CN103306727B

CN103306727B - For the gear-box of V-type multi-cylinder aerodynamic engine

Info

Publication number: CN103306727B
Application number: CN201210063473.7A
Authority: CN
Inventors: 周登荣; 周剑
Original assignee: Individual
Current assignee: Individual
Priority date: 2012-03-13
Filing date: 2012-03-13
Publication date: 2015-10-28
Anticipated expiration: 2032-03-13
Also published as: CN103306727A

Abstract

The present invention relates to a kind of gear-box for V-type multi-cylinder aerodynamic engine, described air-powered motor comprises: engine body (1), controller (6) and high pressure gas holder group.Described in this, front gear box comprises: polygonal lid (1300), crankshaft gear (1030), right exhaust cam shaft carrier gear (1040), left bank gas cam idle gear (1310), admission cam shaft carrier gear (1050), right exhaust cam shaftgear (1060) and left bank gas camshaft gear wheel (1230); Wherein, described left bank gas camshaft gear wheel (1230) and right exhaust cam shaftgear (1060) are located at the arranged on left and right sides of crankshaft gear (1030) respectively, crankshaft gear (1030) is fixedly connected with bent axle (1020) one end through polygonal lid (1300), to transmit the rotation from bent axle.

Description

For the gear-box of V-type multi-cylinder aerodynamic engine

Technical field

The present invention relates to a kind of device of motor, in particular to a kind of gear-box for V-type multi-cylinder aerodynamic engine.

Background technique

Motor is widely used in all trades and professions, in Modern Traffic means of transportation such as automobile, steamer etc., generally adopts the piston internal-combustion engine using fuel oil as power source.This employing fuel oil as the motor of power source on the one hand because oil inflame is insufficient, make in the gas of discharging containing a large amount of harmful matters and befouling environment, fuel oil on the other hand because using refines from oil and obtains, and the day by day in short supply of petroleum resources makes the development of fuel engine and utilization be subject to increasing restriction.Therefore new, clean, free of contamination alternative energy source is developed, or reduce fuel consume as much as possible, reduction discharge becomes urgent problem in development of engine, just in time meet this requirement using pressurized air as the air-powered motor of power source.

That study compressed-air power engine the earliest was the Designer Guy Negre of French MDI company, and he was proposed the pure aerodynamic Domestic bridge car of first item in 2002.About research visible FR2731472A1, US6311486B1, US20070101712A1 etc. of compressed air engine.

FR2731472A1 discloses a kind of motor can supplying two kinds of MODE of operation in fuel supply and pressurized air, adopt conventional fuel as gasoline or diesel oil on a highway, in low speed particularly urban district and suburbs, pressurized air (or other any on-contaminated pressurized gass) is injected firing chamber.Although this motor its part reduces fuel consumption, owing to still have employed fuel oil service pattern, emission problem still fails to solve.

In order to further pollution abatement, US6311486B1 discloses a kind of pure air-powered motor, such motor have employed three independently rooms: air-breathing-pressing chamber, expanded exhaust room and constant volume firing chamber, and air-breathing-pressing chamber is connected to constant volume firing chamber by valve, constant volume firing chamber is connected to expanded exhaust room by valve.One of problem of this motor is that the time that pressurized gas experiences from air-breathing-pressing chamber to expanded exhaust room is longer, the power source gas time obtaining driven plunger acting is longer, simultaneously, the pressurized gas of discharging from expanded exhaust room fail to be used, and which limits working efficiency and the single aeration continuous working period of this kind of motor.

The domestic research to compressed air engine is started late, current research belongs to theoretic discussion and conceptual phase more, all fail to solve compressed-air actuated discharge and (there is higher pressure usually, such as about 30bar) and the control of high pressure air and allocation problem, the commercialization process from compressed air engine is had got long long way to go.

The claimant of the application discloses a kind of air power engine assembly that can be used for transport facility, the turbo dynamo that this motor comprises gas holder, air distributor, engine body, clutch, clutch, automatic transmission, differential mechanism and is placed in exhaust chamber in its patent documentation CN101413403 A (its international application of the same clan is WO2010051668 A1).This motor utilizes compressed air to do work and does not use any fuel, so there is no toxic emission, achieves " zero-emission ", and reuses waste gas and generate electricity, and saves the energy, reduces cost.But this motor is based on traditional four stroke engine, and bent axle often rotates 720 degree, piston acting once.And can promote piston acting when entering in cylinder as the high-pressure air of power source, then discharge, namely the stroke of compressed air engine is actual is air inlet-expansion stroke and discharge stroke.Obviously, this four-stroke compressed air engine disclosed in patent documentation CN101413403 A wastes effective expansion stroke greatly, limits the efficiency of motor.And the tail gas of this motor fails to recycle well, need enough large gas holder deposit high-pressure air could work the sufficiently long time.

Based on the problem existing for patent application CN101413403 A, the claimant of the application discloses a kind of compressed air engine assembly with tail gas recycling loop in China's application of 201110331809.9, and this motor comprises cylinder, cylinder cap system, air inlet pipeline, gas exhaust piping, piston, connecting rod, bent axle, exhaust cam shaft, admission cam shaft, front gear box system and rear gear box.This motor utilizes compressed air to do work and does not use any fuel, so there is no toxic emission, achieves " zero-emission ", and recycles waste gas and do work, and saves the energy, reduces cost.But this motor is In-line multi-cylinder engine, only a controller valve is installed in each controller valve port in controller, when engine total length is certain, limits cylinder cylinder number, thus limit the gross output of motor.Obviously, this in-line multi-cylinder air-powered motor gross output disclosed in No. 201110331809.9 applications is not high, and the configuration of motor is still worth exploring.

The all not concrete mechanism proposing to be carried out by the bent axle power of air-powered motor transmitting and distributing of aforesaid Research Literature, especially for two-stroke V-type multi-cylinder aerodynamic engine.The present invention aims to provide a kind of gear-box for V-type multi-cylinder aerodynamic engine, to realize the interlock of the intake and exhaust cam axle of two-stroke V-type multi-cylinder aerodynamic engine, thus realizes air inlet and the exhaust of multicylinder engine.

Summary of the invention

According to a preferred embodiment of the invention, provide a kind of gear-box for V-type multi-cylinder aerodynamic engine, described air-powered motor: engine body, it comprises left and right two exhaust casings, bent axle, exhaust cam shaft, admission cam shaft; Controller, it comprises high-pressure common rail constant voltage pipe, controller unit and intake cam shaft housing, and this intake cam shaft housing holds described admission cam shaft, this admission cam shaft activated controllers; High pressure gas holder group, it is communicated with external aerator by pipeline; Described front gear box comprises: polygonal lid, crankshaft gear, right exhaust cam shaft carrier gear, left bank gas cam idle gear, admission cam shaft carrier gear, right exhaust cam shaftgear and left bank gas camshaft gear wheel; Wherein, described left bank gas camshaft gear wheel and right exhaust cam shaftgear are located at the arranged on left and right sides of crankshaft gear respectively, and crankshaft gear is fixedly connected with the bent axle one end through polygonal lid, to transmit the rotation from bent axle.

Preferably, the below of described crankshaft gear is provided with transmission gear of engine oil pump, rotates to drive oil pump.

Preferably, above described crankshaft gear, be disposed with described left bank gas camshaft gear wheel, described left bank gas cam idle gear, described admission cam shaft carrier gear, described right exhaust cam shaft carrier gear and described right exhaust cam shaftgear from left to right; Described left bank gas cam idle gear and described right exhaust cam shaft carrier gear are separately positioned on the arranged on left and right sides of described crankshaft gear and engage with described crankshaft gear respectively.

Preferably, outside the left side of described left bank gas cam idle gear, be provided with described left bank gas camshaft gear wheel engageablely, the line of described crankshaft gear, described left bank gas cam idle gear and described left bank gas camshaft gear wheel is the first straight line, this first straight line and horizontal plane oblique.

Preferably, outside the right side of described right exhaust cam shaft carrier gear, be provided with described right exhaust cam shaftgear engageablely; The line of the respective center of rotation of described crankshaft gear, described right exhaust cam shaft carrier gear and described right exhaust cam shaftgear is the second straight line, this second straight line and horizontal plane oblique.

Preferably, directly over described crankshaft gear, be provided with described admission cam shaft carrier gear and described intake cam shaftgear; Described admission cam shaft carrier gear is located between described left bank gas cam idle gear and described right exhaust cam shaft carrier gear, and simultaneously with these two carrier gear outer gearings, and wherein, described admission cam shaft carrier gear does not directly engage with described crankshaft gear.

More preferably, the line of the respective center of rotation of described crankshaft gear, described admission cam shaft carrier gear and described intake cam shaftgear is the 3rd straight line, 3rd straight line substantially with horizontal plane, and described first straight line and described second straight line are distributed in the 3rd straight line both sides substantially symmetrically.

Further, described left bank gas camshaft gear wheel is directly fixedly connected on described left exhaust cam shaft, described right exhaust cam shaft direct geared is fixedly connected on described right exhaust cam shaft, described admission cam shaft direct geared is fixedly connected on described admission cam shaft, and it is driven jointly by described left bank gas cam idle gear, described right exhaust cam shaft carrier gear and described admission cam shaft carrier gear three.

In preferably implementing, equal and opposite in direction, the number of teeth of described crankshaft gear, described left bank gas camshaft gear wheel and described right exhaust cam shaftgear are identical; Equal and opposite in direction, the number of teeth of described left bank gas cam idle gear, described right exhaust cam shaft carrier gear and described admission cam shaft carrier gear are identical.

Preferably, the number of teeth of described crankshaft gear is set to 41, and the external diameter of gear is set to 153 millimeters.

In a preferred embodiment, described admission cam shaft carrier gear is rotatably connected on air inlet bearing stationary axle by admission cam shaft bridging bearing, described right exhaust cam shaft carrier gear is rotatably connected to right exhaust bearing stationary axle by right exhaust cam shaft bridging bearing, and described left bank gas cam idle gear rotatably connects left bank gas bearing stationary axle by left exhaust cam shaft bridging bearing.

According to another aspect of the present invention, in the downstream of described high pressure gas holder group, the upstream of described controller is provided with pressurized air heating equipment, to be heated by the pressurized air from high pressure gas holder group, to improve the temperature of air inlet.

Preferably, described left and right two exhaust casing is respectively containing 6 or 4 cylinders, and the cylinder cap of each cylinder has 4 outlet valves and 1 gas larynx.

Accompanying drawing explanation

To describe according to preferred but nonrestrictive embodiment of the present invention now, these and other features of the present invention, aspect and advantage will become apparent when reading following detailed description in detail with reference to accompanying drawing, wherein:

Fig. 1 is the general illustration according to V-type multi-cylinder aerodynamic engine of the present invention;

Fig. 2 is that the three-dimensional removing the V-type multi-cylinder aerodynamic engine body after controller, cylinder and cylinder head according to the present invention in Fig. 1 looks side ways perspective view;

Fig. 3 is the side view that the transverse direction of engine body in Fig. 1 takes, and it comprises the cross section of cylinder, cylinder head and controller;

Fig. 4 is the exhaust cam shaft structure schematic diagram in Fig. 2;

Fig. 5 is the bent axle modular construction schematic diagram in Fig. 2;

Fig. 6 is the perspective view of the controller for V-type multi-cylinder aerodynamic engine of the present invention;

Fig. 7 is the cross sectional longitudinal view of the controller in Fig. 6;

Fig. 8 is the lateral cross side view of the controller in Fig. 6;

Fig. 9 is the admission cam shaft structure schematic diagram in Fig. 2;

Figure 10 A is the perspective view of the gear-box for V-type multi-cylinder aerodynamic engine;

Figure 10 B is the plan view of Figure 10 A;

Figure 10 C is the side view of Figure 10 A.

Embodiment

The following description is only exemplary and be not to limit the disclosure, application or purposes in essence.Should be understood that, in whole accompanying drawing, corresponding reference character represents identical or corresponding parts and feature.

With reference now to the general illustration that Fig. 1, Fig. 1 are according to V-type multi-cylinder aerodynamic engine of the present invention.In FIG, V-type multi-cylinder aerodynamic engine comprises engine body 1, cylinders power distributor 2, power equipment 4, controller system 6, air compressor 7, condenser 11, tail gas recycle tank 9, high pressure gas holder group 13, constant-pressure tank 16, pressurized air heating equipment 101, air inlet control series flow control valve 23, electronic control unit ECU 29, pressure-limit valve 702, sequence valve 703.As shown in Figure 1, high pressure gas holder group 13 is connected with external gas station or external aerator by compressed air inlet pipeline 14, to obtain required high pressure air from the external world.Compressed air inlet pipeline 14 is provided with flowmeter A, pressure meter P and manual switch (not shown).Flowmeter A is used for the compressed-air actuated flow that measurement and monitoring enters high pressure gas holder group 13, and pressure meter P is used for the compressed-air actuated pressure that measurement and monitoring enters high pressure gas holder group 13.When needs carry out aerating by external aerator or gas station to high pressure gas holder group 13, open manual switch, high pressure air enters high pressure gas holder group 13, when the flowmeter A on compressed air inlet pipeline 14 and pressure meter P reaches specified value, close manual switch, complete the gas replenishment process of high pressure gas holder group 13, so just can obtain the pressurized air of such as 30MPa under rated pressure.In order to ensure the Safety performance of gas holder, high pressure gas holder group 13 can arrange one, two or more safety valve (not shown).

High pressure gas holder group 13 can be there are one, two, three of enough capacity, a four or more high pressure gas holder combines with the form of serial or parallel connection, according to the actual demand of application, determines the composition gas tank number of high pressure gas holder group 13.High pressure gas holder group 13 is connected to constant-pressure tank 16 by pipeline 15, pipeline 15 is provided with equally the flowmeter A and pressure meter P and reduction valve 701 that distinguish monitor and forecast compressed air require and pressure.The high pressure air that reduction valve 701 is used for high pressure gas holder group 13 is provided reduces pressure, and is sent to constant-pressure tank 16 with suitable pressure.Constant-pressure tank 16 is used for the stable pressure from the high-pressure air of high pressure gas holder group 13, its pressure a little less than the pressure in high pressure gas holder group 13, such as between 21-25MPa, preferably at about 21MPa.

Pipeline 17 between constant-pressure tank 16 and air inlet control series flow control valve 23 is provided with pressurized air heating equipment 101, this heating equipment is the device utilizing electric current to heat air, it can adopt Ac also can adopt direct current, adopts which kind of electric current to depend on to be set in that the direct current button 101-2's on pressurized air heating equipment 101 and Ac button 101-4 is selected.Pressurized air heating equipment 101 be also provided with direct current temperature adjustment button 101-1 and exchange two function buttons such as temperature adjustment button 101-3, and four gauge tables such as DC ammeter 101-5, DC voltmeter 101-6, alternating current ammeter 1-7 and A.C. voltmeter 101-8.Direct current temperature adjustment button 101-1 and the preferred temperature exchanging temperature adjustment button 101-3 and be used for respectively regulating pressurized air heating equipment 101 to adopt direct current or Ac to heat pressurized air.In order to make the pressurized air expansion work as much as possible entered in cylinder, wish that the heating-up temperature of the heatproof temperatures contracting air at cylinder and pipeline is high as much as possible.According to a preferred embodiment of the invention, the pressurized air after pressurized air heating equipment 101 heats, its temperature can reach 800 DEG C.According to direct current temperature adjustment button 101-1 and the setting exchanging temperature adjustment button 101-3, its temperature of pressurized air after heating can change at the temperature of ambient temperature to 800 DEG C, so just can meet compressed-air actuated temperature requirement fully, to improve compressed-air actuated acting ability as much as possible.DC ammeter 101-5, DC voltmeter 101-6, alternating current ammeter 101-7 and A.C. voltmeter 101-8 are used for detecting the direct current of pressurized air heating equipment 101 or the current value exchanged and magnitude of voltage respectively.Pipeline 17 is also provided with flowmeter A and the pressure meter P of monitor and forecast compressed air require and pressure respectively.Control the control of series flow control valve 23 from the high temperature of pressurized air heating equipment 101, high-pressure air through air inlet and enter controller system 6 through pipeline after regulating.

Describe now air inlet in detail and control series flow control valve 23.The effect that air inlet controls series flow control valve 23 decides pressurized air air inflow according to the opening time of the command signal Controlling solenoid valve of electronic control unit ECO 29.Because solenoid valve has decompression, it combines just define series flow control valve with decompression pressure regulator valve, thus can by the adjustment of rotational speed of motor in a suitable scope.The control signal 26 that air inlet control series flow control valve 23 is sent by ECU 29 controls.Engine body 1 is optionally provided with multiple sensors, such as measuring the velocity transducer of engine speed, judge the position transducer of cylinder top dead center position and judge the door oil potentiometer of door oil pedal position, can also be the temperature transducer measuring engine temperature.According to exemplary embodiment of the present invention, show velocity transducer 24 and/or door oil potentiometer 242.Velocity transducer 24 can be the various velocity transducers measuring engine speed in prior art, and is usually arranged on bent axle 1020.The oily potentiometer 242 of door can be the various position transducers measuring accelerator pedal position in prior art, and it is arranged on an oily pedal position place usually.In the occasion of non-vehicle application, the door oil potentiometer being similar to pedal position can be engine load sensor, such as, monitor the position transducer etc. that the electric current controlling generation current size in the torque sensor of engine output torque, generating occasion selects knob.ECU 29 is according to the signal of various sensor, any one or two in the position signal of the rate signal of such as velocity transducer 24 and door oil potentiometer 242, control signal 26 is sent through calculation process, control signal 26 controls air inlet and controls series flow control valve, thus air inlet can be realized control high speed, middling speed, the low speed needs of series flow control valve, thus corresponding to motor high speed, middling speed and slowly run.

The high pressure air of series flow control valve is controlled through pressure duct ramp metering device system 6 through air inlet, and provide high pressure air by controller system 6 to each cylinder of engine body 1, pressure such as approximately between 7-18MPa, be preferably 9-15MPa, be more preferably 11-13MPa, to drive engine piston 1140 reciprocating in cylinder body 3008 (with reference to figure 2), and the rotary motion of the bent axle 1020 to-and-fro motion of piston 1140 be transformed into via connecting rod 1100, thus meet the requirement under the various operating modes of motor.The concrete structure of controller system 6 will be described in detail later.

Continue with reference to figure 1, the rotational motion exported from engine body 1 is assigned to application apparatus through cylinders power distributor 2, and as shown in fig. 1, application apparatus comprises air compressor 7, power equipment 4.Air compressor 7 can be traditional vane compressor and piston compressor etc., also can be the pressurization device of claimant disclosed in patent documentation (CN 201261386Y) of the application.Power equipment 4 can be transmission system, generator or transmission system etc.Cylinders power distributor 2 can be fixedly connected with the flywheel on bent axle 1020, also by being such as that the link of coupling is connected with bent axle.Power is divided into two-way by cylinders power distributor 2, and power equipment 4 is distributed on a road, and air compressor 7 is distributed on another road.Power equipment 4 is connected with cylinders power distributor 2 by the connection set of clutch 3 or similar functions, and air compressor 7 is by being such as that the coupling 5 of gearing is connected with cylinders power distributor 2.When the engine operates, the cylinders power distributor 2 that rotarily drives of bent axle 1020 operates, and then power is distributed to respectively power equipment 4 and air compressor 7, thus drives power equipment 4 and air compressor 7 to work.Claimant's Chinese patent application 201110331831.3 and 201110373185.7 before it of the application describe in detail structure and the structure of cylinders power distributor, at this, the full text of these two applications is incorporated herein by reference, open to carry out cylinders power distributor.

Because compressed air engine of the present invention is by high-pressure air Direct driver, in the process of crankshaft rotating 0-180 degree, high pressure air drives piston 1140 moves, when piston arrives moves upward because of inertia after bottom dead center, bent axle is rotated further 180 degree of-360 degree, motor is exhausted stroke, the gas be now vented still has higher pressure, be such as about 3MPa, the Exhaust Gas with elevated pressures is directly discharged in air and easily forms high pressure exhaust gas stream on the one hand, cause tail gas noise, on the other hand the energy that contains of loss pressurized air.Therefore, recycling the tail gas of compressed air engine is an imperative key technology.Supplementary pressurized air loop structure of the present invention is summarized as follows:

The tail gas of discharging from the discharge header 27 of engine body 1 20 is transported to tail gas recycle tank 9 by the road.Pipeline 8 between tail gas recycle tank 9 and air compressor 7 is provided with flowmeter A and pressure meter P, with the flow of the tail gas of difference examination and controlling after air compressor 7 compresses and pressure.Its pressure of tail gas after air compressor 7 compresses is increased significantly, usually can reach between about 10 MPa to about 25MPa.Tail gas after compression divides two-way to replenish the supply to engine body 1 by air compressor 7.Branch line 704 and 10 is provided with at the downstream part of pipeline 705, pipeline 10 leads to high pressure gas holder group 13, when the tail gas pressure after air compressor 7 supercharging is greater than 15MPa, supercharging tail gas is set as it being such as the pressure-limit valve of 15MPa by cracking pressure, high pressure gas holder group 13 is sent into subsequently after being set in the cooling of the condenser 11 on pipeline 10, or again by entering high pressure gas holder group 13 after exhaust gas filter (not shown).Pipeline 704 is provided with sequence valve 703, when the tail gas pressure after air compressor 7 supercharging is less than 15MPa, supercharging tail gas is be such as that (this sequence valve is opened when suction pressure is less than 15MPa for the sequence valve of 15MPa by pressure limiting pressure setting, automatically close when suction pressure is greater than 15MPa), enter constant-pressure tank 16 through pipeline 704 subsequently.In alternative, can according to actual needs, the setting cracking pressure of pressure-limit valve and the closing pressure of sequence valve.Can be such as any pressure between 7Ma to 20MPa.Preferably, be 10,12,15,17, any one in 20MPa.Alternatively, also the pipeline between condenser 11 and high pressure gas holder group 13 can arrange one-way valve (not shown), only allow the clean tail gas unidirectional inflow high pressure gas holder group 13 after supercharging.Thus, for drive the high pressure air of engine piston 1140 after acting its quite a few after supplementing pressurized air loop (comprising pressure-limit valve, sequence valve, tail gas recycle tank, air engine, condenser and the connecting pipeline between them) supercharging purification, be recovered to high pressure gas holder group, thus achieve the recycling of tail gas.The existence supplementing pressurized air loop not only considerably solves the direct problem of noise pollution being vented air and causing of the tail gas (being generally about 3MPa) with equivalent pressure, and effectively reduces the volume requirements problem to Large Copacity high pressure gas holder group 13.In other words, for the high pressure gas holder group 13 of giving constant volume, the existence supplementing pressurized air loop considerably increases the continuous working period of compressed air engine, in the traffic tool using compressed air engine or power generating equipment, considerably increase the continuous working period of the traffic tool or power generating equipment, thus improve the efficiency of compressed air engine significantly.

Consult Fig. 2 and Fig. 3 now, Fig. 2 is that the three-dimensional removing the aerodynamic force V-type multi-cylinder engine body after controller, cylinder body, cylinder head according to the present invention in Fig. 1 looks side ways perspective view.Fig. 3 is the side view that the transverse direction of engine body in Fig. 1 takes, and it comprises the cross section of cylinder, cylinder head and controller.As shown in Figures 2 and 3, motor the machine 1 comprises left and right two exhaust casings, and two exhaust casings become V-type each other, and v-angle can change according to embody rule, can be 60 °, 90 °, 120 ° or other angles.In the configuration shown in Fig. 3, preferably, the angle of left and right two exhaust casing is 75 °-135 °, and what be more preferably is 75 °, 90 °, 120 °, 135 °.Every exhaust casing has multiple cylinder 3008, specifically, can be 1,2,3,4,5,6,7 etc.In example of the present invention, the cylinder number of often arranging is 4 or 6, and this just can form V-type 8 cylinder or 12 cylinder multicylinder engines.In the example of one-sided 6 cylinders shown in Fig. 2,6, left side cylinder is respectively #1 cylinder, #3 cylinder, #5 cylinder, #7 cylinder, #9 cylinder, #11 cylinder; 6 cylinders in right side are respectively #2 cylinder, #4 cylinder, #6 cylinder, #8 cylinder, #10 cylinder, #12 cylinder.Accommodate piston 1140,1130 in cylinder 3008, piston is connected on bent axle 1020 by connecting rod 1170,1100.The piston that rotarily drives of bent axle 1020 moves reciprocatingly in cylinder 3008.Left exhaust cam shaft 1200 is placed in the left side of V-type engine, which is provided with the left bank gas cam of camshaft 1210, be used for control left side exhaust valve unlatching.Right exhaust cam shaft 1070 is placed in the right side of V-type engine, which is provided with right exhaust cam axis cam 1110, is used for controlling the unlatching of right side exhaust door.In the twin-six air-powered motor shown in Fig. 2, be different from traditional twin-six engine, admission cam shaft 1150 only arranges 1, it is used for controlling the high pressure air air inlet of the left and right sides 12 cylinder, it is provided with intake cam axis cam 1160, to be used for the high pressure air air inlet of control cylinder 3008.Left and right exhaust cam shaft 1200,1070 and admission cam shaft 1150 are driven by gear-box by bent axle 1020.In the illustrated example shown in fig. 2, gear-box comprises crankshaft gear 1030, right exhaust cam shaft carrier gear 1040, left bank gas cam idle gear, admission cam shaft carrier gear 1050, right exhaust cam shaftgear 1060 and left bank gas camshaft gear wheel 1230 and oil pump carrier gear 1010.The transmission moving through gear-box of bent axle 1020 and drive the motion of inlet and outlet camshaft, thus realize air inlet and the exhaust of motor.Admission cam shaft carrier gear 1050 has admission cam shaft bridging bearing 1190 and air inlet bearing stationary axle 1260, right exhaust cam shaft carrier gear 1040 has right exhaust cam shaft bridging bearing 1240 and right exhaust bearing stationary axle 1250, left bank gas cam idle gear has left exhaust cam shaft bridging bearing 1220 and left bank gas bearing stationary axle 1270, and oil pump carrier gear 1010 has oil pump bridging bearing 1290 and oil pump bridging bearing stationary axle 1280.The stationary axle of these gears is all used for respective gears to be fixed on the housing of gear-box.The opposite extremity of the crankshaft gear 1030 of bent axle 1020 is provided with flywheel 1120, is used for auxiliary crank rotation.

The distribution device of V-type multi-cylinder aerodynamic engine and the configuration of controller is more clearly show with further reference to Fig. 3, Fig. 3.Cylinder head shown in Fig. 3 is split type cylinder head 002, and cylinder head 002 structure, the pattern of left hand cylinder and right cylinder are identical, but can be installed separately, and is used for the cylinder body 3008 of the airtight left and right sides respectively.Sealing gasket 3006 is provided with between cylinder cap 002 and cylinder body 3008, cylinder cap 002 is the structure of the cuboid substantially of central hollow, its upper end is connected with cylinder cover 3005, cylinder cover 3005 has through hole, pass through to allow admission line 3001 and enter the gas be arranged in cylinder head 002 to shout 3010, thus allow to enter expansion work room 3020 from the high pressure air of controller 6.Pressurized gas are expansion work in expanded exhaust room 3020, and promote piston 1140 and move downward in cylinder liner 3007, this is expansion stroke.The merit that expansion stroke exports is by the outside outputting power of crankshaft rod system.When piston 1140 is moved to top dead center position by bottom dead center position in cylinder, outlet valve 3012 is opened, and have in the air self-expanding exhaust chamber of certain pressure and discharge via exhaust duct 3002, this is exhaust stroke.Piston 1140 near top dead center time, outlet valve 3012 is closed, and controller 6 starts again as expanded exhaust room air feed, enters next circulation.Obviously, the bent axle 1020 of motor of the present invention often rotates a circle (360 degree), just acting once, and unlike traditional four stroke engine, enclose in the process of (720 degree) complete once complete air inlet, compression, expansion and exhaust stroke at crank rotation two.This as two stroke engine the same, but different from traditional two stroke engine because traditional two stroke engine is provided with suction port in cylinder bottom usually, and be provided with scavenging port and relief opening in cylinder appropriate location.And two stroke engine of the present invention is provided with the gas larynx 3010 for high pressure air air inlet and the outlet valve 3012 for exhaust emissions, and it is that admission cam shaft 1150 is realized by controller 6 that the connected sum of gas larynx 3010 closes, and the connected sum of outlet valve 3012 closed be drive exhaust cam shaft 1070 to rotate by bent axle, and to be realized by the opening and closing that rocking arm 3015 controls outlet valve.Therefore two stroke engine of the present invention is different from traditional two stroke engine completely, its efficiently utilize can direct expansion acting high-pressure air, bent axle 1020 often rotates and does work once once circle piston 1140, thus in identical air displacement situation, compare traditional four stroke engine, power can double.

Because high pressure air is behind expansion work room 3020, still there is larger pressure, in time that the air exhaust cylinder after acting is just abnormal important, for this exhaust gear of the present invention is different from traditional multicylinder engine, it adopts 4 outlet valves 3012, and namely two outlet valves are vented by an exhaust cam axis cam 1110, the exhaust gas drive mechanism controls that tappet 3019, rocking arm 3015 and a valve shoulder pole iron 3014 forms.Due to corresponding two the exhaust cam axis cams of each cylinder, thus each cylinder have employed 4 outlet valves 3012.Therewith greatly unlike, admission gear of the present invention then eliminates traditional suction valve, and is realized by the form of a cylinder gas larynx 3010.So, just promptly tail gas can be discharged in exhaust stroke, thus improve the efficiency of motor.With further reference to Fig. 3, right exhaust cam shaft 1070 of the present invention, left exhaust cam shaft 1200 and admission cam shaft 1150 are arranged on the diverse location of cylinder body 3008, namely be different from traditional overhead camshaft engine, being also same as traditional end puts cam axle engine.As can be seen, right exhaust cam shaft 1070 and left exhaust cam shaft 1200 are placed in the outer position in the right side of cylinder body 3008, left side respectively, both the horizontal line of paper plane and horizontal plane substantial parallel.Admission cam shaft 1150 is placed in the top of the V-type groove of cylinder body 3008, and is positioned at the central position of line.The benefit of this configuration is the dynamic balancing of engine body, is convenient to the layout of gear-box.The tail gas of discharging from the gas exhaust piping 3002 of each cylinder of left and right is sent into upper and lower exhaust pipe 3003,3004, is convenient to recycling of tail gas.

With reference now to exhaust cam shaft 1070 structural representation that Fig. 4, Fig. 4 are the engine main body in Fig. 2.Exhaust cam shaft 1070 comprises unit cam 1110A.In the exemplary embodiment, unit cam 1110A comprises 6 unit cams, and it is respectively first module cam 2701, second unit cam 2702, the 3rd unit cam 2703, the 4th unit cam 2704, the 5th unit cam 2705, the 6th unit cam 2706.In an alternative embodiment, the number of unit cam 1110A can be 2,4,6,8,12 or more, and this depends on the outlet valve number of cylinder number and each cylinder.In an exemplary embodiment of the present invention, each unit cam 1110A comprises two cams, the unlatching of the outlet valve of each its correspondence of cam production.In preferred embodiment in the diagram, the phase place of unit cam 1110A is set as follows: first module cam 2701 differ with second unit cam 2702-120 to spend, second unit cam 2702 differ with the 3rd unit cam 2703-120 to spend, the 3rd unit cam 2703 differs 180 degree with the 4th unit cam 2704, the 4th unit cam 2704 differs 120 degree with the 5th unit cam 2705, the 5th unit cam 2705 differs 120 degree with the 6th unit cam 2706.Unit cam under so arranging, the job order that can realize unit cam is: first and the 5th unit cam work simultaneously, then the 3rd work together with the 6th unit cam, the second last works together with the 4th unit cam.Corresponding piston is divided into left and right two row with admission cam shaft 1150 symmetry, and wherein first piston #1, the 3rd piston #3, the 5th piston #5, the 7th piston #7, the 9th piston #9, the 11 piston #11 are positioned at left side; Second piston #2, the 4th piston #4, the 6th piston #6, the 8th piston #8, the tenth piston #10, the 12 piston #12 are positioned at right side.Thus, the job order of corresponding engine piston is: #1 → #6 → #9 → #12 → #5 → #4 → #11 → #8 → #3 → #2 → #7 → #10 → #1.According to instruction of the present invention, those skilled in the art can arrange and be different from unit cam of the present invention and operating phase thereof and job order, but it all falls within the scope of the invention.

With reference now to Fig. 5, bent axle 1020 comprises flywheel connecting end 1021, lubricant oil oilhole 1022, link rotating shaft 1023 and bent axle nipper wheel shaft 1024.Link rotating shaft 1023 on bent axle 1020 is provided with one or more lubricant oil oilhole 1022, to provide lubricating oil for bent axle.The right side adjacent of bent axle nipper wheel shaft 1024 is provided with gear connecting bolt, to be connected with the respective gears in gearbox system.The adjacent position, outside of flywheel connecting end 1021 is provided with flywheel connecting bolt, to form a fixed connection with flywheel 1120.In a preferred embodiment of the invention, the unit crank throw 1080 of bent axle comprises six unit crank throws, is first module crank throw 10801, second unit crank throw 10802, the 3rd unit crank throw 10803, the 4th unit crank throw 10804, the 5th unit crank throw 10805, the 6th unit crank throw 10806 respectively.It corresponds respectively to first to six-bar linkage 1170 or piston 1140.In an alternative embodiment, unit crank throw 1080 can comprise the unit crank throw of different number, and such as 2,4,6,8,12 or more, these are all that those skilled in the art easily expect.In preferred embodiment in Figure 5, the phase place of each unit crank throw is set as follows: first module crank throw 10801 differ with second unit crank throw 10802-120 to spend, second unit crank throw 10802 differ with the 3rd unit crank throw 10803-120 to spend, the 3rd unit crank throw 10803 differs 180 degree with the 4th unit crank throw 10804, the 4th unit crank throw 10804 differs 120 degree with the 5th unit crank throw 10805, the 5th unit crank throw 10805 differs 120 degree with the 6th unit crank throw 10806.Crank throw unit under so arranging, the job order that can realize crank throw unit is: first and the 5th unit crank throw work simultaneously, then the 3rd work together with the 6th unit crank throw, the second last works together with the 4th unit crank throw.Corresponding piston is divided into left and right two row with admission cam shaft 1150 symmetry, and wherein first piston #1, the 3rd piston #3, the 5th piston #5, the 7th piston #7, the 9th piston #9, the 11 piston #11 are positioned at left side; Second piston #2, the 4th piston #4, the 6th piston #6, the 8th piston #8, the tenth piston #10, the 12 piston #12 are positioned at right side.Thus, the job order of corresponding engine piston is: #1 → #6 → #9 → #12 → #5 → #4 → #11 → #8 → #3 → #2 → #7 → #10 → #1.According to instruction of the present invention, those skilled in the art can arrange and be different from unit crank throw of the present invention and operating phase thereof and job order, but it all falls within the scope of the invention.

With reference now to Fig. 6-Fig. 8, it is the view of the controller of compressed air engine.As shown in Figure 6, controller comprises high-pressure common rail constant voltage pipe 2070, controller unit 2000 and intake cam shaft housing 2290.In the controller shown in Fig. 6-Fig. 8, controller comprises 6 controller units 2000, its corresponding twin-six multicylinder engine.According to the difference of V-type multi-cylinder engine cylinder body number, the number of controller unit 2000 can change, and it can be such as 2,3,4,5,7 etc.Controller unit 2000 comprises seat 2140 in seat 2270 under controller upper cover 2080, controller, controller.To be provided with in 1 seat in seat projection 2291,1 in each controller in seat 2140 and outer rim 2292, first and second controller valve 2100, first and second controller valve spring 2170, first and second controller valve cover for seat 2120, first and second controller valve spring cover for seat 2180 and the first and second oil sealing linings 2160 are installed.For convenience of description, the controller valve 2100 for left hand cylinder air feed is called the first controller valve 2100 by us, for the controller valve 2100 of right cylinder air feed is called second controller valve.The title of other corresponding parts the like.First and second controller valves 2100 are supported on middle seat respectively by respective controller valve cover for seat 2120 and install between outer rim 2292 and middle seat projection 2291.According to the spacing of adjacent two intake cams in the size of controller valve cover for seat 2120 and controller valve 2100 and admission cam shaft 1150, the thickness of middle seat projection 2291 can be determined.The existence of middle seat projection makes seat 2140 in each controller can set two controller valves 2100, thus two cylinders making a controller unit 2000 can be the left and right sides of V-type multi-cylinder engine provide pressurized air.In the controller in seat 2140, cavity (being controller valve port 2111 shown in Fig. 7) is there is between oil sealing lining 2160 and controller valve cover for seat 2120, the side of this cavity is provided with inlet hole, in the illustrated embodiment, the first cylinder intake hole 2130 and the second cylinder intake hole 2280 is respectively.Cylinder intake hole communicates with the gas throat in cylinder head, with when controller valve 2100 is opened, pressurized air from high-pressure common rail constant voltage pipe 2070 is entered cylinder intake hole 2130,2180 via an air inlet pipeline 2112, thus pressurized air is sent into expanded exhaust room, thus drive engine operation.

High-pressure common rail constant voltage pipe 2070 has cylindrical outer shape, and it also can be the profile such as rectangle, triangle.High-pressure common rail constant voltage pipe 2070 inside is be such as columniform cavity, to accept the high pressure admission from air intake control valve 2020, and keep the compressed air pressure in cavity balanced substantially, to make the high-pressure air of the expanded exhaust indoor initially entering each cylinder have identical pressure, thus to make engine mildness.The two ends of high-pressure common rail constant voltage pipe 2070 are fixedly equipped with air inlet rear end cover 2060, the air inlet rear end cover 2060 be connected with air intake control valve 2020 at it has outward extending flange, this flange extend in the pipeline between air intake control valve 2020 and high-pressure common rail constant voltage pipe 2070, and is removably fixedly connected with pressure duct by the Placement being such as screw thread.The air inlet rear end cover 2060 of high-pressure common rail constant voltage pipe 2070 is connected with high-pressure common rail constant voltage pipe 2070 by end cover connecting bolt.High-pressure common rail constant voltage pipe 2070 is provided with the upper cover attachment hole (unmarked) corresponding to number of cylinders, and controller upper cover 2080 is communicated with high-pressure common rail constant voltage pipe 2070 by upper cover attachment hole fixing seal ground.In the preferred embodiment shown in the drawings, the number of upper cover attachment hole is 6.Controller upper cover 2080 has inverted T-shaped along on the section of its center line, it has columniform air inlet pipeline 2081 and rounded lower surface, air inlet pipeline 2081 is threaded onto in upper cover attachment hole by its periphery, upper end, is removably connected to be formed to fix with high-pressure common rail constant voltage pipe 2070.Controller upper cover 2080 by upper cover and middle seat connecting bolt or other fastening pieces and seat in controller 2140 formed seal, be detachably fixedly connected with.In controller, seat 2140 forms by middle seat and lower seat connecting bolt 2220 or other fastening pieces and seat under controller 2270 being detachably fixedly connected with of sealing.

With further reference to Fig. 6-Fig. 8, in controller, seat 2140 is provided with the different hole of diameter in the middle, is followed successively by controller valve seat trepanning 2121, controller valve port 2111, oil sealing bush hole 2150, controller valve spring hole 2171 from top to bottom.In the exemplary embodiment, the diameter of controller valve seat trepanning 2121 is greater than the diameter of controller valve port 2111 and is greater than the diameter of oil sealing bush hole 2150, and the diameter of controller valve port 2111 is greater than the diameter of oil sealing bush hole 2150.The diameter in controller valve spring hole 2171 is less than the diameter of controller valve port 2111, but requires the diameter being greater than oil sealing bush hole 2150.In a preferred embodiment, the diameter in controller valve spring hole 2171 is less than the diameter of controller valve port 2111, and is slightly less than the diameter of controller valve seat trepanning 2121.Controller valve cover for seat 2120 is arranged in controller valve seat trepanning 2121, and is supported on controller valve port 2111.Oil sealing lining 2160 is arranged in oil sealing bush hole 2150, and is supported on controller valve spring 2170, by the valve stem 2110 of controller valve 2100 in it.This oil sealing lining 2160 also play the guiding role to valve stem except carrying out sealing to controller valve 2100.Controller valve spring 2170 is arranged in controller valve spring hole 2171, and its lower end is supported with controller valve spring cover for seat 2180, and is fastened on controller valve spring cover for seat 2180 by controller valve collet sheet 2190.When motor does not work, the pretensioning that controller valve spring 2170 preload is certain, controller valve 2100 is resisted against in valve cover for seat 2120 by it, and controller valve 2100 is closed, and then controls entering of gas.

As shown in Figure 9, admission cam shaft 1150 is provided with 12 cams, be respectively the first cam 1151, second cam 1152, the 3rd cam 1153, four-cam 1154, the 5th cam 1155, the 6th cam 1156, the 7th cam 1157, the 8th cam 1158, the 9th cam 1159, the tenth cam 1150-1, the 11 cam 1150-2, the 12 cam 1150-3, be respectively used to the intake process of 12 cylinders controlling V-type multi-cylinder engine.Being just clockwise viewed from intake cam shaftgear direction, be negative counterclockwise, first cam differs 90 ° with the second cam, second cam differs 30 ° with the 3rd cam, 3rd cam differs 90 ° with four-cam, four-cam differs 30 ° with the 5th cam, 5th cam differs 90 ° with the 6th cam, 6th cam differs 90 ° with the 7th cam, 7th cam differs 90 ° with the 8th cam, 8th cam differs 150 ° with the 9th cam, 9th cam differs 90 ° with the tenth cam, tenth cam differs 150 ° with the 11 cam, 11 cam differs 90 ° with the 12 cam.

Consult Fig. 7 and Fig. 9 now, under controller, seat 2270 is fixedly welded on intake cam shaft housing 2290 via admission cam shaft shell aperture 2293, its inside is provided with multiple mounting hole for mount controller fore-set 2200, it is according to the difference of cylinder number, can arrange the mounting hole for controller fore-set 2200 of different number, such as, can be 1 or 2.Controller fore-set 2200 is arranged in the mounting hole of controller fore-set 2200, and rotates with the admission cam shaft 1150 be arranged in admission cam shaft 1150 mounting hole and pump.When needs provide high pressure air to cylinder, the cam upwards jack-up controller fore-set 2200 of admission cam shaft 1150, the valve stem 2110 of controller fore-set 2200 jack-up controller valve 2100 then, valve stem 2110 is made to overcome the pulling force of controller valve spring 2170, leave controller valve cover for seat 2120, thus controller valve 2100 is opened, high pressure air is able to enter expanded exhaust room from high-pressure common rail constant voltage pipe 2070, to meet the air feed demand of motor.Admission cam shaft 1150 is provided with the cam of 12 difference several angles, 12 fore-sets 2200 will be promoted when admission cam shaft 1150 rotates move up and down, what have moves upward, what have peaks, what have moves downward, what have touches the bottom, its job order is followed successively by the first cam, 6th cam, 9th cam, 12 cam, 5th cam, four-cam, 11 cam, 8th cam, 3rd cam, second cam, 7th cam, tenth cam, after admission cam shaft 1150 turns over several angle with bent axle 1020, the valve stem 2110 of controller valve 2100 is again seated in controller valve cover for seat 2120 under the restoring force effect of controller valve spring 2170, controller valve 2100 is closed, air feed terminates.Because compressed air engine of the present invention is two stroke engine, bent axle 1020 often rotates one week, controller valve 2100 and each opening and closing of outlet valve once, therefore, are easy to arrange the annexation of the cam phase of admission cam shaft 1150 and exhaust cam shaft 1070A and they and bent axle.

With reference now to Figure 10, Figure 10 A-Figure 10 C, be referred to as Figure 10, it illustrate in detail the different views of the gear-box for V-type multi-cylinder aerodynamic engine.As shown in Figure 10, gearbox system comprises polygonal lid 1300, crankshaft gear 1030, right exhaust cam shaft carrier gear 1040, left bank gas cam idle gear 1310, admission cam shaft carrier gear 1050, right exhaust cam shaftgear 1060 and left bank gas camshaft gear wheel 1230, oil pump carrier gear 1010 and water pump gear 1320.Crankshaft gear 1030 is fixedly connected with bent axle 1020 one end through polygonal lid 1300, to transmit the rotation from bent axle.It is such as the driving gear 1010 of oil pump gear that the below (shown in Figure 10 B orientation) of crankshaft gear 1030 is provided with, and is such as that the component of oil pump rotates to be driven by driving gear 1010.Above crankshaft gear 1030, (shown in Figure 10 B orientation) is disposed with left bank gas camshaft gear wheel 1230, left bank gas cam idle gear 1310, admission cam shaft carrier gear 1050, right exhaust cam shaft carrier gear 1040 and right exhaust cam shaftgear 1060 from left to right.Left bank gas cam idle gear 1310 and right exhaust cam shaft carrier gear 1040 are separately positioned on the arranged on left and right sides of crankshaft gear 1030 and engage with crankshaft gear 1030 respectively.Outside the left side of left bank gas cam idle gear 1310, be provided with left bank gas camshaft gear wheel 1230 engageablely.The respective center of rotation of crankshaft gear 1030, left bank gas cam idle gear 1310 and left bank gas camshaft gear wheel 1230 point-blank (this is called the first straight line), this first straight line and horizontal plane oblique.Outside the right side of right exhaust cam shaft carrier gear 1040, be provided with right exhaust cam shaftgear 1060 engageablely.The respective center of rotation (this is called the second straight line) on another straight line of crankshaft gear 1030, right exhaust cam shaft carrier gear 1040 and right exhaust cam shaftgear 1060, this second straight line and horizontal plane oblique, and be positioned at same plane with aforementioned first straight line.Admission cam shaft carrier gear 1050 and intake cam shaftgear 1180 is provided with directly over crankshaft gear 1030.Admission cam shaft carrier gear 1050 is located between left bank gas cam idle gear 1310 and right exhaust cam shaft carrier gear 1040, and simultaneously with these two carrier gear outer gearings, but, admission cam shaft carrier gear 1050 does not directly engage with crankshaft gear 1030, and its motion is driven via left and right exhaust cam shaft carrier gear indirectly by crankshaft gear 1030.The respective center of rotation of crankshaft gear 1030, admission cam shaft carrier gear 1050 and intake cam shaftgear 1180 is in alignment (being called the 3rd straight line herein), 3rd straight line substantially with horizontal plane, and the first straight line and the second straight line are distributed in the 3rd straight line both sides substantially symmetrically.In the bottom of crankshaft gear 1030, be also provided with oil pump carrier gear 1010, it engages with the actuation gear of oil pump, to drive oil pump work.Outside the left side of left bank gas camshaft gear wheel 1230, be also provided with water pump gear 1320, it engages with the water pump driving gear arranged on the engine, to drive pump working.

In the exemplary embodiment, left bank gas camshaft gear wheel 1230 is directly fixedly connected on left exhaust cam shaft 1200, right exhaust cam shaftgear 1060 is directly fixedly connected on right exhaust cam shaft 1070, thus the rotation of exhaust cam shaftgear 1310,1060 directly drives the rotation of exhaust cam shaft 1070,1200.Intake cam shaftgear 1180 is directly fixedly connected on admission cam shaft 1150, it is driven jointly by left bank gas cam idle gear 1310, right exhaust cam shaft carrier gear 1040, admission cam shaft carrier gear 1050 three, by the transmission of three carrier gears, crankshaft gear 1030 just drives admission cam shaft 1150 to rotate, thus realizes the opening and closing of controller valve 2100.

With further reference to Figure 10, in order to ensure that crankshaft gear 1030 stably drives intake cam shaftgear 1180, left bank gas camshaft gear wheel 1230, right exhaust cam shaftgear 1060 to rotate, and realize crank rotation of the present invention one week, intake and exhaust respectively requirement once, require that crankshaft gear 1030, left bank gas camshaft gear wheel 1230, the equal and opposite in direction of right exhaust cam shaftgear 1060, the number of teeth are identical, such as the number of teeth of crankshaft gear is set to 41, the external diameter of gear is set to 153 millimeters.Also other the number of teeth can be set according to the inner space size of gear-box, such as 25,31,39,45 etc.Require left bank gas cam idle gear 1310 equally, right exhaust cam shaft carrier gear 1040 is identical with the size of admission cam shaft carrier gear 1050, the number of teeth is identical.These gears above-mentioned are made by identical material such as cast iron, and the external diameter of gear is 153 millimeters, and are helical gear.

The carrier gear of gear-box is all by being fixedly connected with (such as welding) stationary axle on polygonal lid 1300 and the bearing of self rotatably connects on the engine.Such as, admission cam shaft carrier gear 1050 is rotatably connected on air inlet bearing stationary axle 1260 by admission cam shaft bridging bearing 1190, right exhaust cam shaft carrier gear 1040 is rotatably connected to right exhaust bearing stationary axle 1250 by right exhaust cam shaft bridging bearing 1240, and left bank gas cam idle gear is rotatably connected on left bank gas bearing stationary axle 1270 by left exhaust cam shaft bridging bearing 1220.Polygonal lid 1300 is also provided with multiple different hole, such as gear testing hole and bolt connecting hole.Polygonal lid 1300 is bolted hole and is connected on engine housing.Polygonal lid 1300 is also provided with for the oilhole of lubricating oil flow and the rings seat for installing suspension ring.

This specification disclose in detail the present invention, comprises optimal mode, and anyone that also can make related domain puts into practice the present invention, comprises the method manufacturing and use any equipment or system and perform any introducing.Protection scope of the present invention by appended claims, and can be included in the various modification made for the present invention of pin when not departing from scope and spirit, remodeling and equivalents.

Claims

1. for a gear-box for V-type multi-cylinder aerodynamic engine, described air-powered motor:

Engine body (1), it comprises left and right two exhaust casings, bent axle (1020), exhaust cam shaft (1200,1070), admission cam shaft (1150);

Controller (6), it relies on described admission cam shaft (1150) to activate;

High pressure gas holder group (13), it is communicated with external aerator by pipeline (14);

Front gear box comprises: polygonal lid (1300), crankshaft gear (1030), right exhaust cam shaft carrier gear (1040), left bank gas cam idle gear (1310), admission cam shaft carrier gear (1050), right exhaust cam shaftgear (1060) and left bank gas camshaft gear wheel (1230);

It is characterized in that, described left bank gas camshaft gear wheel (1230) and right exhaust cam shaftgear (1060) are located at the arranged on left and right sides of crankshaft gear (1030) respectively, crankshaft gear (1030) is fixedly connected with bent axle (1020) one end through polygonal lid (1300), to transmit the rotation from bent axle; Described left bank gas camshaft gear wheel (1230), described left bank gas cam idle gear (1310), described admission cam shaft carrier gear (1050), described right exhaust cam shaft carrier gear (1040) and described right exhaust cam shaftgear (1060) is disposed with from left to right in the top of described crankshaft gear (1030); Described left bank gas cam idle gear (1310) and described right exhaust cam shaft carrier gear (1040) are separately positioned on the arranged on left and right sides of described crankshaft gear (1030) and engage with described crankshaft gear (1030) respectively.

2. gear-box according to claim 1, is characterized in that, the below of described crankshaft gear (1030) is provided with transmission gear of engine oil pump (1010), rotates to drive oil pump.

3. gear-box according to claim 1, it is characterized in that, outside the left side of described left bank gas cam idle gear (1310), be provided with described left bank gas camshaft gear wheel (1230) engageablely, the line of described crankshaft gear (1030), described left bank gas cam idle gear (1310) and described left bank gas camshaft gear wheel (1230) is the first straight line, this first straight line and horizontal plane oblique.

4. gear-box according to claim 3, is characterized in that, outside the right side of described right exhaust cam shaft carrier gear (1040), is provided with described right exhaust cam shaftgear (1060) engageablely; The line of the respective center of rotation of described crankshaft gear (1030), described right exhaust cam shaft carrier gear (1040) and described right exhaust cam shaftgear (1060) is the second straight line, this second straight line and horizontal plane oblique.

5. gear-box according to claim 1, is characterized in that, is provided with described admission cam shaft carrier gear (1050) and intake cam shaftgear (1180) directly over described crankshaft gear (1030); Described admission cam shaft carrier gear (1050) is located between described left bank gas cam idle gear (1310) and described right exhaust cam shaft carrier gear (1040), and simultaneously with these two carrier gear outer gearings, and wherein, described admission cam shaft carrier gear (1050) is not directly engaged with described crankshaft gear (1030).

6. gear-box according to claim 4, it is characterized in that, the line of the respective center of rotation of described crankshaft gear (1030), described admission cam shaft carrier gear (1050) and intake cam shaftgear (1180) is the 3rd straight line, 3rd straight line substantially with horizontal plane, and described first straight line and described second straight line are distributed in the 3rd straight line both sides substantially symmetrically.

7. gear-box according to claim 1, it is characterized in that, described left bank gas camshaft gear wheel (1230) is directly fixedly connected on left exhaust cam shaft (1200), described right exhaust cam shaftgear (1060) is directly fixedly connected on right exhaust cam shaft (1070), described intake cam shaftgear (1180) is directly fixedly connected on described admission cam shaft (1150), it is by described left bank gas cam idle gear (1310), described right exhaust cam shaft carrier gear (1040) and described admission cam shaft carrier gear (1050) three drive jointly.

8. according to gear-box in any one of the preceding claims wherein, it is characterized in that, equal and opposite in direction, the number of teeth of described crankshaft gear (1030), described left bank gas camshaft gear wheel (1230) and described right exhaust cam shaftgear (1060) are identical; Equal and opposite in direction, the number of teeth of described left bank gas cam idle gear (1310), described right exhaust cam shaft carrier gear (1040) and described admission cam shaft carrier gear (1050) are identical.

9. gear-box according to claim 8, is characterized in that, the number of teeth of described crankshaft gear is set to 41, and the external diameter of gear is set to 153 millimeters.

10. the gear-box according to any one of claim 1-7, it is characterized in that, described admission cam shaft carrier gear (1050) is rotatably connected on air inlet bearing stationary axle (1260) by admission cam shaft bridging bearing (1190), described right exhaust cam shaft carrier gear (1040) is rotatably connected to right exhaust bearing stationary axle (1250) by right exhaust cam shaft bridging bearing (1240), described left bank gas cam idle gear (1310) rotatably connects left bank gas bearing stationary axle (on 1270) by left exhaust cam shaft bridging bearing (1220).

11. gear-boxes according to claim 1, it is characterized in that, in the downstream of described high pressure gas holder group (13), the upstream of described controller (6) is provided with pressurized air heating equipment (101), so that the pressurized air from high pressure gas holder group (13) is heated, to improve the temperature of air inlet.

12. gear-boxes according to claim 1 or 11, it is characterized in that, described left and right two exhaust casing is respectively containing 6 or 4 cylinders, and the cylinder cap (002) of each cylinder has 4 outlet valves (3012) and 1 gas larynx (3010).