CN102400784A - Double-cylinder four-piston opposed hydraulic control engine - Google Patents
Double-cylinder four-piston opposed hydraulic control engine Download PDFInfo
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- CN102400784A CN102400784A CN2011103354292A CN201110335429A CN102400784A CN 102400784 A CN102400784 A CN 102400784A CN 2011103354292 A CN2011103354292 A CN 2011103354292A CN 201110335429 A CN201110335429 A CN 201110335429A CN 102400784 A CN102400784 A CN 102400784A
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Abstract
The invention discloses a double-cylinder four-piston opposed hydraulic control engine. Two groups of opposed piston components are respectively provided with a group of opposed moving pistons; and joints at oil-receiving ends of the pistons correspond to those of two groups of reciprocating volume pumps on a rotating main shaft respectively. The main shaft is rotated, then the volume pump is changed to be directly coupled on the piston, and the moving direction and the positions of the inner dead point and the outer dead point of the pistons are controlled accurately so as to respectively finish the working stroke of gas inlet, compression, working expansion and exhaust, and power output. In the double-cylinder four-piston opposed hydraulic control engine, the pistons are controlled by a simple mode so as to give consideration to the advantages of the conventional engine and the hydraulic free-piston engine, and also avoid the respective defects. Other systems such as a starting system, an oil supply system, a combustion system, a cooling system and a sealing system share the existing fully-mature technology so as to be convenient for implementation of the project. The double-cylinder four-piston opposed hydraulic control engine is applicable to promotion of the engine industry.
Description
Technical field
The present invention relates to a kind of motor, specifically, relate to a kind of twin-tub four piston opposed type hydraulic control motors.
Background technique
Existing conventional engine is to rely on bent axle, piston, connecting rod, cam valve train to accomplish engine working process; Very perfect at present; But reach certain working condition,, compression ratio high-power like big cylinder diameter, long stroke, high pressure-charging can be in harmonious proportion technical order such as energy-conserving and environment-protective and will receive the each side restriction.In this field, people have done the trial of each side, and comprising famous rotary engine, but because of its special curve causes the difficulty of producing and safeguarding, especially sealing is not also from the solution of essence.So also not having large size so far promotes.
Can simplify engine structure like cancellation bent axle, connecting rod etc., guarantee engine reliable work again? This just comprises that wherein starting from the 20-30 age in last century begins one's study, and in the free-piston gas machine/gas compressor of 50-60 age industrialized production.Develop into the hydraulic free-piston engine of 1980-2000 development gradually according to self good and bad characteristic.The 37th the 2nd phases of volume of work " mechanical engineering journal " such as relevant this respect report " development course of hydraulic free-piston engine and research situation " Yang Huayong, February calendar year 2001; " extraordinary engine principles and structure " Zhu Xian ancient cooking vessel version in 1998; Free-piston fluid power motor etc. has more detailed, the argumentation of system.
The internal-combustion engine hydraulic controlization will be brought following characteristic: load power is big, vibration making little, piston is very simple; Moving situation good (not having side pressure) etc., but we also see regardless of the free-piston fluid power motor control system that is the sort of form complicated especially simultaneously.All need lean on control piston operations such as solenoid valve, oil pump, oil motor, inductor.But there is integrity problem in engine revolution in this way from hundreds of to thousands of commentaries on classics, influences transmission efficiency simultaneously greatly.
Summary of the invention
Technical problem to be solved by this invention provides a kind of simple in structure, reliable and stable performance, the twin-tub four piston opposed type hydraulic control motors that transmission efficiency is high.
In order to solve the problems of the technologies described above; Twin-tub four piston opposed type hydraulic control motors provided by the invention; Comprise main shaft and the starting component that is connected with described spindle; Be provided with two groups of single cylinder double-piston opposed type fluid power motor groups; Every group of described single cylinder double-piston opposed type fluid power motor group has a combustion powered chamber and two pistons; Two described pistons are done the reverse sync motion; Be formed with a power oil pocket and oil back chamber between each described piston and the cylinder body; Described combustion powered chamber is provided with air distributing device and fuel injector igniter; The operating movement mode of the piston of two groups of described single cylinder double-piston opposed type fluid power motor groups is provided with on the contrary, and described spindle is connected with two groups of reciprocal conversion equipments of dual-volume storage, and a volume of first group of reciprocal conversion equipment of described dual-volume storage is connected with the power oil pocket of the described piston of an end of first group of described single cylinder double-piston opposed type fluid power motor group; Another volume is connected with the power oil pocket of the described piston of an end of second group of described single cylinder double-piston opposed type fluid power motor group; A volume of second group of reciprocal conversion equipment of described dual-volume storage is connected with the power oil pocket of the described piston of the other end of first group of described single cylinder double-piston opposed type fluid power motor group, and another volume is connected with the power oil pocket of the described piston of the other end of second group of described single cylinder double-piston opposed type fluid power motor group, and the oil back chamber of a piston of first group of reciprocal conversion equipment of described dual-volume storage is connected with the oil back chamber of a piston of second group of described single cylinder double-piston opposed type fluid power motor group.
The structure of the reciprocal conversion equipment of described dual-volume storage is that outer slide is located in the square oil cylinder and is formed with two volumes that are connected with the power oil pocket respectively at described outer slide with two ends between the described square oil cylinder; In described outer slide, be provided with inner slide; Be fixed with eccentric wheel on the described main shaft, described eccentric wheel flip sleeve is contained in the described inner slide.
The structure of the reciprocal conversion equipment of described dual-volume storage is that first piston is located in the oil cylinder and is formed with two volumes that are connected with the power oil pocket respectively at described first piston with two ends between the described oil cylinder, and described first piston passes through linkage mechanism and is connected with described spindle.
Described air distributing device is on the described cylinder body of described single cylinder double-piston opposed type fluid power motor group, to be provided with the plunger that cooperates insertion with each described piston; Be formed with scavenge space between described piston and the described plunger; On described cylinder body, be provided with the breather check valve and the exhaust check valve that are communicated with described scavenge space; Described exhaust check valve is connected with gas holder; Described gas holder is connected with air distributing device, and described air distributing device is communicated with the described combustion powered chamber of two groups of described single cylinder double-piston opposed type fluid power motor groups respectively.
Described air distributing device is on described main shaft, to be connected with air inlet distributing valve and exhaust distributing valve; The structure of described air inlet distributing valve be on described main shaft, endwisely slip, circumferentially fixed cover is equipped with cone valve outside the air inlet; On described main shaft, be fixed with the air inlet limited ring; Be provided with air inlet between the outer cone valve of described air inlet limited ring and described air inlet and hold out against spring; The outer cone valve of described air inlet is provided with the air inlet waveform groove; Rotating sleeve is equipped with cone valve in the air inlet on the cone valve outside described air inlet; Cone valve is provided with two exhaust ports that are connected with two described combustion powered chambeies respectively and one and the tank connected inlet hole of described gas storage in the described air inlet, and the outer cone valve of described air inlet makes described air inlet waveform annular groove be communicated with inlet hole with first exhaust port and cut off inlet hole and second exhaust port in a phase place when rotating, at another phase place connection inlet hole and second exhaust port and cut-out inlet hole and first exhaust port; The structure of described exhaust distributing valve be on described main shaft, endwisely slip, circumferentially fixed cover is equipped with cone valve outside the exhaust; On described main shaft, be fixed with the exhaust limited ring; Be provided with exhaust between the outer cone valve of described exhaust limited ring and described exhaust and hold out against spring; The outer cone valve of described exhaust is provided with air inlet waveform annular groove; Rotating sleeve is equipped with cone valve in the exhaust on the cone valve outside described exhaust; Cone valve is provided with two inlet holes that are connected with two described combustion powered chambeies respectively and the exhaust port of an emptying in the described exhaust, and the outer cone valve of described exhaust makes described air inlet waveform annular groove be communicated with exhaust port with first inlet hole and cut off exhaust port and second inlet hole in a phase place when rotating, at another phase place connection exhaust port and second inlet hole and cut-out exhaust port and first inlet hole.
The oil back chamber of described single cylinder double-piston opposed type fluid power motor group is connected with oil hydraulic pump through hydraulically-controlled one-way valve, relief valve.
The power oil pocket of same described piston and oil back chamber are provided with bypass tube in the motion lower dead center of described piston.
Adopt the twin-tub four piston opposed type hydraulic control motors of technique scheme, power cavity is the firing chamber, is used for gas expansion for doing work, transformation of energy.The acting in conjunction of oil back chamber and power oil pocket is to be used for stablizing control piston motion and direction.Another effect of power oil pocket then is that the gas pressure of expansion that piston is received becomes hydraulic pressure and can and pass.The scavenging chamber that piston cavity forms; Under the effect of breather check valve, exhaust check valve, constantly fresh air is sucked, discharge with the pressurized air form; Discharge pressurized air for two groups and all get into gas holder; The usefulness that is used for the motor exchanging gas in fact just is equivalent to reciprocating compressor, is used for engine air supply systems.Control piston moves and accomplishes whole engine charge-compression-expansion acting-exhaust, and process is to be accomplished by the annex on main shaft and the main shaft.
Main shaft connects two groups of reciprocal conversion equipments of dual-volume storage; Volume oil pump interface is the power oil pocket of corresponding oil cylinder respectively; Main axis rotation, two volume-variation of the reciprocal conversion equipment of dual-volume storage are directly coupled on the piston; Cause that two groups of pistons move respectively in opposite directions or on the contrary, accomplish air inlet-compression-expansion acting-exhaust process.Otherwise piston in opposite directions, and opposite moving then affacts on the reciprocating type volume of the reciprocal conversion equipment of dual-volume storage through the power oil pocket, and at this moment the reciprocal conversion equipment of dual-volume storage changes into the circular movement of main shaft with regard to a suitable oil motor.
Working method of the present invention is similar with two cylinder uniflow scavenging two stroke diesel engines.Adopt EFI, then become petrol engine with spark ignitor.
Main shaft drive oil hydraulic pump rotatablely move fill and replenish begin and operation process in hydraulic oil loss flow, redundance is got rid of through relief valve.
The present invention compares with existing free-piston, and the opposed pistons motion is controlled, and compression ratio is fixing within the specific limits, thereby guarantees the running of motor optimum working state.Two groups of opposed pistons movement velocitys are identical, in the opposite direction, and dynamic balance is good, and the high frequency oscillation that the explosion expansion produces can be absorbed by hydraulic pressure.Main shaft, vital parts such as piston, the one, part number is few, and simple structure is easy to process.The power transmission hydraulic pipe line is direct-connected, needn't pass through valve, and control system does not have solenoid valve, and the control unit that inductor etc. are complicated is reliable and stable, and the motor overall volume especially highly greatly reduces.
Description of drawings
Fig. 1 is overall structure of the present invention and principal intention.
Fig. 2 is a gas port distribution overall structure schematic representation of the present invention.
Fig. 3 is a piston nose pump gas of the present invention, gas port distribution overall structure schematic representation.
Fig. 4 is that main shaft connects air pump, gas distribution structure schematic representation.
Fig. 5 is the reciprocal dual-volume storage pump structure of a present invention schematic representation.
Fig. 6 is the reciprocal dual-volume storage pump structure of an eccentric stiffener schematic representation.
Fig. 7 is the reciprocal dual-volume storage pump structure of a crankshaft & connecting schematic representation.
Fig. 8 is an intake and exhaust structural representation of the present invention.
Fig. 9 further specifies intake and exhaust axis of no-feathering side of the present invention (solid) schematic representation.
Figure 10 is a kind of rotary cylindrical three-way valve structural representation.
Embodiment
Below in conjunction with accompanying drawing and embodiment the present invention is described further.
Press Fig. 1, Fig. 5, Fig. 8 and shown in Figure 9; Comprise the first single cylinder double-piston opposed type fluid power motor group 1 and the second single cylinder double-piston opposed type fluid power motor group 43; The first single cylinder double-piston opposed type fluid power motor group 1 is provided with first cylinder 8; The two ends of first cylinder 8 are provided with between first piston 5 and second piston 14 of the opposed first piston that is provided with 5 and second piston, 14, the first cylinders 8 in first oil cylinder 4 and second oil cylinder, 15, the first cylinders 8 and are formed with the first combustion powered chamber 11; The first combustion powered chamber 11 is provided with first oil sprayer 10; The first combustion powered chamber 11 of first cylinder 8 is provided with first suction port 52 and first relief opening 53, and first piston 5 is in first oil cylinder 4, and first plunger 2 is fixed on first oil cylinder 4 and inserts in the first piston 5; Be formed with the first scavenging chamber 7 between the first piston 5 and first oil cylinder 4; The end of first oil cylinder 4 is provided with first breather check valve 51 and first exhaust check valve 50 that is communicated with the first scavenging chamber 7, is formed with the first power oil pocket 3 between the first piston 5 and first oil cylinder 4 and first oil back chamber, 6, the second pistons 14 are in second oil cylinder 15; Second plunger 17 is fixed on second oil cylinder 15 and inserts in second piston 14; The end that is formed with the second scavenging chamber, 12, the second oil cylinders 15 between second piston 14 and second oil cylinder 15 is provided with between second breather check valve 18 that is communicated with the second scavenging chamber 12 and second exhaust check valve, 19, the second pistons 14 and second oil cylinder 15 and is formed with the second power oil pocket 16 and second oil back chamber 13; The second single cylinder double-piston opposed type fluid power motor group 43 is provided with second cylinder 36; The two ends of second cylinder 36 are provided with the 3rd oil cylinder 38 and the 4th oil cylinder 30; Opposed the 3rd piston 40 that is provided with and the 4th piston 31 in second cylinder 36; Be formed with the second combustion powered chamber 35 between the 3rd piston 40 of second cylinder 36 and the 4th piston 31; The second combustion powered chamber 35 that the second combustion powered chamber 35 is provided with second oil sprayer, 34, the second cylinders 36 is provided with second suction port 54 and second relief opening, 55, the three pistons 40 are in the 3rd oil cylinder 38; The 3rd plunger 42 is fixed on the 3rd oil cylinder 38 and inserts in the 3rd piston 40; The end that is formed with the 3rd scavenging chamber 37, the three oil cylinders 38 between the 3rd piston 40 and the 3rd oil cylinder 38 is provided with between the 3rd breather check valve 44 that is communicated with the 3rd scavenging chamber 37 and the 3rd exhaust check valve 45, the three pistons 40 and the 3rd oil cylinder 38 and is formed with the 3rd power oil pocket 41 and the 3rd oil back chamber 39; The 4th piston 31 is in the 4th oil cylinder 30; The 4th plunger 29 is fixed on the 4th oil cylinder 30 and inserts in the 4th piston 31, and the end that is formed with the 4th scavenging chamber 33, the four oil cylinders 30 between the 4th piston 31 and the 4th oil cylinder 30 is provided with the 4th breather check valve 25 and the 4th exhaust check valve 24 that is communicated with the 4th scavenging chamber 33; Be formed with the 4th power oil pocket 28 and the 4th oil back chamber 32 between the 4th piston 31 and the 4th oil cylinder 30; The power oil pocket of same piston and oil back chamber are provided with bypass tube in the motion lower dead center of piston, and first oil back chamber 6 is communicated with the 3rd oil back chamber 39, and second oil back chamber 13 and the 4th oil back chamber 32 are communicated with.Main shaft 48 1 ends connect starting component 49; The other end is connected with belt wheel 21 and is connected with Injection Pump assembly 20; Injection Pump assembly 20 is connected with second oil sprayer 34 with first oil sprayer 10; Main shaft 48 the be in transmission connection first reciprocating type dual-volume storage pump 47 and the second reciprocating type dual-volume storage pump 22; The structure of the first reciprocating type dual-volume storage pump 47 and the second reciprocating type dual-volume storage pump 22 is: outer slide 224 is located in the square oil cylinder 221 and is formed with two volumes that are connected with the power oil pocket respectively at outer slide 224 with two ends between the square oil cylinder 221; In outer slide 224, be provided with inner slide 223, be fixed with eccentric wheel 222 on the main shaft 48, eccentric wheel 222 flip sleeves are contained in the inner slide 223.A volume of the first reciprocating type dual-volume storage pump 47 is communicated with the first power oil pocket 3; Another volume is communicated with the 3rd power oil pocket 41; A volume of the second reciprocating type dual-volume storage pump 22 is communicated with the second power oil pocket 16, and another volume is communicated with the 4th power oil pocket 28.First exhaust check valve 50, second exhaust check valve 19, the 3rd exhaust check valve 45 and the 4th exhaust check valve 24 are connected with gas holder 9; On main shaft 48, be connected with air inlet distributing valve 56 and exhaust distributing valve 57; The structure of air inlet distributing valve 56 be on main shaft 48, endwisely slip, circumferentially fixed cover is equipped with cone valve 562 outside the air inlet; On main shaft 48, be fixed with air inlet limited ring 564; Be provided with air inlet between the outer cone valve 562 of air inlet limited ring 564 and air inlet and hold out against spring 563; The outer cone valve 562 of air inlet is provided with the air inlet waveform groove; Rotating sleeve is equipped with cone valve 561 in the air inlet on the cone valve 562 outside air inlet; Cone valve 561 is provided with respectively two exhaust ports and an inlet hole that is connected with gas holder 9 that is connected with second suction port 54 with first suction port 52 in the air inlet, and the outer cone valve 562 of air inlet makes air inlet waveform annular groove at a phase place connection gas holder 9 and first suction port 52 and the cut-out gas holder 9 and second suction port 54 when rotating, at another phase place connection gas holder 9 and second suction port 54 and the cut-out gas holder 9 and first suction port 52; The structure of exhaust distributing valve 57 be on main shaft 48, endwisely slip, circumferentially fixed cover is equipped with cone valve 572 outside the exhaust; On main shaft 48, be fixed with exhaust limited ring 574; Be provided with exhaust between the outer cone valve 572 of exhaust limited ring 574 and exhaust and hold out against spring 573; The outer cone valve 572 of exhaust is provided with air inlet waveform annular groove; Rotating sleeve is equipped with cone valve 571 in the exhaust on the cone valve 572 outside exhaust; Cone valve 571 is provided with two inlet holes that are connected with second relief opening 55 with first relief opening 53 respectively and the exhaust port of an emptying in the exhaust, and the outer cone valve 572 of exhaust makes air inlet waveform annular groove be communicated with exhaust port and first relief opening 53 and the cut-out exhaust port and second relief opening 55 in a phase place when rotating, at another phase place connection exhaust port and second relief opening 55 and the cut-out exhaust port and first relief opening 53.Main shaft 48 is through belt wheel 21 hydraulic-pressure pump 27 that is in transmission connection; Hydraulic-pressure pump 27 imports second oil back chamber 13 through first hydraulically-controlled one-way valve 23 and the 4th oil back chamber 32 is communicated with in the oil circuit that forms; Import first oil back chamber 6 through second hydraulically-controlled one-way valve 46 and be communicated with in the oil circuit that forms with the 3rd oil back chamber 39, hydraulic-pressure pump 27 bypass are provided with a relief valve 26.
Working principle of the present invention: starting component 49 startings; Drive main shaft 48 rotations; Main shaft 48 rotations drive the first reciprocating type dual-volume storage pump 47 and second reciprocating type dual-volume storage pump 22 motions; Cause two displacement pumps up and down cavity volume change, the power oil pocket of the corresponding respectively two groups of opposed pistons assembly oil cylinders of the hydraulic fluid port of two displacement pumps receive hydraulic fluid port.The corresponding second power oil pocket 16 of second reciprocating type dual-volume storage pump 22 hydraulic fluid ports and corresponding first power oil pocket 3 of the 4th power oil pocket 28, the first reciprocating type dual-volume storage pump 47 hydraulic fluid ports and the 3rd power oil pocket 41, the volume-variation of displacement pump is directly coupled to two groups of pistons and moves.
Process one, starting component 49 startings drive main shaft 48 rotations, the volume-variation of the first reciprocating type dual-volume storage pump 47 and the second reciprocating type dual-volume storage pump 22.
The first single cylinder double-piston opposed type fluid power motor group 1: first piston 5, second piston 14 move inward; First combustion powered chamber 11 compressions; Air inlet distributing valve 56 control first suction port 52 is closed, and exhaust distributing valve 57 controls first relief opening 53 is closed, and first breather check valve 51, second breather check valve 18 are opened; Second exhaust check valve 19, first exhaust check valve 50 are closed, and the first scavenging chamber 7, the second scavenging chamber 12 begin inflation.
The second single cylinder double-piston opposed type fluid power motor group 43: air inlet distributing valve 56 controls second suction port 54 is closed, and exhaust distributing valve 57 controls second relief opening 55 is closed.The 3rd piston 40, the 4th piston 31 outwards move, and the second combustion powered chamber, 35 volumes increase, and the 3rd exhaust check valve 45, the 4th exhaust check valve 24 are opened, and the 3rd scavenging chamber 37, the 4th scavenging chamber 33 pressurized air are discharged to gas holder 9 and collect.
Process two, rotating spindle 48 be to several angle, the top dead center of the first reciprocating type dual-volume storage pump 47 and the second reciprocating type dual-volume storage pump 22.
Opposed first piston 5, second piston 14 are compressed to the terminal inner dead point in 1: the first combustion powered chamber 11 of the first single cylinder double-piston opposed type fluid power motor group, and fuel is by Injection Pump 20 pumps oil, and first oil sprayer 10 sprays into, and fire burns, begins to expand.First breather check valve 51, second breather check valve 18 begin to close, and second exhaust check valve 19, first exhaust check valve 50 begin to open, the first scavenging chamber 7, the second scavenging chamber, 12 beginning pump gas.
Opposed the 3rd piston 40, the 4th piston 31 move to maximum outer dead point to two ends in 43: the second combustion powered chambeies 35 of the second single cylinder double-piston opposed type fluid power motor group; Exhaust distributing valve 57 controls second relief opening 55 is opened; Air inlet distributing valve 56 controls second suction port 54 is opened, and accomplishes the distribution process.The 3rd exhaust check valve 45, the 4th exhaust check valve 24 begin to close, and the 3rd breather check valve 44, the 4th breather check valve 25 begin to open, and the 3rd scavenging chamber 37,33 beginnings of the 4th scavenging chamber are air-breathing.
Process three, rotating spindle 48 are crossed the top dead center of the first reciprocating type dual-volume storage pump 47 and the second reciprocating type dual-volume storage pump 22 to several angle
The catch fire acting of expanding of 1: the first combustion powered chamber 11 of the first single cylinder double-piston opposed type fluid power motor group promotes first piston 5, second piston 14 and outwards moves; Promote the first reciprocating type dual-volume storage pumps 47 and second reciprocating type dual-volume storage pump 22 motions through the first power oil pocket 3, the second power oil pocket 16; Act on main shaft 48 and transfer to and rotatablely moving, and external outputting power.First breather check valve 51, second breather check valve 18 are closed, and second exhaust check valve 19, first exhaust check valve 50 are opened, and the scavenging chamber begins exhaust.
The second single cylinder double-piston opposed type fluid power motor group 43: the three pistons 40, the 4th pistons 31 move inward in opposite directions; The second combustion powered chamber 35 begins compression; Exhaust distributing valve 57 control second relief opening 55 is closed, and air inlet distributing valve 56 controls second suction port 54 is closed, and the 3rd exhaust check valve 45, the 4th exhaust check valve 24 are closed; The 3rd breather check valve 44, the 4th breather check valve 25 are opened, and the 3rd scavenging chamber 37, the 4th scavenging chamber 33 begin inflation.
Process four, rotating spindle 48 be to several angle, the lower dead center of the first reciprocating type dual-volume storage pump 47 and the second reciprocating type dual-volume storage pump 22.
1: the first combustion powered chamber of the first single cylinder double-piston opposed type fluid power motor group, 11 interior first piston 5, second pistons 14 expand and do work to outermost end; The outer dead point position; Exhaust distributing valve 57 controls first relief opening 53 is opened; Air inlet distributing valve 56 controls first suction port 52 is opened, and cylinder begins uniflow scavenging, accomplishes the distribution process.First breather check valve 51, second breather check valve 18 begin to open, and second exhaust check valve 19, first exhaust check valve 50 begin to close, and first scavenge space 7, second scavenge space 12 are accomplished scavengings.
The 3rd piston 40 in the combustion powered chamber 35 of the second single cylinder double-piston opposed type fluid power motor group 43: the second, the 4th piston 31 move near compression and finish to the inner dead point position; Main shaft 48 drives Injection Pump 20 pumps oil; Through 34 oil spouts of second oil sprayer, the burning expansion acting.The 4th breather check valve 25, the 3rd breather check valve 44 begin to close, and the 3rd exhaust check valve 45, the 4th exhaust check valve 24 begin to open, and inflation is accomplished in the 3rd scavenging chamber 37, the 4th scavenging chamber 33.
The whole circulation process is gone round and begun again, and repeats.
Can find out that from above process its working method is similar with two cylinder uniflow scavenging two stroke diesel engines.Adopt EFI, then become petrol engine with spark ignitor.
The present invention compares with existing free-piston, and the opposed pistons motion is controlled, and compression ratio is fixing within the specific limits, thereby guarantees the running of motor optimum working state.Two groups of opposed pistons movement velocitys are identical, in the opposite direction, and dynamic balance is good, and the high frequency oscillation that the explosion expansion produces can be absorbed by hydraulic pressure.Main shaft, vital parts such as piston, the one, part number is few, and simple structure is easy to process.The power transmission hydraulic pipe line is direct-connected, needn't pass through valve, and control system does not have solenoid valve, and the control unit that inductor etc. are complicated is reliable and stable, and the motor overall volume especially highly greatly reduces.
The pump gas group that air distributing device shown in Figure 1 is made up of first breather check valve 51, second breather check valve 18, the 3rd breather check valve 44, the 4th breather check valve 25, first exhaust check valve 50, second exhaust check valve 19, the 3rd exhaust check valve 45 and the 4th exhaust check valve 24; The gas of discharging is by gas holder 9 storages; And the air inlet distributing valve arranged; Distribute to get into, waste gas is discharged by 57 controls of exhaust distributing valve, and exhaust is formed and can be made up of various ways.
Fig. 2 cancels air inlet distributing valve 56 and exhaust distributing valve 57, by first suction port 52, first relief opening 53, second suction port 54 and the 55 direct distributions of second relief opening.
Fig. 3 forms the distribution assembly by the formed first scavenging chamber 7 of piston nose, the second scavenging chamber 12, the 3rd scavenging chamber 37 and the 4th scavenging chamber 33 through first breather check valve 51, second breather check valve 18, the 3rd breather check valve 44, the 4th breather check valve 25 first exhaust check valves 50, second exhaust check valve 19, the 3rd exhaust check valve 45 and the 4th exhaust check valve 24 and first suction port 52, first relief opening 53, second suction port 54 and second relief opening 55.
Shown in Figure 4; Cancel the first scavenging chamber 7, the second scavenging chamber 12, the 3rd scavenging chamber 37 and the 4th scavenging chamber 33; Main shaft 48 air compressor 58 that is in transmission connection, the air compressor 58 and first suction port 52, first relief opening 53, second suction port 54 and second relief opening 55 are formed gas distribution systems.
Shown in Figure 5 is the structure of the reciprocal conversion equipment of dual-volume storage; Outer slide 224 is located in the square oil cylinder 221 and is formed with two volumes that are connected with the power oil pocket respectively at outer slide 224 with two ends between the square oil cylinder 221; In outer slide 224, be provided with inner slide 223; Be fixed with eccentric wheel 222 on the main shaft 48, eccentric wheel 222 flip sleeves are contained in the inner slide 223.Be formed with two two volume oil pockets up and down that are connected with the power oil pocket respectively at outer slide 224 with two ends between the square oil cylinder 221, the first power oil pocket 3 that the hydraulic fluid port of two displacement pump oil pockets is corresponding respectively to be connected, the second power oil pocket 16, the 3rd power oil pocket 41 and the 4th power oil pocket 28.Rotating spindle 48, the variation of two volume oil pockets up and down then cause the variation that moves forward and backward of outer slide 224 and inner slide 223, otherwise outer slide 224 then causes rotatablely moving of main shaft 48 with seesawing of inner slide 223.Reciprocating type double volume pump has various ways, existing reciprocating hydraulic pump, and radial plunger pump that contains eccentric stiffener etc. can both make into, like Fig. 6 and shown in Figure 7.
Fig. 6 contains the reciprocal dual-volume storage pump structure of eccentric stiffener schematic representation.
Fig. 7 contains the reciprocal dual-volume storage pump structure of crankshaft & connecting schematic representation; The structure of the reciprocal conversion equipment of dual-volume storage is that first piston 602 is located in the oil cylinder 601 and is formed with two volumes that are connected with the power oil pocket respectively at first piston 602 with two ends between the oil cylinder 601, and first piston 602 is in transmission connection through linkage mechanism 603 and described main shaft 48.
Fig. 8 and air distributing device shown in Figure 9 are on main shaft 48, to be connected with air inlet distributing valve 56 and exhaust distributing valve 57; The structure of air inlet distributing valve 56 be on main shaft 48, endwisely slip, circumferentially fixed cover is equipped with cone valve 562 outside the air inlet; On main shaft 48, be fixed with air inlet limited ring 564; Be provided with air inlet between the outer cone valve 562 of air inlet limited ring 564 and air inlet and hold out against spring 563; The outer cone valve 562 of air inlet is provided with the air inlet waveform groove; Rotating sleeve is equipped with cone valve 561 in the air inlet on the cone valve 562 outside air inlet; Cone valve 561 is provided with two exhaust ports that are connected with two combustion powered chambeies respectively and one and the tank connected inlet hole of gas storage in the air inlet, and the outer cone valve 562 of air inlet makes air inlet waveform annular groove be communicated with inlet hole with first exhaust port and cut off inlet hole and second exhaust port in a phase place when rotating, at another phase place connection inlet hole and second exhaust port and cut-out inlet hole and first exhaust port; The structure of exhaust distributing valve 57 be on main shaft 48, endwisely slip, circumferentially fixed cover is equipped with cone valve 572 outside the exhaust; On main shaft 48, be fixed with exhaust limited ring 574; Be provided with exhaust between the outer cone valve 572 of exhaust limited ring 574 and exhaust and hold out against spring 573; The outer cone valve 572 of exhaust is provided with air inlet waveform annular groove; Rotating sleeve is equipped with cone valve 571 in the exhaust on the cone valve 572 outside exhaust, and cone valve 571 is provided with the exhaust port of two inlet holes that are connected with two combustion powered chambeies respectively and an emptying in the exhaust, and the outer cone valve 572 of exhaust makes air inlet waveform annular groove be communicated with exhaust port and first inlet hole and cut-out exhaust port and second inlet hole in a phase place when rotating; Be communicated with exhaust port and second inlet hole and cut-out exhaust port and first inlet hole in another phase place, be equivalent to rotary three-way valve.Three-way valve has various ways, can be cylindrical, conical, footpath phase plane type.Also reciprocating type three-way valve, solenoid valve is given in the position on the main shaft 48 capable of using induction mutually, can direct-connected main shaft 48 on the layout, also vertical shaft system is associated with main shaft 48 in addition.Form is varied.
Figure 10 is a kind of rotary cylindrical three-way valve structural representation.
Claims (7)
1. twin-tub four piston opposed type hydraulic control motors; Comprise main shaft (48) and the starting component (49) that is in transmission connection with described main shaft (48); It is characterized in that: be provided with two groups of single cylinder double-piston opposed type fluid power motor groups; Every group of described single cylinder double-piston opposed type fluid power motor group has a combustion powered chamber and two pistons; Two described pistons are done the reverse sync motion; Be formed with a power oil pocket and oil back chamber between each described piston and the cylinder body; Described combustion powered chamber is provided with air distributing device and fuel injector igniter; The operating movement mode of the piston of two groups of described single cylinder double-piston opposed type fluid power motor groups is provided with on the contrary; Described main shaft 48 is connected with two groups of reciprocal conversion equipments of dual-volume storage; A volume of first group of reciprocal conversion equipment of described dual-volume storage is connected with the power oil pocket of the described piston of an end of first group of described single cylinder double-piston opposed type fluid power motor group, and another volume is connected with the power oil pocket of the described piston of an end of second group of described single cylinder double-piston opposed type fluid power motor group, and a volume of second group of reciprocal conversion equipment of described dual-volume storage is connected with the power oil pocket of the described piston of the other end of first group of described single cylinder double-piston opposed type fluid power motor group; Another volume is connected with the power oil pocket of the described piston of the other end of second group of described single cylinder double-piston opposed type fluid power motor group, and the oil back chamber of a piston of first group of reciprocal conversion equipment of described dual-volume storage is connected with the oil back chamber of a piston of second group of described single cylinder double-piston opposed type fluid power motor group.
2. twin-tub four piston opposed type hydraulic control motors according to claim 1; It is characterized in that: the structure of the reciprocal conversion equipment of described dual-volume storage is that outer slide (224) is located in the square oil cylinder (221) and is formed with two volumes that are connected with the power oil pocket respectively at described outer slide (224) with two ends between the described square oil cylinder (221); In described outer slide (224), be provided with inner slide (223); Be fixed with eccentric wheel (222) on the described main shaft (48), described eccentric wheel (222) flip sleeve is contained in the described inner slide (223).
3. twin-tub four piston opposed type hydraulic control motors according to claim 1; It is characterized in that: the structure of the reciprocal conversion equipment of described dual-volume storage is that first piston (602) is located in the oil cylinder (601) and is formed with two volumes that are connected with the power oil pocket respectively at described first piston (602) with two ends between the described oil cylinder (601), and described first piston (602) is in transmission connection through linkage mechanism (603) and described main shaft (48).
4. twin-tub four piston opposed type hydraulic control motors according to claim 1 and 2; It is characterized in that: described air distributing device is on the described cylinder body of described single cylinder double-piston opposed type fluid power motor group, to be provided with the plunger that cooperates insertion with each described piston; Be formed with scavenge space between described piston and the described plunger; On described cylinder body, be provided with the breather check valve and the exhaust check valve that are communicated with described scavenge space; Described exhaust check valve is connected with gas holder; Described gas holder is connected with air distributing device, and described air distributing device is communicated with the described combustion powered chamber of two groups of described single cylinder double-piston opposed type fluid power motor groups respectively.
5. twin-tub four piston opposed type hydraulic control motors according to claim 4; It is characterized in that: described air distributing device is on described main shaft (48), to be connected with air inlet distributing valve (56) and exhaust distributing valve (57); The structure of described air inlet distributing valve (56) be on described main shaft (48), endwisely slip, circumferentially fixed cover is equipped with cone valve outside the air inlet (562); On described main shaft 48, be fixed with air inlet limited ring (564); Be provided with air inlet between the outer cone valve (562) of described air inlet limited ring (564) and described air inlet and hold out against spring (563); The outer cone valve (562) of described air inlet is provided with the air inlet waveform groove; Cone valve outside described air inlet (562) is gone up rotating sleeve cone valve in the air inlet (561) is housed; Cone valve (561) is provided with two exhaust ports that are connected with two described combustion powered chambeies respectively and one and the tank connected inlet hole of described gas storage in the described air inlet, and the outer cone valve (562) of described air inlet makes described air inlet waveform annular groove be communicated with inlet hole with first exhaust port and cut off inlet hole and second exhaust port in a phase place when rotating, at another phase place connection inlet hole and second exhaust port and cut-out inlet hole and first exhaust port; The structure of described exhaust distributing valve (57) be on described main shaft (48), endwisely slip, circumferentially fixed cover is equipped with cone valve outside the exhaust (572); On described main shaft (48), be fixed with exhaust limited ring (574); Be provided with exhaust between the outer cone valve (572) of described exhaust limited ring (574) and described exhaust and hold out against spring (573); The outer cone valve (572) of described exhaust is provided with air inlet waveform annular groove; Cone valve outside described exhaust (572) is gone up rotating sleeve cone valve in the exhaust (571) is housed; Cone valve (571) is provided with two inlet holes that are connected with two described combustion powered chambeies respectively and the exhaust port of an emptying in the described exhaust; The outer cone valve (572) of described exhaust makes described air inlet waveform annular groove be communicated with exhaust port with first inlet hole and cut off exhaust port and second inlet hole in a phase place when rotating, at another phase place connection exhaust port and second inlet hole and cut-out exhaust port and first inlet hole.
6. twin-tub four piston opposed type hydraulic control motors according to claim 1 and 2, it is characterized in that: the oil back chamber of described single cylinder double-piston opposed type fluid power motor group is connected with oil hydraulic pump (27) through hydraulically-controlled one-way valve, relief valve (26).
7. twin-tub four piston opposed type hydraulic control motors according to claim 1 and 2, it is characterized in that: the power oil pocket of same described piston and oil back chamber are provided with bypass tube in the motion lower dead center of described piston.
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| CN2011103354292A CN102400784B (en) | 2011-10-28 | 2011-10-28 | Double-cylinder four-piston opposed hydraulic control engine |
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| CN2011103354292A CN102400784B (en) | 2011-10-28 | 2011-10-28 | Double-cylinder four-piston opposed hydraulic control engine |
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| CN102400784B CN102400784B (en) | 2013-04-24 |
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Cited By (4)
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| CN103628981A (en) * | 2013-07-18 | 2014-03-12 | 常毅 | Piston type hydraulic engine |
| CN106337735A (en) * | 2016-08-26 | 2017-01-18 | 北京理工大学 | Opposite piston type hydraulic output engine |
| CN109958533A (en) * | 2019-03-28 | 2019-07-02 | 浙江大学 | Fluid power motor |
| CN110886651A (en) * | 2019-02-02 | 2020-03-17 | 烟台小米机械技术有限公司 | Double-acting hydraulic engine and working method thereof |
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| CN102400784B (en) | 2013-04-24 |
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