CN103206304A - Air intake system for free piston engine with opposed pistons and opposed cylinders - Google Patents

Abstract

The invention discloses an air intake system for a free piston engine with opposed pistons and opposed cylinders. The air intake system comprises a free piston engine and a turbocharger, wherein the free piston engine comprises a hydraulic pump component, a first cylinder assembly and a second cylinder assembly. A compressor is driven by a turbine of the turbocharger and intakes air from the air intake system. An exhaust port of the compressor is guided into a first scavenging pump and a second scavenging pump. The air intake system has the advantages that variable compression ratio is beneficial for volumetric efficiency of homogeneous combustion, and meanwhile, control strategy of the engine is applicable to combustion of different burning wider in range characteristics; higher arresting efficiency can be kept, air loss of exhaust valve is reduced, total quantity of required internal exhaust gas recirculation is kept; uniform exhaust valve inlets are arranged for guaranteeing high scavenging efficiency, and non-uniform valve timing and relative complicated structures are omitted.

Description

The gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons motor

Technical field

The present invention relates to free piston engine, relate to the gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons motor specifically.

Background technique

In general, the piston motion mode of internal-combustion engine is mechanical fixation.For example, traditional Vehicular internal combustion engine includes a bent axle and several link assemblies, such structures shape the mechanical action mode of each piston in cylinder separately.The motion of the piston of this type of motor is the desired motion mode that reaches, because piston determines in the position of each node of motor circulation, has so just simplified timing and the running of motor.In recent years, although the engine efficiency of this traditional type is greatly improved, be subject to the intrinsic characteristic of motor itself, its efficient still is restricted.Specifically, exactly because fixing mechanical structure has been fixed the piston motion mode, thereby fixed compression ratio.In addition, all movement parts (also comprise camshaft and valve) directly related with the piston motion have produced very big friction, and this energy that needs consumption of engine itself to send goes to overcome these frictions.Therefore, cause the specific power of motor lower, mean namely that also motor is bigger, heavier than what imagine.Simultaneously, because must adopt mechanical connection, also limited the flexibility of engine design and layout.

Some motors that contain the bent axle type have used the structural design of two strokes in order to improve engine efficiency.Engine efficiency improves by high suction pressure, has therefore also improved the air inflow of each cylinder.In this traditional two-cycle engine, also use as scavenging pump sometimes towards crankcase at the back side of piston.Yet significantly improving of suction pressure is accompanied by the generation (for example, the fresh air that runs off from exhaust valve) of non-homogeneous valve timing, labyrinth and/or scavenging efficiency and arresting efficiency loss equally.

For the reason of environmental protection and other each side, one of desired design has the more motor of high-energy-density than conventional engines.Lighter weight, littler volume and better fuel efficiency all can be with the obvious advantage in the application of vehicle and stationary electric power plant.

Another kind of internal-combustion engine is a kind of free-piston engine.The motion of this engine piston in cylinder is not that mechanical fixation is constant.The motion of piston by each time point effect thereon equilibrium of forces control.Since the motion of piston is not fixed, the compression ratio of motor is exactly variable so, and this also just makes the design at engine running parameter that greater flexibility has been arranged.Simultaneously, since there is not traditional crankshaft-and-connecting-rod in the motor, just can not produce the piston lateral force, the frictional force that produces when engine running naturally will be littler so.

Since characteristics such as the running of the balance that it is intrinsic and compact structure, the more apparent advantage of the opposed cylinder arrangement of the opposed pistons of free piston engine.This motor more is applicable to two stroke combustion circulation---the particularly burning of homogeneous charge compression ignite (HCCI) type, HCCI burning can take full advantage of the advantage that its variable compression ratio is brought, also improved simultaneously motor energy density, reduced discharging and oil consumption.But because the air fuel ratio higher than conventional engines just needs the bigger full admission amount of each stroke of motor.Run off for fear of fresh air and fuel from relief opening in addition and also need the arresting efficiency that reaches higher.This high air inflow ability is desirable, and simultaneously engine structure is can relative compacter weight also lighter under the situation that keeps higher scavenging efficiency, arresting efficiency and specific power.

Chinese patent CN102182589A discloses a kind of engine aspirating system.This engine aspirating system comprises turbosupercharger, engine intake, also comprise the air amplifier, the low-pressure admission mouth of described air amplifier is communicated with the air outlet of the gas compressor of described turbosupercharger, and the air outlet of described air amplifier is communicated with described engine intake; The high pressure admission mouth of described air amplifier is communicated with high-pressure air source.When engine start or vehicle acceleration, this engine aspirating system has intake velocity faster.The present invention has also applied to turbosupercharger and has improved engine charge, but the difference bigger with the application's engine air-intake structure existence, the utilization field that is used for free piston engine with the application is also different.

Chinese patent CN1696480A discloses a kind of gas handling system of V-type engine.There is a surge tank in this system, when gas handling system is connected to V-type engine, its inner space is divided into a top and a bottom, when a plurality of suction tude are communicated with the suction port of surge tank and V-type engine, surge tank is arranged in the position higher than the cylinder head of V-type engine, wherein, the suction tude that is communicated with a bank of cylinder of V-type engine is connected to the top of surge tank, the suction tude that is communicated with another bank of cylinder is connected to the bottom of surge tank, form surge tank like this, make when gas handling system is assembled to the V-type engine that is installed on the vehicle, the front end at top and the front end of bottom be the rear side of more close vehicle comparatively speaking, thereby can reduce the height of engine hood effectively.This patent belongs to the V-type engine field that is mainly used in, and there is difference in the free piston engine field that uses with the application, and also there are bigger difference in its technical problem to be solved and the application's technical problem to be solved.

Summary of the invention

The problems referred to above at existing free piston engine exists the invention provides a kind of gas handling system that can effectively improve the opposed cylinder free piston formula of the opposed pistons motor of engine charge.

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

The gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons motor, 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, and described second cylinder assembly comprises second cylinder; Described first cylinder is connected with first scavenging pump, and described first scavenging pump comprises first suction port, first air outlet and first pump chamber, and described first pump chamber selectively connects described first suction port and described first air outlet; Described second cylinder is connected with second scavenging pump, and described second scavenging pump comprises second suction port, second air outlet and second pump chamber, and described second pump chamber selectively connects described second suction port and described second air outlet;

An inner carrier assembly, comprise first inner carrier and second inner carrier be located at respectively in described first cylinder and described second cylinder, described first inner carrier and described second inner carrier are fixed by the push rod that is connected on the described hydraulic pump body assembly, and the top of described first inner carrier and described second inner carrier is towards the direction away from described hydraulic pump body assembly;

An outer piston assembly, comprise first outer piston be located at respectively in described first cylinder and described second cylinder and second outer piston and respectively with described first inner carrier and the described second inner carrier opposite disposed, the top of described first outer piston and described second outer piston is respectively towards described first inner carrier and described second inner carrier, the afterbody of described first outer piston connects the first piston pin, and the afterbody of described second outer piston connects second wrist pin;

Described gas handling system also comprises a turbosupercharger, described turbosupercharger comprises a turbo machine, described turbosupercharger is connected into described gas handling system by the air-discharging and supercharging pump, from described gas handling system air inlet, the relief opening of described compressor imports first scavenging pump and second scavenging pump to a compressor by described turbine drives.

The gas handling system of the opposed cylinder free piston formula of above-mentioned opposed pistons motor, wherein, first pull bar connects described first piston pin to drive described first outer piston, and second pull bar connects described second wrist pin to drive described second outer piston.

The gas handling system of the opposed cylinder free piston formula of above-mentioned opposed pistons motor, wherein, described first cylinder assembly is provided with first intake duct and the first coupled intake valve, comprise a pair of enclosed region on the described first piston pin, each described enclosed region has one side to link to each other with described first intake duct.

The gas handling system of the opposed cylinder free piston formula of above-mentioned opposed pistons motor, wherein, cooling heat exchanger in the middle of also comprising one, cooling heat exchanger is provided with a suction port that links to each other with the relief opening of described first scavenging pump in the middle of described, and a relief opening that links to each other with the suction port of described first cylinder.

The gas handling system of the opposed cylinder free piston formula of above-mentioned opposed pistons motor, wherein, also comprise an outside venting gas appliance, the suction port of described outside venting gas appliance connects the relief opening of described first cylinder, and the relief opening of described outside venting gas appliance connects the suction port of described first scavenging pump.

The gas handling system of the opposed cylinder free piston formula of above-mentioned opposed pistons motor, wherein, also comprise a petcock that connects the inlet and exhaust valve of described turbosupercharger, described petcock connects an arm, and described arm will be in order to importing described petcock from the gas that described turbosupercharger relief opening is discharged.

The gas handling system of the opposed cylinder free piston formula of above-mentioned opposed pistons motor, wherein, a plurality of relief openings of described first cylinder are equal to a plurality of suction ports of described first cylinder to the distance of the described first outer piston lower dead center to the distance of the described first inner carrier lower dead center.

The gas handling system of the opposed cylinder free piston formula of above-mentioned opposed pistons motor, wherein, a plurality of relief openings of described second cylinder are equal to a plurality of suction ports of described second cylinder to the distance of the described second outer piston lower dead center to the distance of the described second inner carrier lower dead center.

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

1. the free piston engine of the opposed air cylinder structure of opposed pistons, because of it so the characteristic that has makes its balance better.Simultaneously, the movement parts of the free-piston engine of the opposed air cylinder structure of opposed pistons is less relatively, compares with traditional crank engine, and its power loss that overcomes friction during operation is also less; 2. variable compression ratio not only is conducive to the charging efficiency of homogeneous combustion, also makes the control strategy of this motor be suitable for the burning of the more broad different fuel of scope characteristic simultaneously.The opposed cylinder free piston formula of opposed pistons motor can provide enough compression energies for homogeneous combustion, avoids igniting to produce negative work in earlier stage than crank engine is easier simultaneously.The integrated form scavenging pump has significantly increased the air inflow of each stroke, thereby makes homogeneous combustion more feasible; 3. the output of motor can store in the mode of pressurized air stream or electric energy; 4. even delivery temperature also can guarantee suction pressure by air intake pressurized efficiently than traditional combustion process is lower when using homogeneous combustion.Therefore, even when utilizing a high efficiency waste gas recirculation to increase the homogeneous compression-ignition amplitude, the fresh air that is pressed in each stroke cylinder also significantly increases; 5. can keep higher arresting efficiency, and reduce the loss of exhaust valve air, and keep required internal exhaust gas recirculation total amount; 6. be used for guaranteeing the required even exhaust valve entrance of higher scavenging efficiency, and do not need non-homogeneous valve timing and relevant labyrinth.

Description of drawings

Fig. 1 be the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor gas handling system 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 gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor among Fig. 1;

Fig. 3 is the plan view of second cylinder assembly of the free piston engine of the gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor among Fig. 1;

Fig. 4 is the plan view of first cylinder assembly of the free piston engine of the gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor among Fig. 1;

Fig. 5 is the side view of second cylinder assembly of the free piston engine of the gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor among Fig. 1;

Fig. 6 is the side view of first cylinder assembly of the free piston engine of the gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor 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 the free piston engine of the gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor among Fig. 1 and the schematical top view of inner carrier assembly;

Figure 12 is the hydraulic pump body assembly of the free piston engine of the gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor 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 gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor among Fig. 1;

Figure 14 is the hydraulic circuit schematic representation of the free piston engine of the gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor among Fig. 1;

Figure 15 is the circuit diagram of the free piston engine of the gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor among Fig. 1;

Figure 16 is the fragmentary, perspective view of second embodiment of the gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor among Fig. 1;

Figure 17 is the fragmentary, perspective view of the 3rd embodiment of the gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor among Fig. 1;

Figure 18 is the air intake pressurized system diagram of the gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor among Fig. 1;

Figure 19 is the 4th embodiment's the air intake pressurized system diagram of the gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor;

Figure 20 is the 5th embodiment's the air intake pressurized system diagram of the gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor.

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 gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor shown in Fig. 1-18, comprise the free piston engine of being formed by hydraulic pump body assembly 12, first cylinder assembly 14, second cylinder assembly 16 10, 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, and second cylinder assembly 16 comprises second cylinder; First cylinder is connected with first scavenging pump, 74, the first scavenging pumps 74 and comprises first suction port, first air outlet and first pump chamber, and first pump chamber selectively connects first suction port and first air outlet; Second cylinder is connected with second scavenging pump, 174, the second scavenging pumps 174 and comprises second suction port, second air outlet and second pump chamber, and second pump chamber selectively connects second suction port and second air outlet; An inner carrier assembly 200, comprise first inner carrier 202 and second inner carrier 220 be located at respectively in first cylinder and second cylinder, first inner carrier 202 and second inner carrier 220 are fixed by the push rod that is connected on the hydraulic pump body assembly 12, and the top of first inner carrier 202 and second inner carrier 220 is towards the direction away from hydraulic pump body assembly 12; An outer piston assembly 250, comprise first outer piston 252 be located at respectively in first cylinder and second cylinder and second outer piston 275 and respectively with first inner carrier 202 and second inner carrier, 220 opposite disposed, the top of first outer piston 252 and second outer piston 275 is respectively towards first inner carrier 202 and second inner carrier 220, the afterbody that the afterbody of first outer piston 252 connects first piston pin 264, the second outer pistons 275 connects second wrist pin 282; Gas handling system also comprises a turbosupercharger 27, turbosupercharger 27 comprises a turbo machine 25, turbosupercharger 27 is connected into gas handling system by the air-discharging and supercharging pump, from the gas handling system air inlet, the relief opening of compressor 97 imports first scavenging pump 74 and second scavenging pump 174 to a compressor 97 by turbo machine 25 drivings.

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.Turbosupercharger relief opening and a vent systems 29(simply expression in the drawings) to support the exhaust process of motor.As long as being fit to the processing vent systems 29 of exhaust can be any kind, 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.In addition, wastegate 21 and arm 23 are used, if turbine 25 does not need arm, they can remove so.

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 41, 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.

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.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.Pressure transducer 38 can be entered in the first cylinder cylinder hole 44, but pressure transducer 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.Near suction port 56, the oil mist holes 58 that has a series of annulars to be spaced around first cylinder sleeve 42.

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.

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.The size of first inner carrier 202 is fixed, and makes it can not cover any relief opening 46 at the bottom dead center position head, and 46 pairs of first cylinders 44 of relief opening are opened fully; At top dead center position, afterbody exceeds relief opening 46, and its maintenance is closed fully.For second inner carriers in second cylinder 144 also be.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, the mesh portion of first piston pin 264 is opened near guide rod boss 270, but is closed near first rod head 268 and second rod head 269.The open area of mesh portion is to have created the space between first outer piston, 252 inboards and the main pump chamber 78, has therefore increased the volume of main pump chamber 78 effectively.The enclosed region of mesh portion is positioned at the external diameter of first outer piston 252, radial outside.Enclosed region makes the campaign of pumping for the second time become possibility, when first piston pin 264 moves towards top dead center, by upper connecting rod passage 70 and gas-entered passageway 31 pump gas.

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, second wrist pin 282 comprises a mesh portion, and this part is open state around guide rod boss 286, is closed state near the 3rd rod head 284 and four-pull-rod head 285.The open area of mesh portion has been created open space in second outer piston, 275 sleeve inboards.Enclosed region makes the campaign of pumping for the second time become possibility, when second wrist pin 282 moves towards top dead center, by upper connecting rod passage 170 and gas-entered passageway 131 pump gas.

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 the best, 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.

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, may also contain piston stopper on the hydraulic pump body assembly 12, it is provided with a ultimate range at each end of piston stroke.It is because the motion of free piston engine piston is to be determined by equilibrant that these back-up rings play effect, rather than fixing mechanical approach.The piston stopper of inner carrier assembly 200 comprises first step 388 radially that is positioned at 242 each end of inner plunger on the push rod 240, it with the pump housing 302 and seal plug 309 on center hole 304 each hold first radially step part 389 cooperate.First radially step 388 and first radially the relative position of step part 389 determining the range of inner carrier assembly 200 on all directions.If first radially step 388 with first radially step part 389 contact, piston will stop in the motion of this direction.

Further, the piston stopper on the outer piston assembly 250 comprises radially step 390 and 391, and they are each positioned at each end of first outer plunger 295 and second outer plunger 296 of first pull bar 293 and second pull bar 294, and are spaced.The pump housing 302 and seal plug 311 with 313 with inner carrier assembly 200 on identical structure arranged, comprise radially step part 392 and 393, be each positioned at the other end of first tie rod hole 310 and second tie rod hole 312.

Further, another replacement scheme is to remove piston stopper.Like this, the piston head 210 of first inner carrier 202 can clash into the piston head 254 of first outer piston 252, can play the effect of back-up ring in one direction, and the piston head 222 of second inner carrier 220 can clash into the piston head 276 of second outer piston 275, can play the effect of back-up ring on another direction.Because the piston top has bigger area to be used for colliding, and before piston collisions, the pressure in the cylinder is rising sharply, can slow down the speed of collision.

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, 35000KPa～42000KPa 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, 350KPa～420KPa 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 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 10 is minimized.For this motor is effectively turned round, yet, not being both certainly of exhaust pressure-and, the suction pressure-needs higher than exhaust back pressure.Above-mentioned gas handling system can provide this suction pressure.

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.Though initial fuel-burning equipment does not utilize the turbosupercharger 27 of exhaust gas drive.But these can both be by the change compression ratio, oil spout, and perhaps other parameters know that exhaust can drive turbine 25.

Further, combustion process is namely carried out under the homogeneous compression-ignition in normal working usually, utilizes the advantage of engine variable compression ratio 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.Simultaneously, the enclosed region pressurized air of first piston pin 264 mesh-like area is by pull bar passage 70, intake duct 31 and intake valve 56, and enter first outer piston 252 and cover intake valve 56 fully.Though intake duct 31 is because the effect of main scavenging pump has comprised air intake pressurized gas, mesh-like area will help to be sent in the first cylinder cylinder hole 44 by the pumping second time.So first scavenging pump 74 has increased density of the induced air for suction pressure provides important propelling.

Further, first outer piston 252 arrives atdc, the particularly motion after burning, and the volume of main pump chamber 78 is being diminished, and the air of the inside is compressed and extrude, and by the leaf valve 95 of giving vent to anger enter gas-entered passageway 93 and 72 and air inlet ring 31 in.When first outer piston 252 continues to move to its bottom dead center position, will open suction port 56, the pressurized air in the air inlet ring 31 are flowed in the first cylinder cylinder hole 44.Simultaneously, first oil sprayer 34 also can be exposed in the first cylinder cylinder hole 44.Controller 35 will activate first oil sprayer 34, and fuel oil is injected in the cylinder.Controller 35 utilizes position transducer 291 and fuel pressure transmitter 41 to decide the moment and the injection duration of oil spout.

Further, first outer piston 252 arrives after bottom dead center, and the top dead center to it moves again.In movement process, first outer piston 252 will be closed suction port 56 and the nozzle opening 54 in the first cylinder cylinder hole 44.When 252 continuation of first outer piston were moved to top dead center, gas mixture can be compressed.Should be noted that first oil sprayer 34 directly sprays into fuel oil in the first cylinder cylinder hole 44, but it is not directly exposed in the burning because when first outer piston 252 near top dead center position the time, first oil sprayer 34 can be sheltered from by first outer piston 252.

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.

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.Therefore, cooling system pumping cooling liquid on demand is by cooling channel 28,50,128,150,352 and air ring 66,166 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 the embodiment of the opposed cylinder free piston formula of the opposed pistons that is discussed in detail here motor utilizes a hydraulic fluid to store and control media as energy, the opposed cylinder free piston formula of opposed pistons motor can utilize DC generator to control motor and produce electric energy.Casing of hydraulic pump assembly 12 will be replaced by the DC generation thermomechanical components, and push rod and pull bar form the part of generator or drive generator component.Above-mentioned cylinder assembly will turn round and produce heat and drive DC generator.So, in the homogeneous combustion process, under the situation of air abundance, also can use DC generator.

Second embodiment's of the gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor fragmentary, perspective view as shown in figure 16.Be in the example at this, second motor 408 is identical with first embodiment in essence, and except cylinder cover 410 has comprised a sparking plug boss 412, spark plug 414 is installed on the boss.The cylinder liner (not shown) comprises a passage that communicates with sparking plug boss 412, and spark plug 414 just can stretch in the cylinder like this.Spark plug 414 separates with pressure transducer 38 between piston.The end of spark plug 414 links to each other with an electronic control injection system (not shown), by controller 35 control (not shown).Opposed two cylinders in the present embodiment all contain the spark plug layout of said structure.

Further, the structure of second motor 408 is similar to the motor 10 among first embodiment.So more complicated consumption is also bigger because the structure that has increased spark plug 414 second motors 408 becomes, also increased by second motor 408 simultaneously in running and flexibility and adaptability when starting.In second motor, 408 start-up courses, required if cylinder compression ratio does not reach bump combustion chamber, at this moment spark plug 414 just can or closing on each cylinder top dead center in the igniting.So just may operate in advance by general relatively motor, when turbosupercharger is not operated with full load.In this case, suction pressure can be than lacking that two-stroke bump combustion chamber pattern needs.

Further, in general engine operation process, second motor 408 may exchange between spark plug 141 igniting and bump combustion chamber.In this transfer process, air fuel ratio and compression ratio can adapt to the running of motor different mode.In addition, if in the engine operation process of general homogeneous compression-ignition, a combustion process is not finished, spark just can light and promote a back combustion process to avoid the fuel oil accumulation in the cylinder and avoid fuel oil to enter vent systems with this.Perhaps, do not need if bump combustion chamber is this motor, second motor 408 also can utilize spark plug 414 igniting under general operating mode.No matter which, turbosupercharger and scavenging pump air intake pressurized system can both provide required air intake pressurized for it.

Further, though hydraulic oil is as medium and the closed control valve of stored energy, can select other suitable fluid as required.For example, fluid may be gas, and an air energy-storage system is arranged.Fluid also may be a freezing mixture, can be liquid or gaseous state.Above-mentioned two examples because fluid no longer is fluid (incompressible), guarantee the carrying out of two opposed motions of piston assembly by coupled system.Yet the opposed cylinder free piston formula of opposed pistons motor has bump combustion chamber by it, still can utilize flowing medium to come stored energy.

Further, above-mentioned embodiment about the opposed cylinder free piston formula of opposed pistons motor, a turbosupercharger 27 and scavenging pump 74 and 174 are arranged, and as to the supercharging of the opposed cylinder free piston formula of opposed pistons engine charge, are its power supply also by the DC MOTOR CONTROL motor.The oil hydraulic pump plug will replace a dc motor assembly gradually, draw and push rod.The energy drives direct current generator of piston/cylinder left button-comprise scavenging pump-combustion process is produced.So bump combustion chamber has the high quality pressurized air, still operate with the opposed cylinder free piston formula of opposed pistons motor coupling direct current generator, do not provide peak output to motor.

The 4th embodiment's of the gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor air intake pressurized system as shown in figure 19, gas handling system comprises a turbosupercharger 27 equally in this embodiment, one turbo machine 25 is arranged, turbosupercharger 27 links to each other with gas handling system 29 by the air-discharging and supercharging pump, and a compressor 97 is by turbo machine 25 drivings and from gas handling system 87 air inlets.The relief opening of compressor 97 imports first scavenging pump 74 and second scavenging pump 174.First scavenging pump 74 and second scavenging pump 174 scan out one- way valve 95 and 195 with gas, when pressurization gas enters the first cylinder cylinder hole 44 and the second cylinder cylinder hole 144 when intake valve is opened.The structure of the opposed cylinder free piston engine 10 of opposed pistons is identical with first embodiment with details.

Further, most of exhausts still are imported into turbo machine 25 in first embodiment, and a part then is imported in the gas recirculation system device in this embodiment.The first waste gas recirculation assembly 502 includes a variable heat exchanger 504, is used for coolant exhaust, and a vario valve 506 is arranged, and is used for the control exhaust airstream.The first waste gas recirculation assembly 502 imports inlet stream with exhaust.The first waste gas recirculation assembly 502 so just can be avoided flowing into rotary compressor through the gas after the waste gas recycling processing between turbosupercharger 27 and first scavenging pump 74.The second waste gas recirculation assembly 508 comprises second a variable heat exchanger 510 and second vario valve 512, and is identical with the first waste gas recirculation assembly 502, but gas after the waste gas recycling processing is imported second scavenging pump 174.Variable heat exchanger 504 and the second variable heat exchanger 510, vario valve 506 and second vario valve 508 all pass through automatically controlled original paper 35 control (not shown).

Further, the greater flexibility that allows during the amount of the ability that egr gas is cooled off that in the first cylinder cylinder hole 44 and the second cylinder cylinder hole 144, provides of this 4th embodiment and control ability egr gas under the operating condition of the motor of management of entering the combustion process in the cylinder.Though the waste gas that first embodiment's the egr gas amount that enters with almost fixed does not enter cooling,, it provide one not too complicated, the egr gas system that cost is lower.In addition, the external exhaust gas recirculation gas system can be used and the of the present invention second and the 3rd embodiment.

The 4th embodiment's of the gas handling system of the opposed cylinder free piston formula of a kind of opposed pistons of the present invention motor air intake pressurized system as shown in figure 20, the details of the opposed cylinder free piston engine 10 of opposed pistons does not show that in the drawings its structure is identical with first embodiment with details.This embodiment is similar to the 4th embodiment, and turbosupercharger 27 comprises a turbo machine 25, by exhaust gas drive and enter vent systems 29.Turbo machine 25 drive compression machines 97, the gas boosting that will enter from gas handling system 87.This embodiment also has the first waste gas recirculation assembly 502 and the second waste gas recirculation assembly 508 to finish cooling and the recirculation of exhaust.Exhaust and the gas handling system of two free-piston engines that are combined into one in the present embodiment.

Further, the waste gas that removes from each inblock cylinder is led back into going into turbosupercharger 27.As shown in the 4th embodiment, a part of exhaust is by the first waste gas recirculation assembly 502 and the second waste gas recirculation assembly 508 and come back in the gas handling system.

Further, particularly, the exhaust of compressor 97 not only is imported into first scavenging pump 74 and second scavenging pump 174, also is imported into the 3rd scavenging pump 602 and the 4th scavenging pump 604.First scavenging pump 74 is squeezed into first intercooler 606 with pressurization gas, and it can be positioned at as shown in the figure above the one-way valve, also may be positioned at this valve below.First intercooler 606 cooled off it before pressurization gas enters the first cylinder cylinder hole 44, had therefore improved in-cylinder pressure density.First intercooler 606 also can be variable, (not shown) when it is controlled by controller 35.Second scavenging pump 174 imports pressurization gas in second intercooler 608, and second intercooler, 608 intercoolers will cool off it pressurization gas enters the second cylinder cylinder hole 144 by one-way valve 195 before.

Further, the 3rd scavenging pump 602 imports pressurization gas in the 3rd intercooler 610, and gas passes through one-way valve 612 before entering the 3rd cylinder cylinder hole 614, and it also is the part of second free piston engine.The 4th scavenging pump 604 imports pressurization gas in the 4th intercooler 616, and gas passes through one-way valve 618 before entering the 4th cylinder cylinder hole 620, and it equally also is the part of second free piston engine

From four cylinders, the waste gas that the first cylinder cylinder hole 44, the second cylinder cylinder hole 144, the 3rd cylinder cylinder hole 614 and the 4th cylinder cylinder hole 620 are got rid of is led back into going into turbocharger turbine.As shown in the 4th embodiment, a part of exhaust is by exhaust gas recirculatioon left button 502 and 508 and come back in the air inlet.Simultaneously, if needs are arranged, first intercooler 606 among this embodiment and second intercooler 608 also can be as the 4th embodiment's air intake pressurized systems.

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 (8)

1. the gas handling system of the opposed cylinder free piston formula of an opposed pistons motor, 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, and described second cylinder assembly comprises second cylinder; Described first cylinder is connected with first scavenging pump, and described first scavenging pump comprises first suction port, first air outlet and first pump chamber, and described first pump chamber selectively connects described first suction port and described first air outlet; Described second cylinder is connected with second scavenging pump, and described second scavenging pump comprises second suction port, second air outlet and second pump chamber, and described second pump chamber selectively connects described second suction port and described second air outlet;

An inner carrier assembly, comprise first inner carrier and second inner carrier be located at respectively in described first cylinder and described second cylinder, described first inner carrier and described second inner carrier are fixed by the push rod that is connected on the described hydraulic pump body assembly, and the top of described first inner carrier and described second inner carrier is towards the direction away from described hydraulic pump body assembly;

An outer piston assembly, comprise first outer piston and second outer piston be located at respectively in described first cylinder and described second cylinder, and respectively with described first inner carrier and the described second inner carrier opposite disposed, the top of described first outer piston and described second outer piston is respectively towards described first inner carrier and described second inner carrier, the afterbody of described first outer piston connects the first piston pin, and the afterbody of described second outer piston connects second wrist pin;

Described gas handling system also comprises a turbosupercharger, described turbosupercharger comprises a turbo machine, described turbosupercharger is connected into described gas handling system by the air-discharging and supercharging pump, from described gas handling system air inlet, the relief opening of described compressor imports first scavenging pump and second scavenging pump to a compressor by described turbine drives.

2. the gas handling system of the opposed cylinder free piston formula of opposed pistons motor according to claim 1, it is characterized in that, first pull bar connects described first piston pin to drive described first outer piston, and second pull bar connects described second wrist pin to drive described second outer piston.

3. the gas handling system of the opposed cylinder free piston formula of opposed pistons motor according to claim 1, it is characterized in that, described first cylinder assembly is provided with first intake duct and the first coupled intake valve, comprise a pair of enclosed region on the described first piston pin, each described enclosed region has one side to link to each other with described first intake duct.

4. the gas handling system of the opposed cylinder free piston formula of opposed pistons motor according to claim 1, it is characterized in that, cooling heat exchanger in the middle of also comprising one, cooling heat exchanger is provided with a suction port that links to each other with the relief opening of described first scavenging pump in the middle of described, and a relief opening that links to each other with the suction port of described first cylinder.

5. the gas handling system of the opposed cylinder free piston formula of opposed pistons motor according to claim 1, it is characterized in that, also comprise an outside venting gas appliance, the suction port of described outside venting gas appliance connects the relief opening of described first cylinder, and the relief opening of described outside venting gas appliance connects the suction port of described first scavenging pump.

6. the gas handling system of the opposed cylinder free piston formula of opposed pistons motor according to claim 1, it is characterized in that, also comprise a petcock that connects the inlet and exhaust valve of described turbosupercharger, described petcock connects an arm, and described arm will be in order to importing described petcock from the gas that described turbosupercharger relief opening is discharged.

7. the gas handling system of the opposed cylinder free piston formula of opposed pistons motor according to claim 1, it is characterized in that a plurality of relief openings of described first cylinder are equal to a plurality of suction ports of described first cylinder to the distance of the described first outer piston lower dead center to the distance of the described first inner carrier lower dead center.

8. the gas handling system of the opposed cylinder free piston formula of opposed pistons motor according to claim 1, it is characterized in that a plurality of relief openings of described second cylinder are equal to a plurality of suction ports of described second cylinder to the distance of the described second outer piston lower dead center to the distance of the described second inner carrier lower dead center.

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