果，便于发动机100的冷却，进而实现发动机100进气和排气之间的平衡，提高发动机100的散热效果和使用寿命。
在本实施方式中，当气缸孔301的孔径为大于等于71mm且小于等于73mm时，第一夹角α为大于等于12°且小于等于14°，第二夹角β为大于等于12°且小于等于14°。具体的，当气缸孔301的孔径为大于等于71mm且小于等于73mm时，沿第一直线500方向，进气机构81的中心线与贯穿线29在投影平面900的投影所成的夹角为大于等于12°且小于等于14°，第一气门机构811的中心线与贯穿线29在投影平面900的投影所成的夹角为大于等于12°且小于等于14°，进气门8114的轴线与贯穿线29在投影平面900的投影所成的夹角为大于等于12°且小于等于14°。当气缸孔301的孔径为大于等于71mm且小于等于73mm时，沿第一直线500方向，排气机构82的中心线与贯穿线29在投影平面900的投影所成的夹角为大于等于12°且小于等于14°，第二气门机构821的中心线与贯穿线29在投影平面900 的投影所成的夹角为大于等于12°且小于等于14°，排气门8214的轴线与贯穿线29在投影平面900的投影所成的夹角为大于等于12°且小于等于14°。通过上述对进排气机构8的设置方式，既可以使发动机100的进气容积较为合理，从而使发动机100的运行更加稳定；又可以使发动机100的排气温度场分布合理，从而可以提高发动机100在排气时的散热效果。
在本实施方式中，当气缸孔301的孔径为72mm时，第一夹角α为13°，第二夹角β为13°。具体的，当气缸孔301的孔径为72mm时，沿第一直线500方向，进气机构81的中心线与贯穿线29在投影平面900的投影所成的夹角为13°，第一气门机构811的中心线与贯穿线29在投影平面900的投影所成的夹角为13°，进气门8114的轴线与贯穿线29在投影平面900的投影所成的夹角为13°。当气缸孔301的孔径为72mm时，沿第一直线500方向，排气机构82的中心线与贯穿线29在投影平面900的投影所成的夹角为13°，第二气门机构821的中心线与贯穿线29在投影平面900的投影所成的夹角为13°，排气门8214的轴线与贯穿线29在投影平面900的投影所成的夹角为13°。通过上述对进排气机构8的设置方式，既可以使发动机100的进气容积更为合理，从而使发动机100的运行更加稳定；又可以使发动机100的排气温度场分布更为合理，从而可以提高发动机100在排气时的散热效果，便于发动机100的冷却。
此外，如图16至图17所示，第一限位机构24还包括第一锁座246。第一锁座246至少部分设在第一挺柱8111和第一气门弹簧8112之间。第一气门弹簧8112的一端设在第一弹簧座244上，第一气门弹簧8112的另一端设在第一锁座246上。其中，第一锁座246用于固定第一气门弹簧8112的一端。第一锁座246上设有第一锁夹247，第一锁夹247用于限制第一气门弹簧8112和进气门8114的径向方向的运动，即使得第一气门弹簧8112和进气门8114仅在第四直线700方向运动，以便于进气机构81将空气或混合气导入气缸体3。
第二限位机构25还包括第二锁座256。第二锁座256至少部分设在第二挺柱8211和第二气门弹簧8212之间。第二气门弹簧8212的一端设在第二弹簧座254上，第二气门弹簧8212的另一端设在第二锁座256上。其中，第二锁座256用于固定第二气门弹簧8212的一端。第二锁座256上设有第二锁夹257，第二锁夹257用于限制第二气门弹簧8212和排气门8214的径向方向的 运动，即使得第二气门弹簧8212和排气门8214仅在第五直线800方向运动，以便于排气机构82将产生的废气收集、净化并且排放。
具体的，进气门8114靠近第一挺柱8111的一端为进气杆8114b，排气门8214靠近第二挺柱8211的一端为排气杆8214b。在第一气门弹簧8112的弹簧力作用下，第一锁夹247将第一气门弹簧8112和进气杆8114b锁住；在第二气门弹簧8212的弹簧力作用下，第二锁夹257将第二气门弹簧8212和排气杆8214b锁住。进气杆8114b与进气盘8114a为一体件，进气杆8114b依次穿过第一气门导管8113、第一气门弹簧8112后连接第一挺柱8111。排气杆8214b与排气盘8214a为一体件，排气杆8214b依次穿过第二气门道管、第二气门弹簧8212后连接第二挺柱8211。
作为一种实现方式，进气杆8114b具有沿第四直线700方向延伸的轴线，排气杆8214b具有沿第五直线800方向延伸的轴线。沿第一直线500方向，进气杆8114b的轴线在投影平面900的投影基本与第一投影线重合，排气杆8214b的轴线在投影平面900的投影基本与第二投影线重合。具体的，当气缸孔301的孔径为大于等于70mm且小于等于74mm时，沿第一直线500方向，进气杆8114b的轴线与贯穿线29在投影平面900的投影所成的夹角为大于等于11°且小于等于15°，排气杆8214b的轴线与贯穿线29在投影平面900的投影所成的夹角为大于等于11°且小于等于15°。具体的，当气缸孔301的孔径为大于等于70mm且小于等于74mm时，沿第一直线500方向，进气杆8114b的轴线与贯穿线29在投影平面900的投影所成的夹角为13°，排气杆8214b的轴线与贯穿线29在投影平面900的投影所成的夹角为13°。
具体的，当气缸孔301的孔径为大于等于71mm且小于等于73mm时，沿第一直线500方向，进气杆8114b的轴线与贯穿线29在投影平面900的投影所成的夹角为大于等于12°且小于等于14°，排气杆8214b的轴线与贯穿线29在投影平面900的投影所成的夹角为大于等于12°且小于等于14°。通过上述对进气杆8114b和排气杆8214b的设置方式，可以使发动机100的进气容积更加合理，从而使发动机100的运行更加稳定。
在本实施方式中，当气缸孔301的孔径为72mm时，沿第一直线500方向，进气杆8114b的轴线与贯穿线29在投影平面900的投影所成的夹角为13°，排气杆8214b的轴线与贯穿线29在投影平面900的投影所成的夹角为13°。通过上述对进气杆8114b和排气杆8214b的设置方式，采用了合理布 置角度，既可以使发动机100的进气容积更为合理，从而使发动机100的运行更加稳定，提高发动机100的使用寿命；又可以使发动机100的排气温度场分布更为合理，从而可以提高发动机100在排气时的散热效果，便于发动机100的冷却，进而实现发动机100进气和排气之间的平衡，提高发动机100的散热效果和使用寿命。
作为一种实现方式，气缸盖2与气缸体3固定连接，气缸盖2与气缸体3固定连接处为第一固定部307(如图5所示)，气缸盖2靠近第一固定部307的一侧为气缸盖2的底部，气缸盖2靠近第一固定部307的面为气缸盖2的底面。如图20和图21所示，气缸体3包括气缸孔301，气缸盖2的底部设有若干个气缸口26，每个气缸口26均与一个气缸孔301连通，若干个气缸口26周围分布有冷却机构21。具体的，当发动机100为单缸发动机时，气缸盖2的底部设有一个气缸口26；当发动机100为双缸发动机时，气缸盖2的底部设有两个气缸口26。冷却机构21包括若干个冷却水道211，若干个冷却水道211包围若干个气缸口26，从而便于提高气缸盖2的冷却效果，使气缸盖2中的各个零部件得到更好的冷却，有利于提高发动机100的使用寿命。
此外，气缸盖2的底部还设有第一孔组件27和第二传动腔区28。第一孔组件27包括若干个缸盖螺栓过孔271和第一回油孔272，若干个缸盖螺栓过孔271包括若干个缸盖螺栓大孔2711和若干个缸盖螺栓小孔2712。若干个缸盖螺栓大孔2711均匀分布在气缸口26周围，便于在安装过程中，实现气缸盖2和气缸体3的固定，有利于提高气缸盖2和气缸体3之间的连接稳定性。气缸盖2关于贯穿线29基本对称设置。第二传动腔区28设在在气缸口26的一侧，第二传动腔区28的中心与气缸口26的中心均基本处于贯穿线29上，即第二传动腔区28的中心与气缸口26的中心基本处于同一直线。第二传动腔区28用于设置气门传动组件15，便于气门传动组件15穿过气缸盖2，从而使气门传动组件15分别连接曲轴131和凸轮机构7，实现曲轴131对凸轮机构7的驱动作用。若干个缸盖螺栓小孔2712均匀分布在第二传动腔区28周围，既可以实现固定气缸盖2和气缸体3的作用，又可以将第二传动腔区28固定在气缸体3上，从而实现气缸盖2和气缸体3的稳定连接。第一回油孔272设置在若干个缸盖螺栓过孔271周围，第一回油孔272是发动机100内部的润滑油的流动通道，有利于发动机100内润滑油的循环流动，从 而提高发动机100内部零件之间的润滑作用，进而提高发动机100的使用寿命。
具体的，当发动机100为单缸发动机时，进排气机构8的数量为一个，进气机构81和排气机构82的数量均为两个；当发动机100为双缸发动机时，进排气机构8的数量为两个，进气机构81和排气机构82的数量均为四个；即一个进排气机构8包括两个进气机构81和两个排气机构82。具体的，一个气缸口26中设置有两个进气机构81和两个排气机构82，两个进气机构81包括第一进气机构813和第二进气机构814，两个排气机构82包括第一排气机构823和第二排气机构824。
如图20所示，第一进气机构813和第二进气机构814之间的中心距为第一中心距J，第一排气机构823和第二进气机构824的中心距为第二中心距K。其中，第一进气机构813和第二进气机构814之间的中心距指第一进气机构813的中心和第二进气机构814的中心之间的最短距离，第一排气机构823和第二进气机构824的中心距指第一排气机构823的中心和第二进气机构824的中心之间的最短距离。
如图20所示，在本实施方式中，气缸口26处设有两个进气座圈245和两个排气座圈255。进气座圈245设在靠近进气机构81一侧，用于与进气门8114配合，实现进气机构81将空气或混合气导入气缸体3。排气座圈255设在靠近排气机构82一侧，用于与排气门8214配合，实现排气机构82将产生的废气收集、净化并且排放。两个进气座圈245关于气缸口26的径向中心线呈对称分布，两个排气座圈255关于气缸口26的径向中心线呈对称分布。其中，气缸口26的径向中心线指沿进气道812-排气道822方向的气缸口26径向中心线。
作为一种实现方式，当气缸孔301的孔径为72mm时，通过采用合理的进、排气门8214间距布置，从而使发动机100的外形尺寸较小，重量较轻，使气缸盖2的散热和温度场分布较为合理。其中，气缸孔301的孔径指气缸体3的气缸孔301的直径。
当气缸孔301的孔径为72mm时，第一中心距J为32.2mm，第二中心距K为29.1mm。具体的，第一进气机构813包括第一进气门，第二进气机构814包括第二进气门，第一进气门和第二进气门之间的中心距为32.2mm，即第一进气门和第二进气门之间的中心距基本为第一中心距J。第一排气机构 823包括第一排气门，第二进气机构824包括第二排气门，第一排气门和第二排气门之间的中心距为29.1mm，即第一排气门和第二排气门之间的中心距基本为第二中心距K。其中，第一进气门和第二进气门的中心距指第一进气门的中心和第二进气门的中心之间的最短距离，第一排气门和第二排气门的中心距指第一排气门的中心和第二排气门的中心之间的最短距离。通过对第一中心距J和第二中心距K的设置，采用了合理布置距离，既可以使发动机100的进气容积更为合理，从而使发动机100的运行更加稳定，提高发动机100的使用寿命；又可以使发动机100的排气温度场分布更为合理，从而可以提高发动机100在排气时的散热效果，便于发动机100的冷却，进而实现发动机100进气和排气之间的平衡，提高发动机100的散热效果和使用寿命。此外，通过对第一中心距J和第二中心距K的设置，使发动机100的结构更加紧凑，提高发动机100的空间利用率，减少资源的浪费，从而使进气机构81和排气机构82的结构更加合理，提高进排气机构8的使用寿命，进而提高发动机100的使用寿命。
其中，第一进气门和第二进气门的中心距通过进气盘8114a的盘径、鼻梁厚度、第一进气门和第二进气门之间的壁厚等参数进行计算得到；第一排气门和第二排气门的中心距通过排气盘8214a的盘径、鼻梁厚度、第一排气门和第二排气门之间的壁厚等参数进行计算得到，鼻梁厚度指相邻的进气门8114和排气门8214之间的壁厚。
可以理解，当气缸孔301的孔径为大于等于70mm且小于等于74mm时，第一中心距J可以进行1～2mm的距离调整，即第一中心距J可以是大于等于30.2mm且小于等于34.2mm，第一进气机构813和第二进气机构814之间的中心距可以是大于等于30.2mm且小于等于34.2mm，以适应发动机100的整体结构；当气缸孔301的孔径为大于等于70mm且小于等于74mm时，第二中心距K可以进行1～2mm的距离调整，即第二中心距K可以是大于等于27.1mm且小于等于31.1mm，第一排气机构823和第二进气机构824的中心距可以是大于等于27.1mm且小于等于31.1mm，以适应发动机100的整体结构。当气缸孔301的孔径为大于等于70mm且小于等于74mm时，第一进气门和第二进气门的中心距可以进行1～2mm的距离调整，即第一进气门和第二进气门的中心距可以是大于等于30.2mm且小于等于34.2mm，以适应发动机100的整体结构；当气缸孔301的孔径为大于等于70mm且小于等于74mm 时，第一排气门和第二排气门的中心距可以进行1～2mm的距离调整，即第一排气门和第二排气门的中心距可以是大于等于27.1mm且小于等于31.1mm，以适应发动机100的整体结构。其中，第一进气门和第二进气门的中心距指第一进气门的中心和第二进气门的中心之间的最短距离，具体指两个进气盘8114a中心之间的最短距离。第一排气门和第二排气门的中心距指第一排气门的中心和第二排气门的中心之间的最短距离，具体指两个排气盘8214a中心之间的最短距离。1～2mm的距离调整指：将第一进气门和第二进气门原有中心距值进行前后1～2mm的距离调整，或将第一排气门和第二排气门原有中心距值进行前后1～2mm的距离调整，或将第一进气门和第二进气门原有中心距值以及第一排气门和第二排气门原有中心距值均进行前后1～2mm的距离调整。
在本实施方式中，第一进气门包括第一进气盘，第二进气门包括第二进气盘，第一排气门包括第一排气盘，第二排气门包括第二排气盘。当气缸孔301的孔径为大于等于70mm且小于等于74mm时，第一进气盘和第二进气盘的中心距可以是大于等于30.2mm且小于等于34.2mm，即第一进气盘和第二进气盘的中心距基本为第一中心距J，以适应发动机100的整体结构；第一排气盘和第二排气盘的中心距可以是大于等于27.1mm且小于等于31.1mm，即第一排气盘和第二排气盘的中心距基本为第二中心距K，以适应发动机100的整体结构。其中，第一进气盘和第二进气盘的中心距指第一进气盘的中心和第二进气盘的中心之间的最短距离；第一排气盘和第二排气盘的中心距指第一排气盘的中心和第二排气盘的中心之间的最短距离。
作为一种实现方式，当气缸孔301的孔径为大于等于71mm且小于等于73mm时，第一中心距J可以是大于等于31.2mm且小于等于33.2mm，第一进气机构813和第二进气机构814之间的中心距可以是大于等于31.2mm且小于等于33.2mm；第二中心距K可以是大于等于28.1mm且小于等于30.1mm，第一排气机构823和第二进气机构824的中心距可以是大于等于28.1mm且小于等于30.1mm，以适应发动机100的整体结构。
具体的，当气缸孔301的孔径为大于等于71mm且小于等于73mm时，第一进气门和第二进气门的中心距可以是大于等于31.2mm且小于等于33.2mm，第一排气门和第二排气门的中心距可以是大于等于28.1mm且小于等于30.1mm，以适应发动机100的整体结构。
在本实施方式中，当气缸孔301的孔径为大于等于71mm且小于等于73mm时，第一进气盘和第二进气盘的中心距可以是大于等于31.2mm且小于等于33.2mm，第一排气盘和第二排气盘的中心距可以是大于等于28.1mm且小于等于30.1mm，以适应发动机100的整体结构。
如图21所示，气缸体3中设有气缸孔301和第三传动腔区303，气缸孔301的中心与第三传动腔区303的中心均基本处于气缸体3中心线上，即第三传动腔区303的中心与气缸孔301的中心基本处于同一直线。其中，气缸体3中心线指沿第一直线500方向的气缸体3的中心线，且气缸体3中心线基本与第一直线500重合，第一直线500与第二直线300、第三直线400平行。当发动机100为单缸发动机时，气缸孔301的数量为一个，气缸孔301和第三传动腔区303的分布方向为沿第一直线500方向；当发动机100为双缸发动机时，气缸孔301的数量为两个，气缸孔301包括第一气缸孔3011和第二气缸孔3012。第一气缸孔3011和第二气缸孔3012互不连通，第一气缸孔3011的孔径和第二气缸孔3012的孔径基本一致。其中，第一气缸孔3011的孔径指第一气缸孔3011的直径，第二气缸孔3012的孔径指第二气缸孔3012的直径。第一气缸孔3011、第二气缸孔3012和第三传动腔区303分布方向为沿第一直线500方向，第一气缸孔3011、第二气缸孔3012和第三传动腔区303的排列方式依次为第一气缸孔3011、第二气缸孔3012、第三传动腔区303。
第三传动腔区303用于设置气门传动组件15，便于气门传动组件15穿过气缸体3，从而使气门传动组件15分别连接曲轴131和凸轮机构7，实现曲轴131对凸轮机构7的驱动作用。
气缸体3中设有若干个第一固定孔304和第二回油孔305，若干个第一固定孔304均匀分布在气缸孔301周围，便于在固定过程中，实现气缸盖2和气缸体3的固定，既有利于提高气缸盖2和气缸体3之间的连接稳定性，又有利于提高气缸体3和曲轴箱4之间的连接稳定性。第二回油孔305设置在若干个第一固定孔304周围，与第一回油孔272配合，形成发动机100内部的润滑油的流动通道，有利于发动机100内润滑油的循环流动，从而提高发动机100内部零件之间的润滑作用，进而提高发动机100的使用寿命。具体的，气缸体3设有缸体边沿306，缸体边沿306围绕气缸体3设置，若干个第一固定孔304和第二回油孔305均设在缸体边沿306上，若干个第一固定 孔304和第二回油孔305均贯通缸体边沿306，既便于通过若干个第一固定孔304连接气缸体3和气缸盖2，又便于通过若干个第一固定孔304连接气缸体3和曲轴箱4。
此外，气缸体3中设有冷却水套302，冷却水套302均匀分布在气缸孔301周围，从而使冷却水套302包围气缸孔301，提高冷却水套302对气缸孔301的冷却效果，进而提高发动机100的使用寿命。具体的，当发动机100为单缸发动机时，冷却水套302围绕气缸孔301，冷却水套302的内轮廓和气缸孔301的外轮廓基本一致，便于冷却水套302更好地冷却气缸孔301，从而提高对活塞机构11的冷却效果，进而提高了发动机100的散热效果。当发动机100为双缸发动机时，冷却水套302围绕第一气缸孔3011和第二气缸孔3012，第一气缸孔3011和第二气缸孔3012组合后形成有第一外轮廓，冷却水套302的内轮廓和第一外轮廓基本一致，冷却水套302基本呈“8”字形围绕第一气缸孔3011和第二气缸孔3012，便于冷却水套302更好地冷却气缸孔301，从而提高对活塞机构11的冷却效果，进而提高了发动机100的散热效果。其中，冷却水套302的内轮廓指靠近气缸孔301的轮廓，气缸孔301的外轮廓指靠近冷却水套302的轮廓，第一外轮廓指第一气缸孔3011和第二气缸孔3012设置在气缸体3中后，第一气缸孔3011和第二气缸孔3012形成的基本为“8”字型的外轮廓。
在本实施方式中，活塞机构11设置在气缸孔301中，活塞机构11的数量与气缸孔301的数量一致，便于活塞机构11在气缸孔301中做往复运动，既可以通过气缸孔301限定活塞机构11的位置，又可以使冷却水套302通过气缸孔301冷却活塞机构11，便于提高活塞机构11的散热效果。具体的，冷却水套302中设有冷却液，冷却液可以在冷却水套302中流动，从而通过气缸孔301实现对活塞机构11的冷却。如图4所示，具体的，活塞机构11包括活塞111和活塞销112，活塞111和连杆132之间通过活塞销112连接。活塞111的数量与气缸孔301的数量一致，便于活塞111在气缸孔301中做往复运动，既可以通过气缸孔301限定活塞111的位置，又可以使冷却水套302通过气缸孔301冷却活塞111，便于提高活塞111的散热效果。
作为一种实现方式，当发动机100为双缸发动机、气缸孔301的孔径为72mm时，第一气缸孔3011和第二气缸孔3012的缸心距为缸心距L，缸心距L通过第一气缸孔3011和第二气缸孔3012间的壁厚和气缸孔301的孔径进 行计算，便于得到双缸发动机的最佳缸心距，使发动机100的外形尺寸较小，重量较轻，充分利用了气缸体3的空间，使气缸体3的散热和温度场分布较为合理，从而提高气缸体3和活塞机构11的散热效果，提高气缸体3和活塞机构11的使用寿命，进而提高发动机100的散热效果和使用寿命。其中，当发动机100为双缸发动机时，第一气缸孔3011和第二气缸孔3012间的壁厚为缸间壁厚，缸心距L指第一气缸孔3011的中心和第二气缸孔3012的中心之间的距离；气缸孔301的孔径指气缸体3的气缸孔301的直径。
当气缸孔301的孔径确定后，影响缸心距L的因素是缸间壁厚。当缸间壁厚太厚时，会增加发动机100的横向尺寸，且不利于发动机100的冷却。在现有技术中，7mm的缸间壁厚已是相对优秀的水平，因此，缸心距L可以通过缸间壁厚和气缸孔301的孔径相加所得。
具体的，当发动机100为双缸发动机、气缸孔301的孔径为大于等于70mm且小于等于74mm时，通过缸间壁厚和气缸孔301的孔径计算可得，第一气缸孔3011和第二气缸孔3012的缸心距L为大于等于76mm且小于等于82mm。此时，发动机100的外形尺寸较小，重量较轻，整体结构较为紧凑，充分利用了气缸体3的空间，使气缸体3的散热和温度场分布较为合理，从而提高气缸体3和活塞机构11的散热效果，提高气缸体3和活塞机构11的使用寿命，进而提高发动机100的散热效果和使用寿命。
在本实施方式中，当发动机100为双缸发动机、气缸孔301的孔径为大于等于71mm且小于等于73mm时，第一气缸孔3011和第二气缸孔3012的缸心距L为大于等于78mm且小于等于80mm。此时，发动机100的外形尺寸较小，重量较轻，整体结构较为紧凑。
本申请针对气缸孔301的孔径为72mm的双缸发动机，根据第一进气门和第二进气门的中心距、第一排气门和第二排气门的中心距等结构参数，通过缸心距L计算方法，得到最优的第一气缸孔3011和第二气缸孔3012的缸心距L，即第一气缸孔3011和第二气缸孔3012的缸心距L为79mm。此时，发动机100的进气容积较为合理，排气温度场分布合理，从而实现发动机100进气和排气之间的平衡，提高了发动机100的散热效果。
此外，在气缸孔301的孔径为72mm，且第一气缸孔3011和第二气缸孔3012的缸心距为79mm时，发动机100的外形尺寸和重量较优，发动机100的缸体散热效果较好，发动机100的进排气容积效率较合理，从而使发动机 100的各个零部件装配更加合理，进而使发动机100的整体结构更加紧凑，提高了发动机100的工作效率和使用寿命。
可以理解的，当发动机100为双缸发动机、气缸孔301的孔径为大于等于70mm且小于等于74mm时，第一气缸孔3011和第二气缸孔3012的缸心距L可以为大于等于78mm且小于等于80mm。当发动机100为双缸发动机、气缸孔301的孔径为大于等于71mm且小于等于73mm时，第一气缸孔3011和第二气缸孔3012的缸心距L可以大于等于76mm且小于等于82mm。
在发动机100的工作循环中，活塞111的运动速度非常快，而且速度很不均匀。在上下止点位置，活塞111的速度为零；在上下止点中间的位置，活塞111的速度达到最高。由于活塞111在气缸体3内做反复的高速直线运动，必然在活塞111、活塞销112和连杆132上产生很大的惯性力。在连杆132上配置的配重可以有效地平衡这些惯性力。但连杆132上的配重只有一部分运动质量参与直线运动，连杆132上另一部分配重参与旋转运动。除了上下止点位置外，各种惯性力不能被完全平衡，使发动机100产生了振动。其中，上止点为活塞111顶部距离曲轴131旋转中心最远的位置，下止点为活塞111顶部距离曲轴131旋转中心最近的位置，上止点和下止点合成为上下止点。
当活塞111每上下运动一次，将使发动机100产生一上一下两次振动，所以发动机100的振动频率和发动机100的转速有关。在振动理论上，常使用多个谐波振动来描述发动机的振动，其中振动频率和发动机转速相同的叫一阶振动，频率是发动机转速两倍的叫二阶振动，依次类推，还存在三阶、四阶振动。但振动频率越高，振幅就越小，二阶以上可以忽略不计。其中，一阶振动占整个振动的70％以上，是振动的主要来源。
为了消除振动，采用的方法有很多，但在摩托车发动机上普遍采用的方式是增加平衡机构来解决。如图22所示，平衡机构14包括装有偏心重块141并随曲轴131同步旋转的轴，利用偏心重块141所产生的反向振动力，使发动机100获得良好的平衡效果，降低发动机100振动。
作为一种实现方式，平衡机构14与曲轴131配合，实现平衡机构14与曲轴131的同步转动。平衡机构14包括第一平衡轴142、第一轴齿轮143、第二平衡轴144、第二轴齿轮145和主动轴齿轮146。曲轴箱4上设有若干个两两对应的固定轴孔401，第一平衡轴142、第二平衡轴14、传动主轴121、 传动副轴122和曲轴131均设在固定轴孔401中，第一平衡轴142、第二平衡轴14、传动主轴121、传动副轴122和曲轴131基本呈平行设置。第一轴齿轮143设置在第一平衡轴142上，第二轴齿轮145设置在第二平衡轴144上，主动轴齿轮146设置在曲轴131上，主动轴齿轮146分别与第一轴齿轮143、第二轴齿轮145啮合。平衡机构14采用双平衡轴方式，其中第一平衡轴142和第二平衡轴144关于曲轴131中心线成角度对称布置，第一平衡轴142相对曲轴131的旋转方向和第二平衡轴144相对曲轴131的旋转方向相反，第一平衡轴142的转速与曲轴131转速相同，第二平衡轴144的转速与曲轴131转速相同，用以平衡发动机100的一阶往复惯性力，从而实现减少发动机100振动，降低发动机100的噪音，延长发动机100使用寿命，提升驾乘者的舒适度。
第一平衡轴142、第二平衡轴144和曲轴131互相平行，第一轴齿轮143设在第一平衡轴142的一端，第二轴齿轮145设在第二平衡轴144的一端，主动轴齿轮146设在曲轴131的一端。第一轴齿轮143、第二轴齿轮145和主动轴齿轮146至少部分分布在同一平面内，实现第一轴齿轮143和主动轴齿轮146之间的啮合，第二轴齿轮145和主动轴齿轮146之间的啮合，从而便于曲轴131将转动运动传递给第一平衡轴142和第二平衡轴144。其中，第一轴齿轮143和第一平衡轴142通过现有的固定连接固定，第一轴齿轮143和第一平衡轴142通过现有的固定连接固定，主动轴齿轮146和曲轴131通过现有的固定连接固定。
第一平衡轴142和曲轴131的中心距大于等于72mm且小于等于76mm，第二平衡轴144和曲轴131的中心距大于等于72mm且小于等于76mm，第一平衡轴142和曲轴131的中心距为第一中心距H，第二平衡轴144和曲轴131的中心距为第二中心距G，第一中心距H和第二中心距G均通过连杆132的包络线133运动轨迹、第一平衡轴142和第二平衡轴144的强度确定。具体的，第一中心距H设置为73mm，第二中心距G设置为73mm，从而通过减少第一平衡轴142和曲轴131的中心距、第二平衡轴144和曲轴131的中心距的方式实现发动机100的轻量化。其中，第一中心距H和第二中心距G是指两个轴的中心之间的最短距离，第一中心距H即第一平衡轴142中心与曲轴131中心的最短距离，第二中心距G即第二平衡轴144中心与曲轴131中心的最短距离。
如图22所示，曲轴箱4包括与贯穿线29垂直的第一水平面，第一水平面与投影平面900垂直，且曲轴131的轴心处于第一水平面上。沿第一直线500方向，第一平衡轴142的轴心在投影平面900的投影为第一投影点，第二平衡轴144的轴心在投影平面900的投影为第二投影点，曲轴131的轴心在投影平面900的投影为第三投影点，第一水平面在投影平面900的投影为第四投影线，第一投影点和第三投影点的连线为第五投影线，第二投影点和第三投影点的连线为第六投影线。第五投影线和第四投影线所形成的锐角为第三夹角δ，第六投影线和第四投影线所形成的锐角为第四夹角γ。具体的，第一平衡轴142的轴心和曲轴131的轴心的连线在投影平面900的投影与第一水平面在投影平面900的投影所形成的锐角为第三夹角δ，第二平衡轴144的轴心和曲轴131的轴心的连线在投影平面900的投影与第一水平面在投影平面900的投影所形成的锐角为第四夹角γ。第三夹角δ大于等于0°且小于等于20°，第四夹角γ大于等于0°且小于等于20°，在该范围内，可以使发动机100的整机振动频率和振幅降至最小，能使发动机100的整体设计外型较小、重量较轻，从而使发动机100的结构更加紧凑，提高发动机100的空间利用率，使发动机100运行的平稳性更好，进而提高发动机100的使用寿命。其中，当第三夹角δ为0°、第四夹角γ为0°时，第一投影点、第二投影点和第三投影点基本处于同一直线上，即第一平衡轴142的轴心在投影平面900的投影、第二平衡轴144的轴心在投影平面900的投影和曲轴131的轴心在投影平面900的投影基本处于同一直线上。具体的，第三夹角δ设置为20°，第四夹角γ设置为20°，此时，第五投影线和第六投影线之间的夹角为140°，第一中心距H为最短中心距73mm，第二中心距G为最短中心距73mm。在第三夹角δ和第四夹角γ均为20°、第一中心距H和第二中心距G均为73mm时，发动机100结构最为紧凑，从而在保证发动机100正常运行的情况下，实现了发动机100的轻量化，提高了资源利用率。在本实施方式中，当第三夹角δ、第四夹角γ均超过20°时，由于连杆132包络线133的存在，第一平衡轴142和第二平衡轴144会与内部结构(如连杆132等)发生碰撞，从而影响发动机100的整体运行。其中连杆132包络线133是指连杆132的运动轨迹所形成的几何形状。
在本实施方式中，第三夹角δ和第四夹角γ可以关于贯穿线29基本对称设置，即两个夹角的角度基本相同。
作为一种实现方式，当第一中心距H大于等于72mm且小于等于76mm以及第二中心距G大于等于72mm且小于等于76mm时，第三夹角δ大于等于0°且小于等于20°，第四夹角γ大于等于0°且小于等于20°。具体的，当第一平衡轴142和曲轴131的中心距大于等于72mm且小于等于76mm，第二平衡轴144和曲轴131的中心距大于等于72mm且小于等于76mm时，第五投影线和第四投影线所形成的夹角大于等于0°且小于等于20°，第六投影线和第四投影线所形成的夹角大于等于0°且小于等于20。通过上述设置，可以使发动机100的整机振动频率和振幅降至较小，能使发动机100的整体设计外型较小、重量较轻，从而使发动机100的结构更加紧凑，实现发动机100的轻量化，提高发动机100的空间利用率，使发动机100运行的平稳性更好，进而提高发动机100的使用寿命。
具体的，当第一中心距H大于等于72mm且小于等于74mm以及第二中心距G大于等于72mm且小于等于74mm时，第三夹角δ大于等于0°且小于等于20°，第四夹角γ大于等于0°且小于等于20°。在本实施方式中，当第一平衡轴142和曲轴131的中心距大于等于72mm且小于等于74mm，第二平衡轴144和曲轴131的中心距大于等于72mm且小于等于74mm时，第五投影线和第四投影线所形成的夹角大于等于0°且小于等于20°，第六投影线和第四投影线所形成的夹角大于等于0°且小于等于20°。通过上述设置，可以使发动机100的整机振动频率和振幅降至较小，能使发动机100的整体设计外型较小、重量较轻，从而使发动机100的结构更加紧凑，实现发动机100的轻量化，提高发动机100的空间利用率，使发动机100运行的平稳性更好，进而提高发动机100的使用寿命。
具体的，当第一中心距H大于等于72mm且小于等于74mm以及第二中心距G大于等于72mm且小于等于74mm时，第三夹角δ大于等于10°且小于等于20°，第四夹角γ大于等于10°且小于等于20°。在本实施方式中，当第一平衡轴142和曲轴131的中心距大于等于72mm且小于等于74mm，第二平衡轴144和曲轴131的中心距大于等于72mm且小于等于74mm时，第五投影线和第四投影线所形成的夹角大于等于10°且小于等于20°，第六投影线和第四投影线所形成的夹角大于等于10°且小于等于20°。通过上述设置，可以使发动机100的整机振动频率和振幅降至较小，能使发动机100的整体设计外型较小、重量较轻，从而使发动机100的结构更加紧凑，实现 发动机100的轻量化，提高发动机100的空间利用率，使发动机100运行的平稳性更好，进而提高发动机100的使用寿命。
可以理解的，当第一中心距H大于等于72mm且小于等于76mm以及第二中心距G大于等于72mm且小于等于76mm时，第三夹角δ大于等于10°且小于等于20°，第四夹角γ大于等于10°且小于等于20°。具体的，当第一平衡轴142和曲轴131的中心距大于等于72mm且小于等于76mm，第二平衡轴144和曲轴131的中心距大于等于72mm且小于等于76mm时，第五投影线和第四投影线所形成的夹角大于等于10°且小于等于20°，第六投影线和第四投影线所形成的夹角大于等于10°且小于等于20。
具体的，当第一中心距H为73mm以及第二中心距G为73mm时，第三夹角δ大于等于0°且小于等于20°，第四夹角γ大于等于0°且小于等于20°。在本实施方式中，当第一平衡轴142和曲轴131的中心距为73mm，第二平衡轴144和曲轴131的中心距为73mm时，第五投影线和第四投影线所形成的夹角大于等于0°且小于等于20°，第六投影线和第四投影线所形成的夹角大于等于0°且小于等于20°。通过上述设置，可以使发动机100的整机振动频率和振幅降至较小，能使发动机100的整体设计外型较小、重量较轻，从而使发动机100的结构更加紧凑，实现发动机100的轻量化，提高发动机100的空间利用率，使发动机100运行的平稳性更好，进而提高发动机100的使用寿命。
具体的，当第一中心距H为73mm以及第二中心距G为73mm时，第三夹角δ为20°，第四夹角γ为20°。在本实施方式中，当第一平衡轴142和曲轴131的中心距为73mm，第二平衡轴144和曲轴131的中心距为73mm时，第五投影线和第四投影线所形成的夹角为20°，第六投影线和第四投影线所形成的夹角为20°。通过上述设置，可以使发动机100的整机振动频率和振幅降至最小，能使发动机100的整体设计外型较小、重量较轻，从而使发动机100的结构更加紧凑，实现发动机100的轻量化，提高发动机100的空间利用率，使发动机100运行的平稳性更好，进而提高发动机100的使用寿命。
此外，当曲轴131旋转时，活塞111和连杆132的惯性质量使曲轴131失去平衡，产生很大的不平衡力。为了消除这种不平衡力，需要在曲轴131上安装平衡块1311，平衡块1311的质量大小、形状和安装位置需进行合理 设计，以克服曲轴131旋转中产生的离心力。平衡轴上设有偏心重块141，利用偏心重块141所产生的反向振动力，可以使发动机100获得良好的平衡效果，从而降低发动机100振动。
如图23和图24所示，作为一种实现方式，曲轴箱4还设有油泵总成17，油泵总成17连接在平衡机构14上，平衡机构14包括第一平衡轴142、第一轴齿轮143、第二平衡轴144、第二轴齿轮145和主动轴齿轮146。第一轴齿轮143设置在第一平衡轴142上，第二轴齿轮145设置在第二平衡轴144上，主动轴齿轮146设置在曲轴131上，主动轴齿轮146分别与第一轴齿轮143、第二轴齿轮145啮合。第一平衡轴142、第二平衡轴144和曲轴131互相平行，第一轴齿轮143设在第一平衡轴142的第一端1421，第二轴齿轮145设在第二平衡轴144的一端，主动轴齿轮146设在曲轴131的一端；油泵总成17连接在第一平衡轴142的第二端1422，曲轴箱4靠近第二端1422处设有平衡轴瓦147，平衡轴瓦147设在固定轴孔401中，第二端1422设在平衡轴瓦147中。具体的，第二端1422端面上设有扁方连接孔1423，油泵总成17靠近第二端1422的端面设有连接件171，扁方连接孔1423与连接件171通过间隙配合连接，从而实现油泵总成17与第一平衡轴142的连接，并使第一平衡轴142驱动油泵总成17。
在本实施方式中，油泵总成17用于将平衡机构14飞溅的润滑油注回曲轴箱4内部。但在润滑油注回曲轴箱4内部的过程中，由于油压增大，润滑油注回曲轴箱4的速度变慢，当油泵总成17中润滑油达到一定量时，容易造成发动机100的渗水渗油问题。在原有的设计中，通过打孔的形式连通油泵总成与曲轴箱内部。但在实际过程中，由于曲轴箱内部油压过大的原因，通过打孔的形式无法实现曲轴箱中的油压平衡，因而仍旧会造成发动机的渗水渗油问题，不能保证发动机密封性。为防止油泵总成17因泄油压力过大而造成密封不良，本申请在曲轴箱4上设置泄油槽18。泄油槽18可以通过铸造等方式与曲轴箱4一体成型，便于泄油槽18的加工和提高生产效率。具体的，当平衡机构14飞溅的润滑油进入油泵总成17时，油泵总成17将润滑油注入泄油槽18中，由于泄油槽18存在一定的间隙，即泄油槽18为一个泄油通道，润滑油将处于泄油槽18的其中一部分空间中。此时，当油压增大时，过大的油压会进入泄油槽18的另外部分空间中，不会影响润滑油通过泄油槽18输 送至曲轴箱4内部，从而实现曲轴箱4中的油压平衡，有效解决因曲轴箱4油压过大而造成的渗水渗油问题。
如图23和图24所示，具体的，泄油槽18包括第一通道181和第二通道182。作为一种实现方式，第一通道181和第二通道182可以互相重合且连通，第一通道181即油压进入的部分空间，第二通道182即润滑油进入的另一部分空间。当平衡机构14飞溅的润滑油进入油泵总成17时，油泵总成17将润滑油注入泄油槽18中，由于泄油槽18存在一定的间隙，即泄油槽18为一个泄油通道，润滑油将处于第二通道182中，此时，当油压增大时，过大的油压会进入第一通道181中，从而不会影响润滑油通过泄油槽18输送至曲轴箱4内部，进而实现曲轴箱4中的油压平衡，有效解决因曲轴箱4压力过大而造成的渗水渗油问题。可以理解的，第一通道181用于平衡曲轴箱4中的油压，有效解决因曲轴箱4压力过大而造成的渗水渗油问题。第二通道182用于形成润滑油的通道，使润滑油可以通过泄油槽18从油泵总成17输送至曲轴箱4。此外，第一通道181和第二通道182互相重合且连通，可以便于泄油槽18与曲轴箱4一体成型，便于泄油槽18的加工和提高生产效率。
作为一种实现方式，第一通道181和第二通道182可以互相独立设置且不连通，第一通道181即油压进入的部分空间，第二通道182即润滑油进入的另一部分空间。当平衡机构14飞溅的润滑油进入油泵总成17时，油泵总成17将润滑油注入泄油槽18中，由于泄油槽18存在一定的间隙，即泄油槽18为一个泄油通道，润滑油将处于第二通道182中，此时，当油压增大时，过大的油压会进入第一通道181中，从而不会影响润滑油通过泄油槽18输送至曲轴箱4内部，进而实现曲轴箱4中的油压平衡，有效解决因曲轴箱4压力过大而造成的渗水渗油问题。可以理解的，第一通道181用于平衡曲轴箱4中的油压，有效解决因曲轴箱4压力过大而造成的渗水渗油问题。第二通道182用于形成润滑油的通道，使润滑油可以通过泄油槽18从油泵总成17输送至曲轴箱4。此外，第一通道181和第二通道182可以互相独立设置且不连通，也可以便于泄油槽18与曲轴箱4一体成型，便于泄油槽18的加工和提高生产效率。
作为一种实现方式，泄油槽18至少部分设置在第三容纳空间2013中，泄油槽18设置在曲轴箱4和油泵总成17之间，泄油槽18连通曲轴箱4和油泵总成17。具体的，第一通道181至少部分设置在第三容纳空间2013中， 第一通道181设置在曲轴箱4和油泵总成17之间，第一通道181连通曲轴箱4和油泵总成17。第二通道182至少部分设置在第三容纳空间2013中，第二通道182设置在曲轴箱4和油泵总成17之间，第二通道182连通曲轴箱4和油泵总成17。第一通道181和第二通道182基本平行设置。通过上述设置，可以实现曲轴箱4内部的油压平衡，在油压过大的情况下，使润滑油顺利输送至曲轴箱4中，有效解决因曲轴箱4压力过大而造成的渗水渗油问题。
如图24所示，在本实施方式中，油泵总成17依次包括油泵轴172、油泵体173和油泵盖174，油泵轴172、油泵体173和油泵盖174依次通过螺栓等固定方式进行固定连接。油泵体173形成油泵体173容纳空间，油泵轴172至少部分设置在油泵体173容纳空间中，油泵盖174形成油泵盖174容纳空间，油泵叶轮175至少部分设置在油泵盖174容纳空间中。油泵轴172的一端设有连接件171，用于连接油泵轴172与第一平衡轴142，从而使第一平衡轴142驱动油泵总成17。油泵轴172的另一端设有油泵叶轮175，油泵轴172与油泵叶轮175之间通过螺纹连接，油泵轴172通过轴承176与曲轴箱4转动连接。轴承176设在靠近连接件171的一端，轴承176与第二端1422的端面之间设置有泄油槽18。油泵叶轮175与轴承176之间设有油封件177，油封件177用于将润滑油密封，防止润滑油泄露。油封件177和油泵叶轮175之间设有水封件178，水封件178用于防止外界的水等液体进入发动机100，避免由于发动机100进水导致的故障。其中，油泵轴172实现油泵总成17与第一平衡轴142之间的连接，油泵体173实现油泵总成17与曲轴箱4之间的连接，从而实现油泵总成17的固定和转动。
具体的，泄油槽18连通油泵体173和曲轴箱4内部，便于油泵总成17使润滑油在油泵体173和曲轴箱4内部循环，从而使润滑油在发动机100中进行循环。水封件178贴近油泵叶轮175设置，便于在油泵叶轮175转动时，水封件178可以更好地进行密封。油封件177贴近轴承176，既可以保证润滑油对轴承176进行润滑，从而减少油泵轴172和轴承176之间的摩擦，又可以将润滑油密封在发动机100内部，从而便于润滑油在发动机100中进行循环。轴承176的数量至少为一个，从而保证油泵轴172和曲轴箱4之间的转动连接。
应当理解的是，对于本领域普通技术人员来说，可以根据上述说明加以改进或变换，而所有这些改进和变换都应属于本申请所附权利要求的保护范围。

Claims (81)

  1. 一种发动机，包括：
    气缸盖，形成有第一容纳空间；
    进排气机构，所述进排气机构至少部分设置在所述第一容纳空间中，所述进排气机构包括进气机构和排气机构；
    凸轮机构，所述凸轮机构至少部分设置在所述第一容纳空间中，用于控制所述进排气机构；
    曲轴箱，所述曲轴箱形成有第二容纳空间；
    曲轴连杆机构，所述曲轴连杆机构至少部分设置在所述第二容纳空间中；
    平衡机构，所述平衡机构至少部分设置在所述第二容纳空间中并连接所述曲轴连杆机构，所述平衡机构包括第一平衡轴和第二平衡轴；
    其中，所述发动机还包括：
    节气门机构，所述节气门机构包括：
    主通道，所述主通道连接所述进气机构，用于控制空气输入至所述进气机构；
    节气通道，所述节气通道与所述主通道一体成型并至少部分连通所述主通道；
    所述气缸盖包括贯穿自身的贯穿线；所述发动机还包括气缸体，所述气缸体包括气缸孔，所述气缸体基本沿第一直线延伸；
    所述进气机构基本沿第二直线方向延伸；在一个垂直于所述第一直线的投影平面内，所述第二直线沿所述第一直线方向在所述投影平面上的投影为第一投影线；
    所述排气机构基本沿第三直线方向延伸；所述第三直线沿所述第一直线方向在所述投影平面上的投影为第二投影线；
    所述贯穿线沿所述第一直线方向在所述投影平面上的投影为第三投影线；
    当所述气缸孔的直径大于等于70mm且小于等于74mm时，所述第一投影线与所述第三投影线的夹角大于等于11°且小于等于15°，所述第二投影线与所述第三投影线的夹角大于等于11°且小于等于15°。
  2. 根据权利要求1所述的发动机，其中，所述节气通道包括：
    进气孔，用于控制空气输入至所述节气门机构；
    出气孔，用于控制空气输入至所述进气机构；
    节气气道，所述节气气道连通所述进气孔和所述出气孔；
    出气口，所述出气口设置在所述节气气道上，所述出气口设置在所述节气气道和所述出气孔之间并连通所述节气气道和所述出气孔，所述出气口使空气通过所述节气气道输入至所述出气孔。
  3. 根据权利要求2所述的发动机，其中，所述进气孔、所述出气孔、所述节气气道、所述出气口均与所述主通道一体成型。
  4. 根据权利要求2所述的发动机，其中，所述进气孔连通所述主通道的第一段，用于控制空气输入至所述节气气道中；
    所述出气孔连通所述主通道的第二段，用于控制空气输入至所述进气机构。
  5. 根据权利要求4所述的发动机，其中，所述主通道包括：
    通道一端，所述通道一端的一端连通所述进气机构，所述通道一端的另一端连通所述出气孔，所述通道一端用于控制所述出气孔的空气输入至所述进气机构；
    通道二端，所述通道二端的一端连通所述进气孔，所述通道二端的另一端连通外界，所述通道二端用于控制空气输入至所述进气孔中。
  6. 根据权利要求2所述的发动机，其中，所述节气气道与所述主通道基本平行设置。
  7. 根据权利要求1所述的发动机，其中，所述发动机至少包括第一状态和第二状态；
    当所述发动机处于第一状态，所述发动机的进气由所述节气通道控制；
    当所述发动机处于第二状态，所述发动机的进气由所述主通道控制。
  8. 根据权利要求1所述的发动机，其中，所述节气门机构还包括：
    气阀，用于控制所述节气通道的开闭程度；
    阀体电机，所述阀体电机连接所述气阀，用于控制所述节气通道的开闭程度。
  9. 根据权利要求8所述的发动机，其中，所述气阀包括：
    阀头，用于控制所述节气通道的开闭程度；
    阀身，所述阀身连接所述阀体电机，用于控制所述阀头。
  10. 根据权利要求1所述的发动机，其中，所述节气门机构还包括：
    通道阀，所述通道阀至少部分设置在所述主通道中，用于控制所述主通道的开闭；
    所述通道阀包括：
    阀轴，所述阀轴两端贯穿所述主通道；
    油门拉线，所述油门拉线设置在所述阀轴的一端，用于控制所述阀轴转动；
    阻气片，所述阻气片转动连接在所述阀轴上且设置在所述主通道中，用于控制所述主通道的开闭。
  11. 根据权利要求1所述的发动机，其中，
    所述发动机还包括：
    油泵总成，所述油泵总成连接所述平衡机构和所述曲轴箱，所述油泵总成至少部分设置在所述第二容纳空间中；
    泄油槽，所述泄油槽至少部分设置在所述第二容纳空间中且包括第一通道和第二通道，所述泄油槽设置在所述曲轴箱和所述油泵总成之间并连通所述曲轴箱和所述油泵总成；
    所述第一通道设置在所述曲轴箱和所述油泵总成之间并连通所述曲轴箱和所述油泵总成，用于平衡所述曲轴箱内部的油压；
    所述第二通道设置在所述曲轴箱和所述油泵总成之间并连通所述曲轴箱和所述油泵总成，用于形成润滑油的通道。
  12. 根据权利要求11所述的发动机，其中，所述第一通道和所述第二通道互相重合且连通。
  13. 根据权利要求11所述的发动机，其中，所述第一通道和所述第二通道互相独立设置且不连通。
  14. 根据权利要求11所述的发动机，其中，所述第一通道和所述第二通道基本平行设置。
  15. 根据权利要求11所述的发动机，其中，所述泄油槽和所述曲轴箱一体成型。
  16. 根据权利要求11所述的发动机，其中，所述油泵总成和所述第一平衡轴连接，所述第一平衡轴用于驱动所述油泵总成。
  17. 根据权利要求16所述的发动机，其中，所述第一平衡轴上设置有扁方连接孔，所述油泵总成设置有连接件；所述第一平衡轴和所述油泵总成通过所述扁方连接孔和所述连接件连接。
  18. 根据权利要求17所述的发动机，其中，所述油泵总成包括：
    油泵轴，所述油泵轴一端设置有所述连接件，用于连接所述第一平衡轴；
    油泵体，所述油泵体与所述曲轴箱转动连接，所述油泵轴至少部分设置在所述油泵体中。
  19. 根据权利要求18所述的发动机，其中，所述油泵体与所述曲轴箱通过轴承转动连接。
  20. 根据权利要求18所述的发动机，其中，所述扁方连接孔和所述连接件通过间隙配合连接。
  21. 根据权利要求1所述的发动机，其中，所述凸轮机构包括：
    凸轮轴，所述凸轮轴至少部分设置在所述第一容纳空间中；
    轴座，所述轴座至少部分设置在所述第一容纳空间中，用于支撑并润滑所述凸轮轴；
    所述轴座包括：
    通油孔，所述通油孔贯穿所述轴座并连通至所述凸轮轴；
    集油结构，所述集油结构包括集油槽和集油挡板，所述集油挡板半包围所述集油槽，所述通油孔至少部分设置在所述集油槽中。
  22. 根据权利要求21所述的发动机，其中，所述集油挡板包括第一挡板和第二挡板，所述第一挡板和所述第二挡板连接并包围至少部分所述集油槽。
  23. 根据权利要求22所述的发动机，其中，所述轴座上设置有轴座安装孔和第一安装孔；所述第一挡板的一端连接所述轴座安装孔，所述第一挡板的另一端连接所述第二挡板的一端，所述第二挡板的另一端连接所述第一安装孔。
  24. 根据权利要求22所述的发动机，其中，所述第二挡板包括第一表面，所述集油槽靠近所述第二挡板处设置有第二表面，所述第一表面和所述第二表面基本处于同一平面。
  25. 根据权利要求22所述的发动机，其中，所述第一挡板包括第三表面，所述集油槽靠近所述第一挡板处设置有第四表面，所述第三表面与所述通油孔的距离比所述第四表面与所述通油孔的距离远。
  26. 根据权利要求22所述的发动机，其中，所述集油槽包括基本平行的第一槽沿和第二槽沿，所述第一槽沿靠近所述第二挡板，所述第二槽沿远离所述第二挡板；沿所述贯穿线的延伸方向，所述第一槽沿的高度大于所述第二槽沿的高度。
  27. 根据权利要求21所述的发动机，其中，所述轴座基本沿第四直线方向延伸；所述第四直线和所述第一直线平行；所述轴座包括轴槽，所述凸轮轴上设置有环形凸起；沿所述第四直线方向上，所述轴槽用于对所述环形凸起限位，以对所述凸轮轴限位。
  28. 根据权利要求27所述的发动机，其中，所述通油孔连通所述轴槽。
  29. 根据权利要求21所述的发动机，其中，所述通油孔、所述集油槽和所述集油挡板均设置在所述凸轮轴轴线的一侧；
    当所述凸轮轴绕第一方向转动时，所述通油孔、所述集油槽和所述集油挡板均设置在偏向于与所述凸轮轴转动的方向相反的一侧。
  30. 根据权利要求21所述的发动机，其中，所述通油孔、所述集油槽和所述集油挡板均设置在所述凸轮轴轴线的一侧；
    当所述凸轮轴绕第二方向转动时，所述通油孔、所述集油槽和所述集油挡板均设置在偏向于与所述凸轮轴的转动方向相反的一侧。
  31. 根据权利要求1所述的发动机，其中，所述发动机还包括：
    气缸盖罩，所述气缸盖罩至少部分连接所述气缸盖，用于密封所述发动机；
    点火机构，所述点火机构至少部分设置在所述第一容纳空间中，用于将可燃混合气点燃；
    点火孔，所述点火孔至少部分设置在所述第一容纳空间中且至少部分设置在所述气缸盖罩中；
    所述点火机构至少部分设在所述点火孔中；
    所述点火孔与所述气缸盖罩之间设有通气孔，所述通气孔连通所述点火孔并贯穿所述气缸盖罩，所述通气孔还通过所述气缸盖罩连通至所述气缸盖罩的外表面。
  32. 根据权利要求31所述的发动机，其中，所述点火孔包括第一连通孔和第二连通孔，所述第一连通孔连通所述气缸盖罩，所述第二连通孔连通所述气缸体。
  33. 根据权利要求32所述的发动机，其中，所述通气孔的一端连通所述第一连通孔，所述通气孔的另一端连通所述气缸盖罩的外表面。
  34. 根据权利要求33所述的发动机，其中，所述通气孔包括互相连通的第三连通孔和第四连通孔，所述第三连通孔连通所述点火孔，所述第四连通孔连通所述气缸盖罩的外表面。
  35. 根据权利要求31所述的发动机，其中，所述点火孔包括第一点火孔和第二点火孔；所述通气孔包括第一通气孔和第二通气孔；所述第一通气孔设置在所述第一点火孔和所述气缸盖罩之间；所述第二通气孔设置在所述第二点火孔和所述气缸盖罩之间。
  36. 根据权利要求35所述的发动机，其中，所述第一通气孔连通所述第一点火孔和所述气缸盖罩的外表面；所述第二通气孔连通所述第二点火孔和所述气缸盖罩的外表面。
  37. 根据权利要求32所述的发动机，其中，所述发动机还包括冷却机构；所述冷却机构至少部分设置在所述容纳空间中且至少部分围绕所述点火机构，所述冷却机构用于冷却所述点火机构。
  38. 根据权利要求37所述的发动机，其中，所述冷却机构至少部分延伸至所述第二连通孔处。
  39. 根据权利要求1所述的发动机，其中，所述第一投影线与所述第三投影线的夹角为第一夹角；所述第二投影线与所述第三投影线的夹角为第二夹角；所述第一夹角与所述第二夹角的角度基本一致。
  40. 根据权利要求1所述的发动机，其中，当所述气缸孔的直径大于等于70mm且小于等于74mm时，所述第一投影线与所述第三投影线的夹角为13°，所述第二投影线与所述第三投影线的夹角为13°。
  41. 根据权利要求1所述的发动机，其中，当所述气缸孔的直径为72mm时，所述第一投影线与所述第三投影线的夹角大于等于11°且小于等于15°，所述第二投影线与所述第三投影线的夹角大于等于11°且小于等于15°。
  42. 根据权利要求1所述的发动机，其中，当所述气缸孔的直径为72mm时，所述第一投影线与所述第三投影线的夹角为13°，所述第二投影线与所述第三投影线的夹角为13°。
  43. 一种发动机，包括：
    气缸盖，所述气缸盖形成有第一容纳空间；
    进排气机构，所述进排气机构至少部分设置在所述第一容纳空间中，所述进排气机构包括进气机构和排气机构，所述进气机构用于所述发动机的进气，所述排气机构用于所述发动机的排气；
    凸轮机构，所述凸轮机构至少部分设置在所述第一容纳空间中，用于控制所述进排气机构；
    其中，所述发动机还包括：
    节气门机构，所述节气门机构包括：
    主通道，所述主通道连接所述进气机构，用于控制空气输入至所述进气机构；
    节气通道，所述节气通道与所述主通道一体成型并至少部分连通所述主通道。
  44. 根据权利要求43所述的发动机，其中，所述节气通道包括：
    进气孔，用于控制空气输入至所述节气门机构；
    出气孔，用于控制空气输入至所述进气机构；
    节气气道，所述节气气道连通所述进气孔和所述出气孔；
    出气口，所述出气口设置在所述节气气道上，所述出气口设置在所述节气气道和所述出气孔之间并连通所述节气气道和所述出气孔，所述出气口使空气通过所述节气气道输入至所述出气孔。
  45. 根据权利要求44所述的发动机，其中，所述进气孔、所述出气孔、所述节气气道、所述出气口均与所述主通道一体成型。
  46. 根据权利要求44所述的发动机，其中，所述进气孔连通所述主通道的第一段，用于控制空气输入至所述节气气道中；
    所述出气孔连通所述主通道的第二段，用于控制空气输入至所述进气机构。
  47. 根据权利要求46所述的发动机，其中，所述主通道包括：
    通道一端，所述通道一端的一端连通所述进气机构，所述通道一端的另一端连通所述出气孔，所述通道一端用于控制所述出气孔的空气输入至所述进气机构；
    通道二端，所述通道二端的一端连通所述进气孔，所述通道二端的另一端连通外界，所述通道二端用于控制空气输入至所述进气孔中。
  48. 根据权利要求44所述的发动机，其中，所述节气气道与所述主通道基本平行设置。
  49. 根据权利要求43所述的发动机，其中，所述发动机至少包括第一状态和第二状态；
    当所述发动机处于第一状态，所述发动机的进气由所述节气通道控制；
    当所述发动机处于第二状态，所述发动机的进气由所述主通道控制。
  50. 根据权利要求43所述的发动机，其中，所述节气门机构还包括：
    气阀，用于控制所述节气通道的开闭程度；
    阀体电机，所述阀体电机连接所述气阀，用于控制所述节气通道的开闭程度。
  51. 根据权利要求50所述的发动机，其中，所述气阀包括：
    阀头，用于控制所述节气通道的开闭程度；
    阀身，所述阀身连接所述阀体电机，用于控制所述阀头。
  52. 根据权利要求43所述的发动机，其中，所述节气门机构还包括：
    通道阀，所述通道阀至少部分设置在所述主通道中，用于控制所述主通道的开闭；
    所述通道阀包括：
    阀轴，所述阀轴两端贯穿所述主通道；
    油门拉线，所述油门拉线设置在所述阀轴的一端，用于控制所述阀轴转动；
    阻气片，所述阻气片转动连接在所述阀轴上且设置在所述主通道中，用于控制所述主通道的开闭。
  53. 根据权利要求43所述的发动机，其中，所述发动机还包括气缸体、曲轴箱和曲轴连杆机构；所述气缸体基本沿第一直线延伸；所述曲轴箱形成有第二容纳空间，所述曲轴连杆机构至少部分设置在所述第二容纳空间中；
    在一个垂直所述第一直线的投影平面内，所述曲轴箱包括与所述投影平面垂直的第一水平面；所述曲轴连杆机构包括曲轴；
    所述发动机还包括：平衡机构，所述平衡机构至少部分设置在所述容纳空间中并连接所述曲轴；
    所述平衡机构包括第一平衡轴和第二平衡轴；
    所述第一平衡轴与所述曲轴的中心距大于等于72mm且小于等于76mm，所述第二平衡轴与所述曲轴的中心距大于等于72mm且小于等于76mm；
    沿所述第一直线方向，所述第一平衡轴的轴心在所述投影平面的投影为第一投影点，所述第二平衡轴的轴心在所述投影平面的投影为第二投影点，所述曲轴的轴心在所述投影平面的投影为第三投影点，所述第一水平面在所述投影平面的投影为第四投影线，所述第一投影点和所述第三投影点的连线为第五投影线，所述第二投影点和所述第三投影点的连线为第六投影线；
    所述第五投影线和所述第四投影线的夹角大于等于0°且小于等于20°，所述第六投影线和所述第四投影线的夹角大于等于0°且小于等于20°。
  54. 根据权利要求53所述的发动机，其中，
    所述第一平衡轴与所述曲轴的中心距大于等于72mm且小于等于74mm；
    所述第二平衡轴与所述曲轴的中心距大于等于72mm且小于等于74mm；
    所述第五投影线和所述第四投影线的夹角大于等于0°且小于等于20°；
    所述第六投影线和所述第四投影线的夹角大于等于0°且小于等于20°。
  55. 根据权利要求53所述的发动机，其中，
    当所述第一平衡轴与所述曲轴的中心距大于等于72mm且小于等于74mm，且所述第二平衡轴与所述曲轴的中心距大于等于72mm且小于等于74mm时；
    所述第五投影线和所述第四投影线的夹角大于等于10°且小于等于20°；
    所述第六投影线和所述第四投影线的夹角大于等于10°且小于等于20°。
  56. 根据权利要求53所述的发动机，其中，
    当所述第一平衡轴与所述曲轴的中心距大于等于72mm且小于等于76mm，且所述第二平衡轴与所述曲轴的中心距大于等于72mm且小于等于76mm；
    所述第五投影线和所述第四投影线的夹角大于等于10°且小于等于20°；
    所述第六投影线和所述第四投影线的夹角大于等于10°且小于等于20°。
  57. 一种发动机，包括：
    气缸盖，所述气缸盖形成有第一容纳空间；
    进排气机构，所述进排气机构至少部分设置在所述第一容纳空间中，所述进排气机构包括进气机构和排气机构，所述进气机构用于所述发动机的进气，所述排气机构用于所述发动机的排气；
    凸轮机构，所述凸轮机构至少部分设置在所述第一容纳空间中，用于控制所述进排气机构；
    曲轴箱，所述曲轴箱形成有第二容纳空间；
    曲轴连杆机构，所述曲轴连杆机构至少部分设置在所述第二容纳空间中；
    平衡机构，所述平衡机构至少部分设置在所述第二容纳空间中并连接所述曲轴连杆机构，所述平衡机构包括第一平衡轴和第二平衡轴；
    其中，所述发动机还包括：
    节气门机构，所述节气门机构包括：
    主通道，所述主通道连接所述进气机构，用于控制空气输入至所述进气机构；
    节气通道，所述节气通道与所述主通道一体成型并至少部分连通所述主通道；
    油泵总成，所述油泵总成连接所述平衡机构和所述曲轴箱，所述油泵总成至少部分设置在所述第二容纳空间中；
    泄油槽，所述泄油槽至少部分设置在所述第二容纳空间中且包括第一通道和第二通道，所述泄油槽设置在所述曲轴箱和所述油泵总成之间并连通所述曲轴箱和所述油泵总成；
    所述第一通道设置在所述曲轴箱和所述油泵总成之间并连通所述曲轴箱和所述油泵总成，用于平衡所述曲轴箱内部的油压；
    所述第二通道设置在所述曲轴箱和所述油泵总成之间并连通所述曲轴箱和所述油泵总成，用于形成润滑油的通道。
  58. 根据权利要求57所述的发动机，其中，所述节气通道包括：
    进气孔，用于控制空气输入至所述节气门机构；
    出气孔，用于控制空气输入至所述进气机构；
    节气气道，所述节气气道连通所述进气孔和所述出气孔；
    出气口，所述出气口设置在所述节气气道上，所述出气口设置在所述节气气道和所述出气孔之间并连通所述节气气道和所述出气孔，所述出气口使空气通过所述节气气道输入至所述出气孔。
  59. 根据权利要求58所述的发动机，其中，所述进气孔、所述出气孔、所述节气气道、所述出气口均与所述主通道一体成型。
  60. 根据权利要求58所述的发动机，其中，所述进气孔连通所述主通道的第一段，用于控制空气输入至所述节气气道中；
    所述出气孔连通所述主通道的第二段，用于控制空气输入至所述进气机构。
  61. 根据权利要求60所述的发动机，其中，所述主通道包括：
    通道一端，所述通道一端的一端连通所述进气机构，所述通道一端的另一端连通所述出气孔，所述通道一端用于控制所述出气孔的空气输入至所述进气机构；
    通道二端，所述通道二端的一端连通所述进气孔，所述通道二端的另一端连通外界，所述通道二端用于控制空气输入至所述进气孔中。
  62. 根据权利要求58所述的发动机，其中，所述节气气道与所述主通道基本平行设置。
  63. 根据权利要求57所述的发动机，其中，所述发动机至少包括第一状态和第二状态；
    当所述发动机处于第一状态，所述发动机的进气由所述节气通道控制；
    当所述发动机处于第二状态，所述发动机的进气由所述主通道控制。
  64. 根据权利要求57所述的发动机，其中，所述节气门机构还包括：
    气阀，用于控制所述节气通道的开闭程度；
    阀体电机，所述阀体电机连接所述气阀，用于控制所述节气通道的开闭程度。
  65. 根据权利要求64所述的发动机，其中，所述气阀包括：
    阀头，用于控制所述节气通道的开闭程度；
    阀身，所述阀身连接所述阀体电机，用于控制所述阀头。
  66. 根据权利要求57所述的发动机，其中，所述节气门机构还包括：
    通道阀，所述通道阀至少部分设置在所述主通道中，用于控制所述主通道的开闭；
    所述通道阀包括：
    阀轴，所述阀轴两端贯穿所述主通道；
    油门拉线，所述油门拉线设置在所述阀轴的一端，用于控制所述阀轴转动；
    阻气片，所述阻气片转动连接在所述阀轴上且设置在所述主通道中，用于控制所述主通道的开闭。
  67. 根据权利要求57所述的发动机，其中，所述第一通道和所述第二通道互相重合且连通。
  68. 根据权利要求57所述的发动机，其中，所述第一通道和所述第二通道互相独立设置且不连通。
  69. 根据权利要求57所述的发动机，其中，所述第一通道和所述第二通道基本平行设置。
  70. 根据权利要求57所述的发动机，其中，所述泄油槽和所述曲轴箱一体成型。
  71. 根据权利要求57所述的发动机，其中，所述油泵总成和所述第一平衡轴连接，所述第一平衡轴用于驱动所述油泵总成。
  72. 根据权利要求71所述的发动机，其中，所述第一平衡轴上设置有扁方连接孔，所述油泵总成设置有连接件；所述第一平衡轴和所述油泵总成通过所述扁方连接孔和所述连接件连接。
  73. 根据权利要求72所述的发动机，其中，所述油泵总成包括：
    油泵轴，所述油泵轴一端设置有所述连接件，用于连接所述第一平衡轴；
    油泵体，所述油泵体与所述曲轴箱转动连接，所述油泵轴至少部分设置在所述油泵体中。
  74. 根据权利要求73所述的发动机，其中，所述油泵体与所述曲轴箱通过轴承转动连接。
  75. 根据权利要求73所述的发动机，其中，所述扁方连接孔和所述连接件通过间隙配合连接。
  76. 根据权利要求57所述的发动机，其中，所述发动机还包括：
    气缸体，所述气缸体连接所述气缸盖且包括气缸孔；
    所述进气机构包括第一进气机构和第二进气机构；
    所述排气机构包括第一排气机构和第二排气机构；
    当所述气缸孔的直径大于等于70mm且小于等于74mm时，
    所述第一进气机构与所述第二进气机构的中心距大于等于30.2mm且小于等于34.2mm；
    所述第一排气机构与所述第二排气机构的中心距大于等于27.1mm且小于等于31.1mm。
  77. 根据权利要求76所述的发动机，其中，当所述气缸孔的直径大于等于71mm且小于等于73mm时，所述第一进气机构与所述第二进气机构的中心距大于等于31.2mm且小于等于33.2mm；所述第一排气机构与所述第二排气机构的中心距大于等于28.1mm且小于等于30.1mm。
  78. 根据权利要求76所述的发动机，其中，当发动机为双缸发动机时，所述气缸孔包括第一气缸孔和第二气缸孔；
    当所述气缸孔的直径大于等于70mm且小于等于74mm时，所述第一气缸孔和所述第二气缸孔的缸心距大于等于76mm且小于等于82mm。
  79. 根据权利要求78所述的发动机，其中，当所述气缸孔的直径大于等于70mm且小于等于74mm时，所述第一气缸孔和所述第二气缸孔的缸心距大于等于78mm且小于等于80mm。
  80. 根据权利要求78所述的发动机，其中，当所述气缸孔的直径大于等于71mm且小于等于73mm时，所述第一气缸孔和所述第二气缸孔的缸心距大于等于76mm且小于等于82mm。
  81. 根据权利要求78所述的发动机，其中，当所述气缸孔的直径大于等于71mm且小于等于73mm时，所述第一气缸孔和所述第二气缸孔的缸心距大于等于78mm且小于等于80mm。
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