CN103195563A - Fuel injector for free piston type engine - Google Patents

Abstract

The invention discloses a fuel injector for a free piston type engine. The fuel injector comprises a hydraulic pump body assembly, a first air cylinder assembly and a second air cylinder assembly, wherein a first air inlet, a first exhaust opening and a first fuel injection port close to the first air inlet are formed in the extending surface on the cylinder wall of the first air cylinder assembly; a first spray nozzle of the first fuel injector is positioned in the first fuel injection port; a second air inlet, a second exhaust opening and a second fuel injection port close to the second air inlet are formed in the extending surface on the cylinder wall of the second air cylinder assembly; and a second spray nozzle of the second fuel injector is positioned in the second fuel injection port. The fuel injector disclosed by the invention has the benefits that a fuel injector with lower use cost can be used; the fuel is prevented from being contacted with the air cylinder wall; more-uniform mixed oil gas is ensured; the fuel injector is positioned nearby close to the air inlet, so that the fuel can be directly injected to the air cylinder; and meanwhile, the fuel injector can be allowed to leave from the burning range. Therefore, the fuel injector is prevented from being exposed in a severe burning environment.

Description

A kind of fuel injector of free piston engine

Technical field

The present invention relates to free piston engine, relate to a kind of fuel injector of free piston engine specifically.

Background technique

Usually, internal-combustion engine relies on and is turned round by the motion of the piston of mechanical constraint.For example, traditional car combustion engine comprises a crankshaft-and-connecting-rod assembly, and these mechanical structures have determined the motion mode of piston in the respective cylinder.This motor is suitable, because each position of piston any given point in the motor circulation determines that this has simplified the operation of timing and motor.Though traditional motor is greatly improved in efficient these years recently, because the restriction of engine structure causes its efficient still limited.Particularly the specific power of motor has been limited because by mechanical constraint the piston of motion formed fixing compression ratio.In addition, all movement parts (comprising camshaft and valve) of moving together with piston can produce a large amount of frictional losses, and the power that the energy of these losses all needs to sacrifice motor self is offset.The result who produces low specific power mean motor will be bigger than ideal designs state size, quality is heavier.In addition, because all these necessary mechanical connections have limited the flexibility of engine design and complete machine layout.

Some crank engine uses direct injection technology that fuel oil is injected cylinder.Though it is useful using fuel oil directly to spray further raising engine power, fuel injector and ejecting system are very expensive usually.Particularly, fuel oil directly sprays need very high fuel pressure, and this just needs a very expensive system produce and control this high pressure fuel.In addition, the nozzle of each fuel injector is directly exposed under the excessive temperature and extremely high pressure that whole combustion process produces in its place cylinder, therefore needs a relatively costly fuel injector design working under these harsh environmental conditions.

Therefore, consider from environment and other factors, just be worth us to develop a motor higher than conventional engines specific power.It should have lighter weight, littler complete machine size and the fuel efficiency of Geng Gao; These will have huge advantage in the application of automobile and stationary power generation machine.

Free piston engine is exactly the internal-combustion engine of this form, and the motion of piston can't be limited by mechanical structure in this cylinder.The motion of piston is to be controlled at the equilibrant of arbitrary given time by each piston.Because motion is non-restraint-type, so motor has variable compression ratio, this just allows to have more flexibility when the Operational Limits of designed engines.And, owing to there is not traditional crankshaft rod structure, so reduced the lateral force of piston, therefore in engine operation process, reduced loss of friction.In addition, the opposed cylinder free piston formula of opposed pistons motor is satisfactory be since himself intrinsic equilbrium running characteristic with and compact layout.Also have a significant advantage be exactly it be the motor of a two-stroke burn cycle; Also have a bigger advantage to be to use homogeneous mixing and compressed ignition (HCCI) technology, the variable compression ratio of utilizing motor that this technology can be best is with the specific power of further raising motor.

Yet, a problem is arranged, be exactly how in such layout, to design fuel to spray, it is simplified cost minimization, engine structure when keeping fuel efficiency most.

Chinese patent CN1904346 discloses a kind of fuel injector, a plurality of spray orifices distribute on the jet orifice plate, be divided into many groups, in working order down, the corresponding suction valve fuel feeding of each group spray orifice, the deviation angle of spray orifice and separation angle guarantee that the mist of oil of each group spray orifice ejection is in the cross section of corresponding suction valve oral area at the area that scatters of the suction valve oral area of correspondence.Design targetedly by separation angle, deviation angle and spray-cone angle to spray orifice, adopt porous partition to spray fuel supply method, make fuel oil spray to corresponding suction valve oral area respectively, greatly reduce wet wall effect, make fuel-oil atmozation more superior, combustion gas mixing is more even, and the combustion efficiency of motor improves greatly, and the operational efficiency of motor improves, oil consumption reduces.In addition, because the mixing of oil gas is more even, make its burning more abundant, reduced the discharging of tail gas, more environmental protection.This patent and the application will reach that the technique effect of the compression that improves engine structure balance and balanced motor and combustion stroke is different, and both described fields are also different, and the present invention is mainly used in free piston engine.

Chinese patent CN201517457U discloses a kind of fuel injector, comprise fuel nozzle, rotary fluid, oil nozzle junctor, fuel nozzle and oil nozzle junctor link into an integrated entity, rotary fluid is arranged in fuel nozzle inside, it is characterized in that: also comprise the deflector and the spring that are arranged in injector interior, rotary fluid is fixed by deflector, spring compression successively, spring one end is resisted against on the shoulder of oil nozzle junctor endoporus, the other end is resisted against on the convex shoulder of deflector, thus rotary fluid is pressed abd fixed on the fuel nozzle; Above-mentioned oil sprayer, simple in structure, easy to assembly, the reliability height is difficult for knot carbon, the fuel oil spray application occasion of small flow in very suitable Stirling engine, the oil-fired boiler etc.There are bigger difference in the fuel injector concrete structure of this patent and the application's concrete structure, and described technical field is also different.

Summary of the invention

At the problems referred to above that existing free piston engine exists, the invention provides a kind of fuel injector of free piston engine of balance.

The technological scheme that the present invention adopts for achieving the above object is:

A kind of fuel injector of free piston engine, comprise the free piston engine of being formed by hydraulic pump body assembly, first cylinder assembly, second cylinder assembly, described first cylinder assembly is connected in a side of described hydraulic pump body assembly, and described second cylinder assembly is connected in the opposite side of described hydraulic pump body assembly; Described first cylinder assembly comprises first cylinder, the described first cylinder bearing of trend is parallel to axis of movement, described second cylinder assembly comprises second cylinder, the described second cylinder bearing of trend is parallel to axis of movement, is respectively equipped with inner carrier assembly and outer piston assembly in described first cylinder and described second cylinder; The casing wall extended surface of described first cylinder assembly is provided with the first fuel oil jetburner of first suction port, first relief opening and close described first suction port, first fuel injector is installed on the motor and its first nozzle is arranged in the described first fuel oil jetburner, makes can not be exposed in the extreme temperature and pressure at described first nozzle of initial part that burns; The casing wall extended surface of described second cylinder assembly is provided with the second fuel oil jetburner of second suction port, second relief opening and close described second suction port, second fuel injector is installed on the motor and its second nozzle is arranged in the described second fuel oil jetburner, makes can not be exposed in the extreme temperature and pressure at described second nozzle of initial part that burns.

The fuel injector of above-mentioned free piston engine, wherein, described inner carrier assembly comprises to be located at first inner carrier in the described first cylinder assembly cylinder and to be located at the second interior inner carrier of the described second cylinder assembly cylinder, described first inner carrier is connected with described hydraulic pump body assembly by inside connecting rod with described second inner carrier, and the end face of the end face of described first inner carrier and described second inner carrier is in the position away from described hydraulic pump body assembly; Described outer piston assembly comprises to be located at first outer piston in the described first cylinder assembly cylinder and to be located at the second interior outer piston of the described second cylinder assembly cylinder, described first outer piston is connected with described hydraulic pump body assembly by outside connecting rod with described second outer piston, form first firing chamber between described first inner carrier and the opposed layout of described first outer piston and the two-piston end face, form second firing chamber between described second inner carrier and the opposed layout of described second outer piston and the two-piston end face.

The fuel injector of above-mentioned free piston engine, wherein, described first suction port and described second suction port are arranged one respectively at least, and described first suction port and described second suction port are made up of little suction port in the form of a ring.

The fuel injector of above-mentioned free piston engine, wherein, described first fuel injector and described second fuel injector all have the angle of attack of 90 degree approximately, and described first fuel injector and described second fuel injector are respectively towards at least one suction port.

The fuel injector of above-mentioned free piston engine, wherein, also comprise a position transducer, described position transducer transmits the information of described inner carrier assembly and described outer piston assembly to control the shut-in time point of the described first fuel oil jetburner and the described second fuel oil jetburner to controller in real time.

Owing to adopted above-mentioned technology, the good effect that technique scheme compared with prior art has is:

1. injector assembly directly sprays into cylinder with fuel oil, can not be exposed in the extreme temperature and pressure at the initial part oil nozzle that burns.Therefore, the direct-injection system that is exposed in whole combustion strokes compared with oil nozzle just can the cheaper oil sprayer of user cost; 2. fuel oil directly sprays in the cylinder of a two stroke engine, does not use air inlet and exhaust valve.Yet, spraying into fuel oil by the time slow slightly before exhaust close, the fuel oil that motor is not fired minimizes and overflows relief opening, therefore before closing relief opening, does not allow fuel oil to arrive relief opening on the time; 3. utilizing mistization, hyposmosis sparger can allow fuel oil to form mist of oil at cylinder axis, avoid fuel oil to touch cylinder wall.Thereby impel oil gas to mix fully, especially be incorporated into the athletic meeting of gas port guiding air eddy and produce better effect; 4. can allow oil gas enter has a quite long incorporation time in the cylinder, thereby guarantees to have more uniform mixed oil and gas than the direct fuel-injection engine of other type.In addition, than traditional direct fuel-injection engine, fuel oil normally is injected in the cylinder under the lower pressure environment.

Description of drawings

Fig. 1 be a kind of free piston engine of the present invention piston stopper be applied in schematic representation on the opposed cylinder type free piston engine of opposed pistons;

Fig. 2 is the end view of the free piston engine of the piston stopper of a kind of free piston engine of the present invention among Fig. 1;

Fig. 3 is the plan view of second cylinder assembly of the free piston engine of the piston stopper of a kind of free piston engine of the present invention among Fig. 1;

Fig. 4 is the plan view of first cylinder assembly of the free piston engine of the piston stopper of a kind of free piston engine of the present invention among Fig. 1;

Fig. 5 is the side view of second cylinder assembly of the free piston engine of the piston stopper of a kind of free piston engine of the present invention among Fig. 1;

Fig. 6 is the side view of first cylinder assembly of the free piston engine of the piston stopper of a kind of free piston engine of the present invention among Fig. 1;

Fig. 7 is the sectional view of 5A-5A part among Fig. 3;

Fig. 8 is the sectional view of 5B-5B part among Fig. 4;

Fig. 9 is the sectional view of 6A-6A part among Fig. 5;

Figure 10 is the sectional view of 6B-6B part among Fig. 6;

Figure 11 is the hydraulic pump body assembly of free piston engine of the piston stopper of a kind of free piston engine of the present invention among Fig. 1 and the schematical top view of inner carrier assembly;

Figure 12 is the hydraulic pump body assembly of free piston engine of the piston stopper of a kind of free piston engine of the present invention among Fig. 1 and the bottom schematic view of inner carrier assembly;

Figure 13 is the cylinder liner schematic representation of the free piston engine of the piston stopper of a kind of free piston engine of the present invention among Fig. 1;

Figure 14 is the hydraulic circuit schematic representation of the free piston engine of the piston stopper of a kind of free piston engine of the present invention among Fig. 1;

Figure 15 is the circuit diagram of the free piston engine of the piston stopper of a kind of free piston engine of the present invention among Fig. 1;

Figure 16 is the process status figure of fuel injector injected fuel in the motor of a kind of free piston engine of the present invention among Fig. 1.

Embodiment

The invention will be further described below in conjunction with the drawings and specific embodiments, but not as restriction of the present invention.

The fuel injector of a kind of free piston engine of the present invention shown in Fig. 1-16, comprise by hydraulic pump body assembly 12, first cylinder assembly 14, the free piston engine 10 that second cylinder assembly 16 is formed, free piston engine 10 is not only stored the energy of the pressure fluid form of motor generation, and can start with the partial pressure fluid, sometimes can help the balance controlling the running of motor and keep motor, first cylinder assembly 14 is connected in a side of hydraulic pump body assembly 12, and second cylinder assembly 16 is connected in the opposite side of hydraulic pump body assembly 12; First cylinder assembly 14 comprises first cylinder, the first cylinder bearing of trend is parallel to axis of movement, second cylinder assembly 16 comprises second cylinder, the second cylinder bearing of trend is parallel to axis of movement, is respectively equipped with inner carrier assembly 200 and outer piston assembly 250 in first cylinder and second cylinder; Inner carrier assembly 200 comprises the inner carrier that is fixed on the push rod 240 that passes hydraulic pump body assembly 12, the top of inner carrier is away from hydraulic pump body assembly 12, outer piston assembly 250 comprises wrist pin, pull bar and outer piston, outer piston is connected with pull bar by wrist pin, and the top of outer piston is respectively towards inner carrier.

Further, first cylinder assembly 14 has comprised first water jacket 18, is installed on the described hydraulic pump body assembly 12.There is one above first water jacket 18 near the first waste gas spiral outlet 20 of hydraulic pump body assembly 12.The first waste gas spiral outlet, 20 inside have one around the internal exhaust passages 22 of first water jacket 18, and internal exhaust passages 22 extends radially outward first exhaust flange 24.Exhaust flange 24 is connected with the vent systems (not shown), can export waste gas during the engine running.Vent systems can be the type of any hope, as long as it can handle and take away waste gas fully.For example, it can comprise a gas exhaust manifold, a baffler, a catalyst, a pressurized machine, the perhaps combination of these parts and other possibility assemblies.

Further, there is one above first water jacket 18 near the cooling liquid entrance 26 of hydraulic pump body assembly 12, and extends to the cooling channel 28 that an annular is extended.Cooling liquid entrance 26 is connected on the cooling liquid cooling system (not shown), this cooling system can comprise for example heat exchanger, shift the radiator of heat from engine coolant, water pump by cooling system pumping cooling liquid, interior temperature transducer and the flow control valve of temperature range that makes cooling liquid maintain a hope, cooling line between the component extends, perhaps the combination of these parts and other possibility assemblies.This cooling system can be the engine-cooling system of any kind wanted, as long as can take away suitable heat from motor.

Further, from the first waste gas spiral outlet, 20 1 sides, the other end of first water jacket 18 is the air inlet rings 30 that annular is extended, and its inside is intake duct 31.Near on air inlet ring 30, the first water jacket 18 an oil sprayer boss 32 is arranged, the inside is equipped with first oil sprayer 34.First oil sprayer 34 is connected with a controller 35, provides a signal to decide oil spout constantly and injection duration by controller 35.First oil sprayer 34 also is connected with oily rail 37, and oily rail 37 only shows schematic representation to 34 supplies of first oil sprayer from oil-fired system 39() next fuel oil.Oil-fired system 39 can comprise, fuel tank for example, and fuel pump leads to the fuel pipe of oily rail 37, perhaps the combination that these and other may assemblies.The oil-fired system 39 of any kind is as long as can provide enough fuel oils to accept to first oil sprayer 34 under predetermined pressure.Oil rail 37 preferably has a fuel pressure transmitter, and is connected with controller 35.Controller 35 is preferably powered by the electrical system that contains the battery (not shown), the energy drives that generator or alternator are preferably exported by motor, or other reliable power supplys are supplied with.When controller 35 when being single, as required, it can comprise the electronic processors of a plurality of communications each other.

Further, between the first waste gas spiral outlet 20 and air inlet ring 30, a pressure transducer installation base 36 is arranged on first water jacket 18, the inside is equipped with the first cylinder pressure sensor 38.The first cylinder pressure sensor 38 is connected with controller 35.Oil sprayer boss 32 and pressure transducer installation base 36 pass first water jacket 18 and extend to main aperture 40, increase the length of first water jacket 18 like this.Cooling passage 28, internal exhaust passages 22 and air inlet ring 30 all communicate with main aperture 40.

Further, first cylinder assembly 14 has also comprised first cylinder sleeve 42, and it is press-fited and pass the main aperture 40 of first water jacket 18.First cylinder sleeve 42 has a columniform main aperture to be defined as the first cylinder cylinder hole 44.The central axis in the first cylinder cylinder hole 44 is along the direction of axial-movement.First cylinder sleeve 42 also comprises a series of relief openings 46 that circularize arrangement, and they are between the internal exhaust passages 22 of the first cylinder cylinder hole 44 and first water jacket 18, and are communicated with both.

Further, near having one above relief opening 46, the first water jacket 18 near the cooling channel 28 of first cylinder sleeve 42.This cooling channel 28 with a series ofly be spaced apart, spiral muscle 48 is connected, muscle 48 extends radially outward from the outer surface of first cylinder sleeve 42, and near the main aperture 40 of first water jacket 18, has formed a series of cylinder bodies cooling channel 50.

Further, in these muscle 48 the insides, a cylinder body pressure tap 52 that extends to surface sensor installation base 36 on first water jacket 18 from the first cylinder cylinder hole 44 is arranged.First cylinder pressure sensor 38 can be entered in the first cylinder cylinder hole 44, but first cylinder pressure sensor 38 need sealing, prevents that engine coolant from entering. Oil injector hole 54 and 32 alignment of oil sprayer boss are passed muscle 48 and are entered the first cylinder cylinder hole 44.First oil sprayer 34 can be entered in the first cylinder cylinder hole 44 by the direct injection fuel oil.

Further, the suction port 56 that first cylinder sleeve 42 also has a series of edges circumferentially to be spaced aligns with air inlet ring 30 on first water jacket 18, and leads to the first cylinder cylinder hole 44.Suction port 56 is near oil injector holes 54, compared with oil injector hole 54, and at interval farther of exhaust port 46.Oil injector hole 54 is angled, and oil nozzle 55 just is sprayed to fuel oil 57 on the direction of suction port 56 so.Adjacent suction port 56 is a series of oil mist holes 58 that center on first cylinder sleeve 42 spaced apart in addition.

Further, first cylinder assembly 14 also comprises first air cavity 60.First air cavity 60 is installed on first cylinder sleeve 42, near the air inlet ring 30 on first water jacket 18.An oil inlet pipe 62 passes first air cavity 60 and communicates with annular mist of oil chamber 64.Annular mist of oil chamber 64 is around the oil mist holes 58 on first cylinder sleeve 42.Oil inlet pipe 62 communicates with a mist of oil producer (not shown), and the mist of oil producer communicates with the machine oil source, provides gas mixture to annular mist of oil chamber 64.The machine oil source can be the part of oil supply system (not shown).Oil supply system can comprise for example combination of oil pump, oil filter, machine oil cooler, oil sump, the pipeline road that is used for transmission machine oil or these parts and other possible assemblies.When engine running, oil supply system can fully filter machine oil with other component, and to the enough lubricant oil of motor supply.

Further, near and around the air ring 66 that also has of first cylinder sleeve 42.Air ring 66 communicates with cylinder body cooling channel 50, and communicates with the coolant outlet 68 that passes first air cavity 60.Coolant outlet 68 communicates with cooling system (not shown) above-mentioned.A pair of pull bar passage 70 and a gas-entered passageway 72 are arranged in first air cavity 60, and they communicate with air inlet ring 30 on first water jacket 18.

Further, first cylinder assembly 14 is also integrated first scavenging pump 74.First scavenging pump 74 has a scavenging pump housing 76 that is installed on first air cavity 60, is positioned at the end of first cylinder sleeve 42.Scavenging pump housing 76 has a main pump chamber 78, communicates with suction chamber 82 by the suction port 80 above it, communicates with discharge chamber 86 by air outlet 84.Main pump chamber 78 is columniform, has the cross section of substantially elliptical.

Further, an air inlet reed valve ASSY 88 and a scavenging pump Intake Cover 90 are installed on the suction chamber 82.A suction port 92 that communicates with the gas handling system (not shown) is arranged on the Intake Cover 90.Gas handling system can comprise intake manifold, air control shutter, air flow sensor, air temperature sensor, the air-strainer that for example communicates with turbosupercharger or mechanical supercharger, perhaps the combination of these parts and other possibility assemblies.Gas handling system can be the system of any kind, as long as under certain operating mode, can supply the air of requirement to suction port 92 under required pressure.

Further, the leaf valve 94 on the air inlet reed valve ASSY 88 can make the air-flow in the Intake Cover 90 enter suction chamber 82, but stops air-flow to flowing in the other direction.Give vent to anger reed valve ASSY 89 and a scavenging pump are given vent to anger and are covered 91 and be installed on the discharge chamber 86.Giving vent to anger to cover has a gas-entered passageway 93 in 91, the air that the reed valve ASSY 89 of giving vent to anger is discharged enters in the air inlet ring 31 by the gas-entered passageway 72 in first air cavity 60.The reed valve ASSY 89 interior leaf valves 95 of giving vent to anger can make the air-flows in the discharge chamber 86 enter in the gas-entered passageway 93, but stop air-flow to flowing in the other direction.

Further, second cylinder assembly 16 has second water jacket 118 that is installed on the hydraulic pump body assembly 12.Second water jacket 118 has one near the second waste gas spiral outlet 120 of hydraulic pump body assembly 12.The second waste gas spiral outlet, 120 inside are the internal exhaust passages 122 around second water jacket 118, and internal exhaust passages 122 extends radially outward second exhaust flange 124.Second exhaust flange 124 communicates with described vent systems (not shown).Have one on second water jacket 118 near the cooling liquid entrance 126 of hydraulic pump body assembly 12, cooling liquid entrance 126 communicates with the cooling channel 128 that annular is extended.Cooling liquid entrance 126 (not shown) that communicates with cooling system.

Further, from the second waste gas spiral outlet, 120 1 sides, the other end of second water jacket 118 is the air inlet rings 130 that annular is extended, and its inside is intake duct 131.Near on air inlet ring 130, the second water jacket 118 an oil sprayer boss 132 is arranged, the inside is equipped with second oil sprayer 134.Second oil sprayer 134 is connected with controller 35, provides a signal to decide oil spout constantly and injection duration by controller 35.Second oil sprayer 134 also is connected with oily rail 37, the fuel oil of oily rail 37 to 134 supplies of second oil sprayer from oil-fired system 39.Oil-fired system 39 can comprise, fuel tank for example, and fuel pump leads to the fuel pipe of oily rail 37.Oil rail 37 preferably has one to be connected fuel pressure transmitter 141 with controller 35.

Further, between the second waste gas spiral outlet 120 and the air inlet ring 130, a pressure transducer installation base 136 is arranged on second water jacket 118, the inside is equipped with the second cylinder pressure sensor 138.Oil sprayer boss 132 and pressure transducer installation base 136 pass second water jacket 118 and extend to main aperture 140, have increased the length of second water jacket 118 like this.Cooling channel 128, internal exhaust passages 122 and air inlet ring 130 all communicate with main aperture 140.

Further, second cylinder assembly 16 has also comprised second cylinder sleeve 142, and it is press-fited and pass the main aperture 140 of second water jacket 118.Second cylinder sleeve 142 has a columniform main aperture to be defined as the second cylinder cylinder hole 144.The central axis in the second cylinder cylinder hole 144 is along the direction of axial-movement.Second cylinder sleeve 142 also comprises a series of relief openings 146 that circularize arrangement, and they are between the internal exhaust passages 122 of the second cylinder cylinder hole 144 and second water jacket 118, and are communicated with both.

Further, near having one above relief opening 146, the second water jacket 118 near the cooling channel 128 of second cylinder sleeve 142.This cooling channel 128 with a series ofly be spaced apart, spiral muscle 148 is connected, muscle 148 extends radially outward from the outer surface of second cylinder sleeve 142, and near the main aperture 140 of second water jacket 118, has formed a series of cylinder bodies cooling channel 150.In these muscle 148 the insides, a cylinder body pressure tap 152 that extends to surface sensor installation base 136 on second water jacket 118 from the second cylinder cylinder hole 144 is arranged.Second cylinder pressure sensor 138 can be entered in the second cylinder cylinder hole 144, but second cylinder pressure sensor 138 need sealing, prevents that engine coolant from entering.Oil injector hole and 132 alignment of oil sprayer boss are passed muscle 148 and are entered the second cylinder cylinder hole 144.Second oil sprayer 134 can be entered in the second cylinder cylinder hole 144 by the direct injection fuel oil.

Further, the suction port 156 that second cylinder sleeve 142 also has a series of edges circumferentially to be spaced aligns with air inlet ring 130 on second water jacket 118, and leads to the second cylinder cylinder hole 144.Near suction port 156, the oil mist holes 158 that has a series of annulars to be spaced around second cylinder sleeve 142.

Further, second cylinder assembly 16 also comprises second air cavity 160.Second air cavity 160 is installed on second cylinder sleeve 142, near the air inlet ring 130 on second water jacket 118.An oil inlet pipe 162 passes second air cavity 160 and communicates with annular mist of oil chamber 164.Annular mist of oil chamber 164 is around the oil mist holes 158 on second cylinder sleeve 142.Oil inlet pipe 162 communicates with a mist of oil producer (not shown), provides gas mixture to annular mist of oil chamber 164.

Further, near and around the air ring 166 that also has of second cylinder sleeve 142.Air ring 166 communicates with cylinder body cooling channel 150, and communicates with the coolant outlet 168 that passes second air cavity 160.Coolant outlet 168 communicates with cooling system (not shown) above-mentioned.A pair of pull bar passage 170 and a gas-entered passageway 172 are arranged in second air cavity 160, and they communicate with air inlet ring 130 on second water jacket 118.

Further, second cylinder assembly 16 is also integrated second scavenging pump 174.Second scavenging pump 174 has a scavenging pump housing 176 that is installed on second air cavity 160, is positioned at the end of second cylinder sleeve 142.Scavenging pump housing 176 has a main pump chamber 178, communicates with suction chamber 182 by the suction port 180 above it, communicates with discharge chamber 186 by air outlet 184.Main pump chamber 178 is columniform, has the cross section of substantially elliptical.An air inlet reed valve ASSY 188 and a scavenging pump Intake Cover 190 are installed on the suction chamber 182.A suction port 192 that communicates with the intake manifold (not shown) is arranged on the Intake Cover 190.Intake manifold receives the air of coming from turbosupercharger or mechanical supercharger.Leaf valve 194 on the air inlet reed valve ASSY 188 can make the air-flow in the Intake Cover 190 enter suction chamber 182, but stops air-flow to flowing in the other direction.

Further, give vent to anger reed valve ASSY 189 and a scavenging pump are given vent to anger and are covered 191 and be installed on the discharge chamber 186.Giving vent to anger to cover has a gas-entered passageway 193 in 191, the air that the reed valve ASSY 189 of giving vent to anger is discharged enters in the air inlet ring 131 by the gas-entered passageway 172 in second air cavity 160.The reed valve ASSY 189 interior leaf valves 195 of giving vent to anger can make the air-flows in the discharge chamber 186 enter in the gas-entered passageway 193, but stop air-flow to flowing in the other direction.

Further, two cylinder assembly inside two piston assemblys are arranged, i.e. inner carrier assembly 200 and outer piston assembly 250.Inner carrier assembly 200 has a piston top 210 that is installed in first inner carrier, 202, the first inner carriers 202 in the first cylinder cylinder hole 44 towards the direction away from hydraulic pump body assembly 12, and rear end 211 is towards the direction near hydraulic pump body assembly 12.A very little gap is arranged between the outer surface of first inner carrier 202 and the first cylinder cylinder hole 44.Thus, the outer surface of first inner carrier 202 has three road piston ring grooves, and first road annular groove the inside is equipped with annular grooves the inside, compression ring 204, the second road and annular grooves the inside, compression ring 206, the three road is installed oil ring 208 is installed.Three all road rings are designed to certain size, make its outer surface be adjacent to the first cylinder cylinder hole, 44 inwalls, play the effect of sealing.

Further, first inner carrier 202 also has a series of holes 212 of extending vertically, and extend to piston top 210 from the rear end 211 of first inner carrier 202 in these holes.In each hole 212 a certain amount of sodium compound is housed, there is plug 214 end in hole 212, is used for the sealing sodium compound.

Further, inner carrier assembly 200 has a piston top 222 that is installed in second inner carrier, 220, the second inner carriers 220 in the second cylinder cylinder hole 144 towards the direction away from hydraulic pump body assembly 12, and rear end 223 is towards the direction near hydraulic pump body assembly 12.A very little gap is arranged between the outer surface of second inner carrier 220 and the second cylinder cylinder hole 144.Thus, the outer surface of second inner carrier 220 has three road piston ring grooves, and first road annular groove the inside is equipped with annular grooves the inside, compression ring 224, the second road and annular grooves the inside, compression ring 226, the three road is installed oil ring 228 is installed.Three all road rings are designed to certain size, make its outer surface be adjacent to the second cylinder cylinder hole, 144 inwalls, play the effect of sealing.

Further, second inner carrier 220 also has a series of holes 230 of extending vertically, and extend to piston top 222 from the rear end 223 of second inner carrier 220 in these holes.In each hole 230 a certain amount of sodium compound is housed, there is plug 232 end in hole 230, is used for the sealing sodium compound.

Further, the middle position of first inner carrier 202 has an axially extended hole 216, and the inside has the middle position of clamping bolt 218, the second inner carriers 220 that an axially extended hole 234 is arranged, and there is clamping bolt 226 the inside.Bolt 218 and 236 is by on the two ends that are threaded in push rod 240, and push rod 240 passes hydraulic pump body assembly 12.Push rod 240 two ends are separately fixed on first inner carrier 202 and second inner carrier 220, and first inner carrier 202 and second inner carrier 220 are synchronized with the movement along axial direction.The zone that has place's diameter to increase on the push rod 240 has formed an inner plunger 242.Inner plunger 242 is positioned at the neutral position of first inner carrier 202 and second inner carrier 220.

Further, inner carrier assembly 200 also contains first guide rod 244 and 245, two guide rods of second guide rod all pass hydraulic pump body assembly 12, and the rear end 211 and 223 of first inner carrier 202 and second inner carrier 220 is linked together.During engine running, first guide rod 244 and second guide rod 245 play the effect that prevents 200 rotations of inner carrier assembly.First guide rod 244 and above second guide rod 245 at least one position transducer is arranged when engine running, can be determined the axial position of inner carrier assembly 200.The mode of sensor sensing can adopt the form of first group of copper ring 246 being installed at first guide rod 244.Second group of copper ring 247 arranged above second guide rod 245.Position transducer on first guide rod 244 is when reading data, and second guide rod 245 can be used as the part of position correction sensor, to guarantee to read accurately the axial position of inner carrier assembly 200.

Further, have a piston top 254 that is positioned at first outer piston, 252, the first outer pistons 252 in the first cylinder cylinder hole 44 to push up 210 towards the piston of first inner carrier 202 on the outer piston assembly 250, rear end 256 is towards the main pump chamber 78 of first scavenging pump.A very little gap is arranged between the outer surface of first outer piston 252 and the first cylinder cylinder hole 44.Thus, the outer surface of first outer piston 252 has three road piston ring grooves, and first road annular groove the inside is equipped with annular grooves the inside, compression ring 258, the second road and annular grooves the inside, compression ring 260, the three road is installed oil ring 262 is installed.Three all road rings are designed to certain size, make its outer surface be adjacent to the first cylinder cylinder hole, 44 inwalls, play the effect of sealing.

Further, first piston pin 264 is installed on the rear end 256 of first outer piston 252.First piston pin 264 and first outer piston 252 move together, become the part of first outer piston 252.An oval part 266 is arranged, the main pump chamber 78 inwall sliding contacts of it and first scavenging pump 74 and sealing on the first piston pin 264.It is little that the path of oval part 266 pushes up 254 diameters than the piston of first outer piston 252 a little, but that 254 diameters are obviously pushed up than the piston of first outer piston 252 in the big footpath of oval part 266 is big.The big footpath direction along oval part 266 of first rod head 268 and second rod head 269 is positioned at the radially outer position of first outer piston, 252 outsides.

Further, guide rod boss 270 is positioned at the central position of first piston pin 264, and this central position is on the axis of first outer piston, 252 motions.The 3rd guide rod 271 is fixed on the first scavenging pump housing 76, and extends out therefrom.The outer surface of the 3rd guide rod 271 is cylindrical, and it is in the central position in cylinder hole, and axis is parallel with axis of movement.The outer surface of the 3rd guide rod 271 is enclosed within guide rod boss 270 inside, and guide rod boss 270 can be slided along the 3rd guide rod 271.Because the 3rd guide rod 271 is fixed, so it can accurately be located with respect to the position in the first cylinder cylinder hole 44.Therefore, the 3rd guide rod 271 can make the position of first piston pin 264, first outer piston 252 can accurate in locating with respect to the position in the first cylinder cylinder hole 44.

Further, during the engine running, guide rod boss 270 slides at the 3rd guide rod 271, makes first outer piston 252 correct direction of maintenance during the to-and-fro motion the first cylinder cylinder hole 44 in, make have only compression ring 258, compression ring 260 contacts with the first cylinder cylinder hole 44 with oil ring 262.Owing to have only compression ring 258, compression ring 260 and oil ring 262 and guide rod boss 270 and other part surface sliding contacts in the time of motion, and first outer piston, 252 outer surfaces contact with the first cylinder cylinder hole 44 not, so the frictional force that produces is very little.

Further, have a piston top 276 that is positioned at second outer piston, 275, the second outer pistons 275 in the second cylinder cylinder hole 144 to push up 222 towards the piston of second inner carrier 220 on the outer piston assembly 250, rear end 277 is towards the main pump chamber 178 of second scavenging pump.A very little gap is arranged between the outer surface of second outer piston 275 and the second cylinder cylinder hole 144.Thus, the outer surface of second outer piston 275 has three road piston ring grooves, and first road annular groove the inside is equipped with annular grooves the inside, compression ring 278, the second road and annular grooves the inside, compression ring 279, the three road is installed oil ring 280 is installed.Three all road rings are designed to certain size, make its outer surface be adjacent to the second cylinder cylinder hole, 144 inwalls, play the effect of sealing.

Further, second wrist pin 282 is installed on the rear end 277 of second outer piston 275.It is oval part 283 that an outside is arranged on second wrist pin 282, the main pump chamber 178 inwall sliding contacts of it and second scavenging pump 174 and sealing.The path of oval part 283 diameter than the piston top 276 of second outer piston 275 a little is little, but that 276 diameter is obviously pushed up than the piston of second outer piston 275 in the big footpath of oval part 283 is big.The 3rd rod head 284 and four-pull-rod head 285 are positioned at the radially outer position of first outer piston, 275 outsides along the big footpath direction of oval part 283.

Further, guide rod boss 286 is positioned at the central position of second wrist pin 282, and the 4th guide rod 287 is fixed on the second scavenging pump housing 176, and extends out therefrom.The outer surface of the 4th guide rod 287 is cylindrical, and it is in the central position in cylinder hole, and axis is parallel with axis of movement.Guide rod boss 286 can slide along the 4th guide rod 287.Because the 4th guide rod 287 is fixed with respect to the second cylinder cylinder hole 144, therefore, the 4th guide rod 287 can make the position of second wrist pin 282, second outer piston 275 can accurate in locating with respect to the position in the second cylinder cylinder hole 144.During the engine running, guide rod boss 286 slides at the 4th guide rod 287, makes second outer piston 275 correct direction of maintenance during the to-and-fro motion the second cylinder cylinder hole 144 in, make compression ring 278 is only arranged, compression ring 279 contacts with the second cylinder cylinder hole 144 with oil ring 280.So just make and minimum friction forces simultaneously piston is had suitable leading role.

Further, also formed the part of position transducer assembly 288 on the 4th guide rod 287, position transducer assembly 288 comprises a rodmeter 289, has a location index 290 above the rodmeter 289 at least, is fixed on second outer piston 275 also mobile thereupon.Sensor 291 is installed near the rodmeter 289, and passes the second scavenging pump housing 176, and by electronic connector 292, sensor 291 is connected with controller 35.Controller 35 can utilize the signal of sensor 291 outputs to judge position and the speed of outer piston assembly 250.

Further, outer piston assembly 250 also contains first pull bar 293 and second pull bar 294.First rod head 268 on first pull bar, the 293 connection first piston pins 264 and the 3rd rod head 284 on second wrist pin 282.Because first piston pin 264 and second wrist pin 282 are oval-shaped, first pull bar 293 can make their motions of paralleling to the axis that combines, and does not influence the work of cylinder.

Further, first pull bar 293 has the bigger zone of an end diameter, has formed first outer plunger 295.First outer plunger 295 is positioned on the hydraulic pump body assembly 12, is in the neutral position of first piston pin 264 and second wrist pin 282.The first pull bar sleeve 272 is enclosed within first pull bar, 293 outsides, is between hydraulic pump body assembly 12 and first water jacket 18, and the second pull bar sleeve 274 is enclosed within on first pull bar 293, is between hydraulic pump body assembly 12 and second water jacket 118.The first pull bar sleeve 272 and the second pull bar sleeve 274 guarantee that first pull bar 293 is enclosed in the engine components the inside completely, stop the pollutant contact and interfere the running of first pull bar 293.

Further, second rod head 269 on second pull bar, the 294 connection first piston pins 264 and the four-pull-rod head 285 on second wrist pin 282.Second pull bar 294 has one section zone that diameter is bigger, has formed second outer plunger 296.Second outer plunger 296 is positioned on the hydraulic pump body assembly 12, is in the neutral position of first piston pin 264 and second wrist pin 282.The 3rd pull bar sleeve 273 is enclosed within second pull bar, 294 outsides, be between hydraulic pump body assembly 12 and first water jacket 18, the four-pull-rod sleeve 281 of a band position transducer is enclosed within on second pull bar 294, is between hydraulic pump body assembly 12 and second water jacket 118.The 3rd pull bar sleeve 273 and four-pull-rod sleeve 281 guarantee that second pull bar 294 is enclosed in the engine components the inside completely, stop the pollutant contact and interfere the running of second pull bar 294.

Further, also be installed in copper ring 298 above it, spaced apart above second pull bar 294, and be positioned at four-pull-rod sleeve 281 the insides for position sensing.Four-pull-rod sleeve 281 the insides comprise one near the sensor unit 297 of copper ring 298.Sensor unit 297 is connected with controller 35, is used for surveying the position of copper ring 298.Controller 35 utilizes the signal of sensor unit 297 outputs to proofread and correct another sensor 291, therefore can guarantee accurately to survey position and the speed of outer piston assembly 250.

Further, in order to ensure the service performance of motor 10 the bests, motor need keep balance.In order to make motor keep balance, the gross mass of outer piston assembly 250, namely with the gross mass of all parts of first outer piston 252 and the motion of second outer piston 275, the gross mass that must be equal to inner carrier assembly 200 is namely with the gross mass of all parts of first inner carrier 202 and the motion of second inner carrier 220.In addition, for balanced engine, first outer plunger 295 of the hydraulic pressure area of the inner plunger 242 of push rod 240 and first pull bar 293 and second pull bar 294 and total hydraulic pressure area of second outer plunger 296 equates and the hydraulic pressure area of first outer plunger 295 also will equate with the hydraulic pressure area of second outer plunger 296.Thereby different parts can select suitable material to guarantee heat resistance and strength characteristics on inner carrier assembly 200 and the outer piston assembly 250, guarantee the mass balance of assembly simultaneously.For example, first inner carrier 202, second inner carrier 220 and push rod 240 can cylinder iron be made, first pull bar 293 and second pull bar 294 also can cylinder iron be made, first outer piston 252 and second outer piston 275 can be used the aluminum alloy manufacturing, and the first piston pin 264 of elliptical shape and second wrist pin 282 can be made with steel.If desired, other suitable material also can be used.

Further, hydraulic pump body assembly 12 is between first cylinder assembly 14 and second cylinder assembly 16, and it comprises one with the pump housing 302 of steel, has formed a lot of hydraulic port and passage such as cooling passage, lubricating oil sump and passage etc. above the pump housing 302.

Further, the push-rod hole 304 that has a push rod 240 to pass on the pump housing 302.The Sealing annular of inner plunger 242 is around push-rod hole 304.The two ends of push-rod hole 304 also seal push rod 240 and an end adopts seal plug 309 to seal.These Sealings make a side of inner plunger 242 form an interior pumping chamber 306, and opposite side has formed coupling pumping chamber 308 in.

Further, also have first tie rod hole 310 that first pull bar 293 passes on the pump housing 302, reach second tie rod hole 312 that second pull bar 294 passes.The Sealing of first outer plunger 295 circumferentially circumferentially centers on second tie rod hole 312 around the Sealing of first tie rod hole, 310, the second outer plunger 296.Each end of first tie rod hole 310 all is designed to the shape being convenient to seal, and an end of first pull bar 293 utilizes seal plug 311 to seal.First tie rod hole 310 and first pull bar 293 have formed pump chamber 314 outside first in a side of first outer plunger 295 together, have formed coupling pump chamber 316 outside first at opposite side.Each end of second tie rod hole 312 all is designed to the shape being convenient to seal, and an end of second pull bar 294 utilizes seal plug 313 to seal.Second tie rod hole 312 and second pull bar 294 have formed pump chamber 318 outside second in a side of second outer plunger 296 together, have formed coupling pump chamber 320 outside second at opposite side.

Further, interior coupling pumping chamber 308 and the first outer coupling pump chamber 316 are communicated with by the first interconnection passage 322.In addition, interior coupling pumping chamber 308 and the second outer coupling pump chamber 320 are communicated with by the second interconnection passage 323, so interior coupling pumping chamber 308, the first outer coupling pump chamber 316 and the second outer pump chamber 320 that is coupled are in the state that is interconnected.

Further, low-pressure channel 324 and a flow controller 326 make the second interconnection passage 323 be communicated with the first coupling modulating valve 328.The first coupling modulating valve 328 is communicated with the low pressure oil storage pool 330 of hydraulic system 329 1 sides.The first coupling modulating valve 328 can switching position, makes fluid enter low pressure oil storage pool 330 from the second interconnection passage 323, can also switch a position, stops fluid to pass through.High-pressure channel 332 and a flow controller 334 make the first interconnection passage 322 be communicated with the second coupling modulating valve 336.The second coupling modulating valve 336 is communicated with the high pressure oil storage pool 338 of hydraulic system 329 1 sides.The second coupling modulating valve 336 can switching position, makes fluid enter the first interconnection passage 322 from high pressure oil storage pool 338, can also switch a position, stops fluid to pass through.The first coupling modulating valve 328 is connected with controller 35 with the second coupling modulating valve 336, and by its control.

Further, the resonator passage 340 on the pump housing 302 has connected the second interconnection passage 323 and Helmholtz resonator 342.Helmholtz resonator 342 configures, be used for damper fluid when mobile back and forth in the outer coupling of interior coupling pumping chamber's 308, first outer coupling pump chamber 316 and second pump chamber 320 by the first interconnection passage 322 and the second interconnection passage 323 generation pulse.If desired, Helmholtz resonator 342 can remove from motor 10.

Further, the first interconnection passage 322 and the second interconnection passage 323, and the hydraulic element that are connected with them have formed an oil hydraulic circuit, and hydraulic pressure makes the motion of inner carrier assembly 200 and outer piston assembly 250 synchronous.Because, when the first coupling modulating valve 328 and the second coupling modulating valve 336 when closing, the interior pumping chamber 308 that is coupled, the first outer coupling pump chamber 316 and the second outer inside that is coupled pump chamber 320 and the first interconnection passage 322 and the second interconnection passage 323 have been full of compressed fluid (for example hydraulic oil), and this volume remains unchanged.Every straight line moves a certain distance, and the fluid volume variable quantities in the inner plunger of push rod 240 242 are in first outer plunger 295 of first pull bar 293 and second pull bar 294 and second outer plunger 296 2 times of the fluid volume variable quantity separately.Therefore, the 1mm if inner carrier assembly 200 moves right, the fluid that flows out from interior pumping chamber 308 the insides that are coupled makes outer piston assembly 250 be moved to the left 1mm, so that the first outer coupling pump chamber 316 and the second outer pump chamber 320 that is coupled receive these fluids.This can guarantee, even without mechanically fixedly inner carrier assembly 200 and the motion of outer piston assembly 250, they also can carry out relative movement accurately.Therefore, inner carrier assembly 200 and outer piston assembly 250 can arrive top dead center and lower dead center simultaneously.

Further, if Sealing is revealed the stereomutation that makes the Coupler inner fluid, as required, the first coupling modulating valve 328 and the second coupling modulating valve 336 can increase or reduce the fluid volume of Coupler the inside.Though above-described be make inner carrier assembly 200 and the hydraulic system of outer piston assembly 250 interlock, if other mechanical devices can guarantee inner carrier assembly 200 and 250 relative movement of outer piston assembly, also can use.

Further, a pair of pump housing 302 bottoms that are positioned at are arranged on the hydraulic pump body assembly 12, pass the oil inlet pipe 344 and 345 that the pump housing 302 communicates with oil sump 346.A lot of movement parts are all on oil sump 346 tops on the hydraulic pump body assembly 12 so that can splash lubrication movement parts, particularly first inner carrier 202, second inner carrier 220 part of sliding along the first cylinder cylinder hole 44 and the second cylinder cylinder hole 144.Also has an oil return outlet 348 on the oil sump 346. Oil inlet pipe 344 and 345 and oil return outlet 348 all communicate with the oil supply system (not shown).When first inner carrier 202 and 220 to-and-fro motion of second inner carrier, oil sump 346 also can make the movement that the air of piston rear end can be back and forth.

Further, cooling liquid entrance 350 is positioned at the bottom of the pump housing 302, communicates with a series of pump housing 302 cooling channels 352 everywhere that are distributed in, and communicates with two cooling liquid outlets 354 that are installed in the pump housing 302 tops again.Cooling liquid entrance 350 and cooling liquid outlet 354 communicate with the cooling system (not shown).Cooling liquid is in the pump housing 302 internal flows, and is not overheated with movement parts during guaranteeing engine running.

Further, hydraulic pump body assembly 12 also comprises a low pressure oil rail 356 that is installed in the pump housing 302 tops, and the low pressure oil rail port 358 on the low pressure oil rail 356 communicates with low pressure oil storage pool 330 by hydraulic pipe line.Low pressure oil rail 356 and three groups of low pressure check valve, namely inner one-way valve 360, the first outside one-way valve 362, the second outside one-way valve 363 communicate.Inner one-way valve 360 communicates with internal pump chamber 306 by a passage 364, and 360 on inner one-way valve allows fluid to flow to internal pump chamber 306 from low pressure oil rail 356.The first outside one-way valve 362 communicates with the first outside pump chamber 314 by passage 365, and 362 on the first outside one-way valve allows fluid to flow to the first outside pump chamber 314 from low pressure oil rail 356.The second outside one-way valve 363 communicates with the second outside pump chamber 318 by passage 366, and 363 on the second outside one-way valve allows fluid to flow to the second outside pump chamber 318 from low pressure oil rail 356.Inner one-way valve 360 contains four independent valves, and the first outside one-way valve 362 and the second outside one-way valve 363 respectively have two valves, if desired, can adopt the valve of varying number.But the circulation area of inner one-way valve 360 must be the first outside one-way valve 362 and the second outside one-way valve 363 2 times of circulation area separately, because the pumping capacity of inner plunger 242 must be first outer plunger 295 and second outer plunger 296 2 times of pumping capacity separately.

Further, the pump housing 302 bottoms are equipped with high pressure oil rail 368, and the high pressure oil rail port 369 on the high pressure oil rail 368 communicates with high pressure oil storage pool 338 by hydraulic pipe line.High pressure oil rail 368 and three groups of high pressure one-way valves, namely inner one-way valve 370, the first outside one-way valve 371, the second outside one-way valve 372 communicate.Inner one-way valve 370 communicates with internal pump chamber 306 by a passage 373, and 370 permissions of inner one-way valve fluid pump chamber 306 internally flows to high pressure oil rail 368.The first outside one-way valve 371 communicates with the first outside pump chamber 314 by passage 374, and 371 on the first outside one-way valve allows fluid to flow to high pressure oil rail 368 from the first outside pump chamber 314.The second outside one-way valve 372 communicates with the second outside pump chamber 318 by passage 375, and 372 on the second outside one-way valve allows fluid to flow to high pressure oil rail 368 from the second outside pump chamber 318.Equally, the circulation area of inner one-way valve 370 must be the first outside one-way valve 371 and the second outside one-way valve 372 2 times of circulation area separately.

Further, pressure transducer 376 is installed on the low pressure oil rail 356, for detection of the pressure of low pressure oil rail 356 inner fluids.Equally, pressure transducer 377 is installed on the high pressure oil rail 368, for detection of the pressure of high pressure oil rail 368 inner fluids.Pressure transducer 376 all is connected with controller 35 with 377, is used for receiving and the processing pressure signal.

Further, a hydraulic starting control valve 379 is installed on the pump housing 302, and the place of close low pressure oil rail 356.The hydraulic starting control valve 379 here just schematically shows.Hydraulic starting control valve 379 is connected with the pump housing 302 by four ports on the pump housing 302, and four ports are respectively high pressure port 380, low-pressure port 381, internal pump chamber port 382, outside pump chamber port 383.High pressure port 380 communicates with high pressure oil rail 368 by a fluid passage, and low-pressure port 381 communicates with low pressure oil rail 356 by a fluid passage.Internal pump chamber port 382 opens by first and overflow ducts 384 communicates with internal pump chamber 306, and outside pump chamber port 383 opens by second and overflow ducts 385 communicates with the first outside pump chamber 314 and the second outside pump chamber 318.

Further, hydraulic starting control valve 379 can make high pressure port 380 be communicated with internal pump chamber port 382, and low-pressure port 381 is communicated with outside pump chamber port 383 simultaneously.Hydraulic starting control valve 379 can also make low-pressure port 381 be communicated with internal pump chamber port 382, and high pressure port 380 is communicated with outside pump chamber port 383 simultaneously.Under the third state, passage between hydraulic starting control valve 379 obstruction high pressure port 380, low-pressure port 381 and internal pump chamber port 382, the outside pump chamber port 383.Controller 35 can be controlled the working state of hydraulic starting control valve 379.

Further, hydraulic pump body assembly 12 can also comprise piston stopper, and it is fixed on each end of travel maximum distance apart of piston.Because piston motion determines by equilibrium of forces, so what need for free-piston engine may be above-mentioned back-up ring rather than path.The either side first that the piston stopper of inner carrier assembly 200 preferably includes the inner plunger 242 of push rod 240 at interval is step 388 radially, and mate first radially step part 389 be positioned at each end of the push-rod hole 304 of the pump housing 302 and seal plug 309.First radially step 388 first radially the position of step part 389 will determine the range of inner carrier assembly 200 in either direction.If first radially step 388 be positioned at first step part 389 places radially, piston on this direction with stop motion.

Further, the piston stopper of outer piston assembly 250 preferably also is included at interval the radially step 390 and 391 respectively of either side on first outer plunger 295 of first pull bar 293 and second pull bar 294 and second outer plunger 296.The pump housing 302 and seal plug 311 and 313 similar to inner carrier assembly 200 will comprise and mate radially step part 392 and 393, and they are positioned at the other end of first tie rod hole 310 and second tie rod hole 312 separately.

Further, perhaps also can cancel piston stopper.Adopt this structure, the piston head 210 of first inner carrier 202 that clashes into the piston head 254 of first outer piston 252 will be as the back-up ring of a direction, will be as the back-up ring of another direction and clash into the piston head 222 of second inner carrier 220 of the piston head 276 of second outer piston 275.Though may not be very good at first view, piston crown has big relatively contact surface area, and it is very high to rise before collision as the pressure in the cylinder of back-up ring with piston, thereby reduces the speed when clashing into.

Further, hydraulic pump body assembly 12 also comprises a pair of position transducer.Primary importance sensor 395 is installed on the pump housing 302, be positioned at first group of copper ring 246 part on first guide rod 244 near.Second place sensor 396 is installed on the pump housing 302, be positioned at second group of copper ring 247 part on second guide rod 245 near.Primary importance sensor 395, second place sensor 396 are connected with controller 35, and provide position signal to it.Controller 35 obtains signal from primary importance sensor 395, thereby can learn position and the speed of inner carrier assembly 200.The signal that second place sensor 396 provides is used for proofreading and correct the signal of primary importance sensor 395.

Further, the working principle of motor, because motor is free piston engine 10, the motion of piston is to be decided by the equilibrium of forces that acts on inner carrier assembly 200 and the outer piston assembly 250.Significant feature power has: the in-cylinder pressure in the opposed cylinder first cylinder cylinder hole 44 and the second cylinder cylinder hole 144, the frictional force that each movement parts produces, scavenging, inertial force when inner carrier assembly 200 and 250 motions of outer piston assembly, any load that plunger 242, first outer plunger 295 and second outer plunger 296 produce.Therefore, in order to keep the to-and-fro motion of piston, inner carrier assembly 200 and outer piston assembly 250 must receive sizeable input power in the correct time.In the combustion process in the first cylinder cylinder hole 44 and the second cylinder cylinder hole 144, the to-and-fro motion of piston must enough realize required compression.Control the motion of inner carrier assembly 200 and outer piston assembly 250 by input power, particularly near the motion of the top dead center position of the terminal piston of stroke, therefore can control compression ratio.And the variation of compression ratio makes the easier realization of homogeneous combustion, because compression ratio need make a change the firing chamber according to engine operation condition.Since equilibrant must be accurate regularly and controlled, for engine efficiency with keep engine running, controller 35 monitors and the driving engine components are very crucial.

Further, before the engine start, the fluid of high pressure oil storage pool 338 the insides of hydraulic system 329 is in the relatively high pressure state, for example, 5000～6000 pounds per square foots is arranged.The fluid of low pressure oil storage pool 330 the insides of hydraulic system 329 is in the relatively low pressure state, for example, 50～60 pounds per square foots is arranged.

Further, after the engine start, controller 35 gives hydraulic pressure starting control valve door 379 energisings, and according to the working order of motor, hydraulic starting control valve 379 alternately changes between first valve location and second valve location.The first valve location state is that high pressure port 380 communicates with internal pump chamber port 382, and low-pressure port 381 communicates with outside pump chamber port 383; The second valve location state is that high pressure port 380 communicates with outside pump chamber port 383, and low-pressure port 381 communicates with internal pump chamber port 382.

Further, when hydraulic starting control valve 379 was in first valve location, in the pump chamber 306, the inner plunger 242 that promotes on 240 moved right in the fluid in the high pressure oil storage pool 338 can be pressed into, and therefore made whole inner carrier assembly 200 begin to move right.This will make the fluid in the inner couplings pump chamber 308 be pressed in the first coupled outside pump chamber 316 and the second coupled outside pump chamber 320 by the first interconnection passage 322 and the second interconnection passage 323.This will make first outer plunger 295 and second outer plunger 296 on first pull bar 293 and second pull bar 294 be moved to the left separately, therefore make whole outer piston assembly 250 begin to be moved to the left.When outer piston assembly 250 was moved to the left, the fluid in the first outer pump chamber 314 and the second outer pump chamber 318 will be pressed in the low pressure oil storage pool 330 by hydraulic starting control valve 379.

Further, the relative movement meeting of inner carrier assembly 200 and outer piston assembly 250 is moved first outer piston 252 and first inner carrier 202 in the first cylinder cylinder hole 44 simultaneously towards their bottom dead center positions separately, simultaneously, second outer piston 275 in the second cylinder cylinder hole 144 and second inner carrier 220 can be simultaneously towards they top dead center motions separately.Inner carrier assembly 200 and outer piston assembly 250 all move back and forth along an axis of movement single, straight line.This unique axis of movement extends through the center of two cylinders, shown in double-head arrow on the first cylinder cylinder hole 44 among Figure 10,11 and the second cylinder cylinder hole 144.

Further, when hydraulic starting control valve 379 is in second valve location, fluid in the high pressure oil storage pool 338 can be pressed in the first outer pump chamber 314 and the second outer pump chamber 318, first outer plunger 295 and second outer plunger 296 on first pull bar 293 and second pull bar 294 are moved right separately, therefore make whole outer piston assembly 250 begin to move right.Fluid in the first coupled outside pump chamber 316 and the second coupled outside pump chamber 320 is pressed in the inner couplings pump chamber 308 by the first interconnection passage 322 and the second interconnection passage 323.This will make the inner plunger 242 that promotes on the push rod 240 be moved to the left, and therefore make whole inner carrier assembly 200 begin to be moved to the left.When inner carrier assembly 200 was moved to the left, the fluid in the interior pump chamber 306 can be pressed in the low pressure oil storage pool 330 by hydraulic starting control valve 379.

Further, the relative movement meeting of inner carrier assembly 200 and outer piston assembly 250 is moved first outer piston 252 and first inner carrier 202 in the first cylinder cylinder hole 44 simultaneously towards their top dead center positions separately, simultaneously, second outer piston 275 in the second cylinder cylinder hole 144 and second inner carrier 220 can be simultaneously towards they lower dead center motions separately.

Further, three valve locations of the conversion hydraulic starting control valve 379 by accurately and fast, inner carrier assembly 200 and outer piston assembly 250 can be implemented in the compression that hockets in the first cylinder cylinder hole 44 and the second cylinder cylinder hole 144.Controller 35 obtains position and the velocity information of inner carrier assembly 200 and outer piston assembly 250 by monitoring position sensor 288 and 395.Controller 35 is used the valve that these information are changed hydraulic starting control valve 379 in due course, makes the compression ratio that realization needs in the first cylinder cylinder hole 44 and the second cylinder cylinder hole 144.Can learn that by above in the engine start stage, hydraulic starting control valve 379 is being controlled the motion of inner carrier assembly 200 and outer piston assembly 250, this can make inner carrier assembly 200 and outer piston assembly 250 move according to the engine running needs.

Further, motor 10 turns round as two stroke engine, opens and closes suction port and relief opening on the first cylinder cylinder hole 44 and the second cylinder cylinder hole 144 without any independent valve mechanism.The ventilation (comprising air inlet and exhaust) of therefore, compression, burning (comprise and light), expansion, fuel oil and air mixture is all finished in two strokes of piston.Such layout makes the movement parts minimum numberization, and the overall dimensions of motor is minimized.

Further, the motion of inner carrier assembly 200 makes first inner carrier 202 and second inner carrier, the 220 selectable relief openings 46 and 146 that open and close on the first cylinder cylinder hole 44 and the second cylinder cylinder hole 144.The motion of outer piston assembly 250 makes first outer piston 252 and second outer piston, the 275 selectable suction ports 56 and 156 that open and close on the first cylinder cylinder hole 44 and the second cylinder cylinder hole 144, and first piston pin 164 and second wrist pin 282 are air intake pressurized simultaneously.The motion of outer piston assembly 250 makes first outer piston 252 and second outer piston, the 275 selectable oil sprayers 34 and 134 that open and close on the first cylinder cylinder hole 44 and the second cylinder cylinder hole 144.Therefore, the motion of hydraulic starting control valve 379 control inner carrier assemblies 200 and outer piston assembly 250, pressurized air is entered in the first cylinder cylinder hole 44 and the second cylinder cylinder hole 144, fuel oil is entered in the cylinder mix with pressurized air, and burning takes place in compression fully.

Further, combustion process is namely carried out under the homogeneous compression-ignition in normal working usually, utilizes the advantage of motor 10 variable compression ratios to make motor carry out high efficiency burning.Because higher compression ratio is arranged, in the homogeneous compression-ignition process, gas mixture can be lighted automatically uniformly; That is to say the compressed temperature that is heated to automatic igniting of premixed gas mixture.Because mixed gas is spontaneous combustion in the homogeneous compression-ignition process, so gas mixture inside has just formed a lot of burning-points, can guarantee rapid combustion, owing to no longer need flame propagation, this makes can adopt low equivalent proportion (ratio of actual mixing ratio and chemically correct fuel).Improving the advantage that the thermal efficiency reduces the cylinder maximum temperature simultaneously is, compares with the traditional type internal-combustion engine, has significantly reduced the formation of oxynitrides.If desired, on each cylinder spark plug can be installed, motor can turn round as the internal-combustion engine of spark ignition.

Further, in the homogeneous compression-ignition process, during the normal working of engine, the motion of first outer piston 252 not only makes the first cylinder cylinder hole 44 can air inlet, and has determined the moment and the endurance that suction port 56 and first oil sprayer 34 are opened.When top dead center when motion of first outer piston 252 towards it, the volume of the main pump chamber 78 of first scavenging pump 74 makes air enter in the main pump chamber 78 by air inlet leaf valve 94 becoming big.

Further, after top dead center, finish combustion stroke, the movement of first outer piston 252 has reduced the volume in the main pump chamber 78, causes gas to pass compressed suction tude 93 and 72 and air inlet ring 31 of entering of leaf valve 95.When 252 continuation of first outer piston are moved towards its bottom dead center position, electronic controller 35 will determine that first outer piston 252 has moved to enough distant places that can expose first oil sprayer 34 from the signal that position transducer 288 transmits.Electronic controller 35 will activate 34 a period of times of oil sprayer, based on motor and the condition of hydraulic system operation and the fuel pressure of measuring by fuel pressure transmitter 41.When first outer piston 252 continues to its bottom dead center position motion, it will expose suction port 56, and this can allow pressurized air from the air inlet ring 31 inflows first cylinder cylinder hole 44.Air inlet will be inhaled into and mix with fuel oil after atomizing and enter intake duct.The timing meeting of fuel injector and EXO gives the sufficient incorporation time of oil gas to guarantee more uniform mixing.Oil gas mixing uniformly is necessary for homogeneous compression-ignition.More optimizedly, sparger 34 permeates for the fuel oil that obtains a short time in cylinder for generation of extraordinary oil droplet.This helps avoid on the wall that is sprayed onto first oil sprayer, 34 opposites.In addition, preferably oil nozzle 55 has an angle of attack widely---even close to 90 degree.This can help mixed oil and gas by being distributed in the suction port 56 on cylinder 44 circumference.Also have, suction port 56 can arrange to create the effect of eddy current at a certain angle, and this also will further increase the oil gas mixability.Owing to the structure of first cylinder 44 and first outer piston 252, also have the position of nozzle opening 54, the pressure of this position may be not high, so can use a low-pressure sparger.This sparger is lower compared with the high-pressure injector cost that must use in the fuel oil direct-injection system.

Further, after arriving lower dead center, first outer piston 252 moves to top dead center position again.In this process, first outer piston 252 will be closed suction port 56 and nozzle opening 54.Though nozzle opening 54 is by 252 controls of first outer piston in stroke of piston, this injection system is to inject needed fuel oil when nozzle opening 54 is exposed in the first cylinder cylinder hole 44.The mixing of supercharging oil gas is continued to be compressed to top dead center position by first outer piston 252 now.Should know that first oil sprayer 34 directly is sprayed onto the first cylinder cylinder hole 44, but since first outer piston 252 arrives or when arriving top dead center soon oil nozzle 55 be closed, it is not directly exposed to combustion stroke.This is an advantage because in early days combustion stroke the time oil nozzle 55 be in the first cylinder cylinder hole 44 and be not exposed under the extreme temperature and pressure condition.Therefore, under the lower temperature of each combustion stroke and littler pressure condition, just can use more cheap oil sprayer.

Further, the motion of first inner carrier 202 has determined relief opening 46 to open in the first cylinder cylinder hole 44 constantly and the endurance.When first inner carrier 202 leaves top dead center, particularly after the burning, first inner carrier 202 can make waste gas pass through relief opening 46 and discharge through relief openings 46.Waste gas is discharged by the first waste gas spiral outlet 20 and remaining vent systems (not shown).First inner carrier 202 arrives after bottom dead center, to the top dead center motion, can close relief opening 46 effectively in the movement process again.This moment, the waste gas that does not have to discharge can be left in the first cylinder cylinder hole 44, uses as internal exhaust gas recirculation when burning next time.Move to top dead center when 202 continuation of first inner carrier, gas mixture can be compressed.

Further, because the working order in the second cylinder cylinder hole 144 is opposite with the first cylinder cylinder hole 44, burnings in the first cylinder cylinder hole 44 make first inner carrier 202 and second inner carrier 252 towards each other away from the direction motion, and the burnings in the second cylinder cylinder hole 144 make the close direction motion (causing the compression in the first cylinder cylinder hole 44) towards each other of first inner carrier 202 and second inner carrier 252, therefore the work cycle of motor are continued.Various operating modes when considering engine running are kept the running of motor by the injection of control fuel oil before burning.The control fuel oil sprays and can be used for the length of control piston stroke, and the stroke of piston is essential enough obtaining the required compression ratio that burns, but will avoid colliding with piston stopper.Certainly have cas fortuit and take place, as combustion once in a while, system is uneven or other situation, at this moment, hydraulic starting control valve 379 works, and comes together to correct the motion of piston with the fuel oil control measure.This not only is included under the given running operating mode suitable compression ratio is provided, and also is included in top dead center or atdc generation spontaneous combustion and with the burning energy that avoids waste the moving direction of inner carrier assembly 200 and outer piston assembly 250 is changed.If too many kinetic energy passes to inner carrier assembly 200 and outer piston assembly 250, the fluid of piston stopper the inside can absorption portion or whole energy at that time, and piston and back-up ring can bump in case of necessity.

Further, during the normal working of engine, when burning made inner carrier assembly 200 and 250 to-and-fro motion of outer piston assembly, push rod 240 and first pull bar 293, second pull bar 294 made plunger 242, first outer plunger 295 and second outer plunger 296 in they to-and-fro motion in the hole 304,310 and 312 separately.When inner carrier assembly 200 moves right, the motion of inner plunger 242 is opened inner low pressure check valve 360, and fluid is entered in the internal pump chamber 306 from low pressure oil rail 356.Low pressure oil storage pool 330 can replenish from the low pressure oil rail 356 interior fluids that flow out.The fluid that stores in the low pressure oil rail 356 and low pressure oil storage pool 330 replenish the ability of low pressure oil rail 356 must enough pass through low pressure check valve 360 to keep fluid, otherwise, cavitation can appear.

Further, outer piston assembly 250 is to left movement the time, first outer plunger 295 and second outer plunger 296 make the fluid in the first outside pump chamber 314 and the second outside pump chamber 318 enter in the high pressure oil rail 368 by the first external high pressure one-way valve 371 and the second external high pressure one-way valve 372, and the fluid of equivalent enters in the high pressure oil storage pool 338 again in the high pressure oil rail 368.High-pressure liquid in the high pressure oil storage pool 338 can be used as the energy storage source of engine running, also can drive miscellaneous part and system.Because the hydraulic oil available energy is the function of hydraulic fluid pressure and flow, when initial design motor relative dimensions, can utilize required output energy to decide the stroke of piston, the frequency of piston or the size of hydraulic pump plunger.In general, the piston assembly quality of motion is more big, and the operating frequency of motor the best is more low.

Further, when inner carrier assembly 200 moves right during engine running, inner plunger 242 pump the fluid in the inner couplings pump chamber 306 and enter the first coupled outside pump chamber 316 and the second coupled outside pump chamber 320 in.Just as above-mentioned, this makes inner carrier assembly 200 and outer piston assembly 250 keep a kind of relative movement state.If position transducer 288 and 395 detects inner carrier assembly 200 and outer piston assembly 250 does not have in middle position, cylinder hole, a meeting in the first coupling regulating valve 328 and the first coupling regulating valve 336 is activated to adjust the skew of piston so.

Further, during the next stroke of motor, when inner carrier assembly 200 was moved to the left, the pressure flow cognition that inner plunger 242 produces was opened internal high pressure one-way valve 370, makes fluid enter high pressure oil rail 368, and then enters high pressure oil storage pool 338.Simultaneously, outer piston assembly 250 moves right, and first outer plunger 295 and second outer plunger 296 make the fluid in the low pressure oil rail 356 pass through the first outer low pressure one-way valve 362 and the second outer low pressure one-way valve 363.During this stroke of motor, first outer plunger 295 and second outer plunger 296 can pump into the fluid in the first coupled outside pump chamber 316 and the second coupled outside pump chamber 320 in the inner couplings pump chamber 306.

Further, because inner carrier assembly 200 is always opposite with outer piston assembly 250 moving direction, inner plunger 242 is also always opposite with the moving direction of first outer plunger 295, second outer plunger 296, therefore in each stroke of motor, has only in inner plunger 242 or first outer plunger 295, second outer plunger 296 one to high pressure oil storage pool 338 pump oil.In each case, all can be to coupled system pump oil.On the other hand, if want to make inner plunger 242, first outer plunger 295 and second outer plunger 296 at both direction all to high pressure oil storage pool 338 pump oil, need to use different coupled systems.

Further, during the engine running, except the subsystem work of engine interior, the external engine system also work on demand to keep the running of motor 10.Therefore, cooling system pumping cooling liquid on demand by cooling channel 28,50,66,128,150,166 and air ring 352 not overheated to guarantee engine components.In addition, oil-fired system 39 will store fuel oil and the fuel oil of required pressure is provided for first oil sprayer 34 and second oil sprayer 134.Electrical system will provide power supply so that its work for controller 35, sensor and miscellaneous part.Lubrication system can provide required lubricant oil with lubricated some component for motor.During the engine running, gas handling system can provide required clean air for suction port 92 and 192.

Further, though among the disclosed embodiment, be hydraulic oil as the fluid of energy storage medium and control valve, if desired, other suitable fluids also can be used.For example, described fluid can be gas, and oil storage pool can be a pneumatic energy stocking system.The refrigeration agent that fluid also exists with liquid or gaseous state.In these two examples, because fluid no longer is liquid (incompressible usually), be used for the coupled system of 2 opposed motions of piston assembly must be changed.Yet the opposed cylinder type free piston engine of opposed pistons is particularly used the motor of bump combustion chamber, still can be used to produce power and be stored in fluid energy storage medium the inside.

Further, in addition, the opposed cylinder free piston engine of opposed pistons in the example has used hydraulic oil to store and control media as energy, and the opposed cylinder free piston engine of opposed pistons also can use linear alternator as the engine control object and produce electric energy.The oil hydraulic pump assembly also can be replaced by the linear alternator assembly, forms a part that drives the linear alternator assembly with pull bar and push rod.The scavenging pump that the piston/cylinder assembly comprises also uses the energy that drives the linear alternator generation in the combustion stroke to turn round.So the generator that the pressurized air of the high quantity that bump combustion chamber is required can use free-piston engine to connect drives, this can make the specific power maximization of motor.

The above is only for preferred embodiment of the present invention, is not so limits claim of the present invention, so the equivalent structure that all utilizations specification of the present invention and diagramatic content are made changes, all is included in protection scope of the present invention.

Claims (5)

1. the fuel injector of a free piston engine, it is characterized in that, comprise the free piston engine of being formed by hydraulic pump body assembly, first cylinder assembly, second cylinder assembly, described first cylinder assembly is connected in a side of described hydraulic pump body assembly, and described second cylinder assembly is connected in the opposite side of described hydraulic pump body assembly; Described first cylinder assembly comprises first cylinder, the described first cylinder bearing of trend is parallel to axis of movement, described second cylinder assembly comprises second cylinder, the described second cylinder bearing of trend is parallel to axis of movement, is respectively equipped with inner carrier assembly and outer piston assembly in described first cylinder and described second cylinder; The casing wall extended surface of described first cylinder assembly is provided with the first fuel oil jetburner of first suction port, first relief opening and close described first suction port, first fuel injector is installed on the motor and its first nozzle is arranged in the described first fuel oil jetburner, makes can not be exposed in the extreme temperature and pressure at described first nozzle of initial part that burns; The casing wall extended surface of described second cylinder assembly is provided with the second fuel oil jetburner of second suction port, second relief opening and close described second suction port, second fuel injector is installed on the motor and its second nozzle is arranged in the described second fuel oil jetburner, makes can not be exposed in the extreme temperature and pressure at described second nozzle of initial part that burns.

2. the fuel injector of free piston engine according to claim 1, it is characterized in that, described inner carrier assembly comprises to be located at first inner carrier in the described first cylinder assembly cylinder and to be located at the second interior inner carrier of the described second cylinder assembly cylinder, described first inner carrier is connected with described hydraulic pump body assembly by inside connecting rod with described second inner carrier, and the end face of the end face of described first inner carrier and described second inner carrier is in the position away from described hydraulic pump body assembly; Described outer piston assembly comprises to be located at first outer piston in the described first cylinder assembly cylinder and to be located at the second interior outer piston of the described second cylinder assembly cylinder, described first outer piston is connected with described hydraulic pump body assembly by outside connecting rod with described second outer piston, form first firing chamber between described first inner carrier and the opposed layout of described first outer piston and the two-piston end face, form second firing chamber between described second inner carrier and the opposed layout of described second outer piston and the two-piston end face.

3. the fuel injector of free piston engine according to claim 1, it is characterized in that, described first suction port and described second suction port are arranged one respectively at least, and described first suction port and described second suction port are made up of little suction port in the form of a ring.

4. the fuel injector of free piston engine according to claim 1, it is characterized in that, described first fuel injector and described second fuel injector all have the angle of attack of 90 degree approximately, and described first fuel injector and described second fuel injector are respectively towards at least one suction port.

5. the fuel injector of free piston engine according to claim 1, it is characterized in that, also comprise a position transducer, described position transducer transmits the information of described inner carrier assembly and described outer piston assembly to control the shut-in time point of the described first fuel oil jetburner and the described second fuel oil jetburner to controller in real time.

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