CN101555827A - Arc cylinder load response engine - Google Patents

Arc cylinder load response engine Download PDF

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Publication number
CN101555827A
CN101555827A CNA2008101775401A CN200810177540A CN101555827A CN 101555827 A CN101555827 A CN 101555827A CN A2008101775401 A CNA2008101775401 A CN A2008101775401A CN 200810177540 A CN200810177540 A CN 200810177540A CN 101555827 A CN101555827 A CN 101555827A
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cylinder
control gear
piston
connecting rod
adjustable
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CN101555827B (en
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靳北彪
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Abstract

The invention discloses an arc cylinder load response engine. The arc cylinder load response engine comprises cylinders and pistons. Central line of the cylinders is an arc, and a piston connector of the pistons is arranged outside a sealed section of a combustion chamber of the cylinders. The cylinders and the pistons rotate and relatively swing with center of a circle of the central line of the cylinders as center. In the cylinders, cylinders which are clockwise set are cylinder group A, cylinders which are anticlockwise set are cylinder group B, all pistons clockwise set are piston group A, all pistons anticlockwise set are piston group B, an adjustable swinging angle control device is arranged between a cylinder system A represented by the cylinder group A and a cylinder system B represented by the cylinder group B, and a stroke control device is arranged between a swing system represented by all the cylinders and a swing system represented by all the pistons. The engine can regulate discharge capacity of the engine, and enhance efficiency of the engine.

Description

Arc cylinder load response engine
Technical field
The present invention relates to engine art.
Background technique
As everyone knows, reciprocating internal combustion engine has had the history in more than 100 year, is a kind of extremely successful hot merit switch machine.But because the human at present energy and the environmental problem that is faced had higher requirement to the hot merit switch machine.Thereby reciprocating internal combustion engine just seems that volume is big, weight is big, efficient is low, low emission is poor.Therefore in the last few years, people began to pay attention to especially the research and development of free piston engine, pendulum piston type rotor engine and oscillating piston engine.Compare characteristics such as free piston engine has efficiently, low emission is good, and volume is little, in light weight with reciprocating-piston engine.Yet, because free piston engine mostly is two-stroke, and can't directly use as the rotational power source, so many power as generator, its application area also just is restricted.And oscillating piston engine and pendulum piston type rotor engine are because due to the mutual assembly relation of its cylinder body and piston, its sealing, working life and low emission are had a strong impact on, and moreover also there are the transfer problem of swing type or title pulsed power and rotating power in oscillating piston engine and pendulum piston type rotor engine.
In the recent period more about the research and the scheme of oscillating piston engine and pendulum piston type rotor engine, for example U.S. Pat 6,431, and 139; US4,068,985; US3,144,007; US3,356,079; US5,147,191; US3,873,247; US4,174,930; US2,734,489; US6,886,527; US6,305,345; US5,433,179; US4,257,752; US6,009,847 and US2006/0191499 etc., world patent WO2008/104569; WO2008/012006; WO2007/096154; WO2007/073883; WO2006/089576; WO2003/093650; WO2003/074839; WO2002/084078; WO2000/060218; WO2000/042290; WO1998/026157 and WO1998/013558 etc., and Chinese patent ZL01134215.3 and ZL91201678.7 etc., multi-form oscillating piston engine and pendulum piston type rotor engine are all disclosed, the disclosed scheme of not mentioning at this paper but all these and the applicant consulted of patent all exists a common shortcoming, and there is the sliding interface of piston link in (wall thickness direction) in the cylinder wall in combustion chamber of air cylinder's seal section exactly.No matter to motor or gas compressor, its sealing all is vital, and particularly concerning motor, its sealing has determined performance, efficient and the life-span of motor, is the most important problem in engine design and the manufacture process.And the sealing that is present in the sliding interface of (wall thickness direction) in the cylinder wall of combustion chamber of air cylinder's seal section is unusual difficulty, particularly because the factors such as cold shrinkage and thermal expansion of motor make the sealing of this sliding interface more be difficult to solve.So the sealing by the engine chamber of disclosed scheme production in the above-mentioned patent is difficult to be protected, these schemes also will be difficult to be used widely in the manufacturing of commercialization motor.U.S. Pat 4,058,088 discloses the scheme of a kind of straight line type cylinder and slide block structure.In this scheme, because cylinder is rectilinear, so can only arrange by the string of a musical instrument of circle.Meet at right angles between two cylinders or between two cylinder in-blocks, thus between two cylinders or the idle space between two cylinder in-blocks big, thereby caused the big weight of this scheme volume big.Moreover,, reduced the reliability of motor, particularly, can only bear, so influenced the seal and the efficient of motor by the outside inwall of cylinder because the huge centrifugal force that the piston swing produces can't be offset by the piston link owing to the existence of slide block.In addition, present all oscillating piston engines, pendulum piston type rotor engine and free piston engine, the employing oil hydraulic motor, or adopt bent axle, noncircular gear or cam bawl formula ratchet that swing type power or title pulsed power-converting are become rotational power.Problems such as all there is poor reliability in these schemes, and efficient is low.For this reason, the inventor discloses arc cylinder rotary motor patent (application number 200810172692.2,200820178435.5), for the manufacturing of motor provides new approaches.Yet, for further improving the efficient of arc Cylinder engine, need invention a kind of air displacement (stroke) and the controllable novel arc Cylinder engine of geometrical compression ratio, to improve efficient, low emission and the practicability of arc Cylinder engine.
Summary of the invention
The greatest drawback of conventional reciprocating formula motor is that piston does not have moment to bent axle at blast stroke top dead center, and also less in suitable corner moment of resistance, thereby make high temperature and high pressure gas in the cylinder long heat loss that causes of holding time big, nitrogen oxide forms many, and efficient is low, and it is poor to discharge.And arc cylinder rotary formula motor is quite different, and piston just has very big moment when the blast stroke begins, and the burning indoor gas expands fast, and heat loss is little, and nitrogen oxide forms few, and the efficient height discharges.But, if can make the air displacement (stroke) and the geometrical compression ratio of arc cylinder rotary motor controllable, then will increase substantially the efficient of arc Cylinder engine.
Which kind of explosive motor all is a kind of hot merit switch machine.The core of its efficient is the temperature and pressure after cylinder combustion is burnt, i.e. operating mode after the burning.Operating mode after the burning directly determines the thermal efficiency of motor, and the operating mode after the burning is to be determined by operating mode before the burning and air fuel ratio basically.So pressure, temperature and air fuel ratio in the burning front air cylinder have determined the thermal efficiency of motor basically, and the amount of air decision motor power in the cards.Say that in principle the temperature after burning high pressure more is also just big more, efficient is also just high more.Under the prerequisite of the practical factors such as heat load of the intensity of considering detonation, material and material, a kind of fuel has only an optimum condition, i.e. optimum temperature value, optimum pressure value and an optimal air-fuel ratio value, and this optimum value of any one parameter drift-out all can have a strong impact on the efficient of motor in temperature, pressure and the air fuel ratio.Because the throttle effect of the distribution device of motor is very big, so when engine load and rotating speed change, the amount that single suction stroke sucks the air in the cylinder is different, because the geometrical compression ratio of conventional engines is a definite value, so the interior temperature and pressure of cylinder also is different when compression stroke is over.In diesel engine, because of there not being closure, the low more inhaled air of rotating speed is many more, and the temperature and pressure after the compression is also high more.Load often little the time and rotating speed is low, so can only in cylinder, spray into a small amount of fuel oil, cause air fuel ratio to depart from optimum value significantly and then have a strong impact on the thermal efficiency of motor, and because the existence of a large amount of remaining oxygens has caused the generation befouling environment of a large amount of nitrogen oxide.In petrolic, have to be provided with closure owing to consider the problem that gasoline is lighted, but motor air inflow when low speed is reduced so that when spraying into a small amount of fuel oil ignition engine still, temperature, pressure when therefore this causes petrol engine compression stroke is over when slow-speed of revolution low-load is very low, operating mode substantial deviation optimum value, the efficient of motor also descend significantly.This shows that when rotating speed and load changed, the operating mode of conventional engines and air fuel ratio all can depart from optimum value significantly, thereby cause the efficient of motor seriously to descend, the discharging severe exacerbation.If when the rotating speed of motor and load change, all can keep the optimum condition and the optimal air-fuel ratio of motor, then will significantly improve the efficient and the feature of environmental protection of motor.For realizing this purpose, must make engine exhaust amount (being stroke) and geometrical compression ratio simultaneously adjustable.
Purpose of the present invention will disclose a kind of air displacement (stroke) and the controllable novel arc Cylinder engine of geometrical compression ratio exactly.Get final product based on fuel difference and load variations, adjust the arc Cylinder engine of air displacement (stroke) and geometrical compression ratio, just so-called arc cylinder load response engine is to improve efficient, low emission and the practicability of motor.
The invention discloses a kind of arc cylinder load response engine, comprising: cylinder, piston its objective is such realization;
The center line of described cylinder is made as arc, the section of described cylinder is made as circular or non-circular, one or more described pistons are set in described cylinder, the piston link of described piston is located at outside the combustion chamber sealing section of described cylinder, described cylinder is center of circle rotation and relative swing type with the center of circle that described piston is made as with described cylinder axis camber line, or be made as stationary phase to swing type, all described cylinders that are provided with clockwise are made as cylinder block A in the described cylinder, all described cylinders that are provided with counterclockwise are made as cylinder block B, all described pistons that are provided with clockwise are made as piston set A in the described piston, all described pistons that are provided with counterclockwise are made as piston set B, between the cylinder system B of the cylinder system A of described cylinder block A representative and described cylinder block B representative, adjustable pivot angle control gear is set, between the oscillation system of the oscillation system of all described cylinder representatives and all described piston representatives, the adjustable travel control gear is set; Or between the piston system B of the piston system A of described piston set A representative and described piston set B representative, adjustable pivot angle control gear is set, between the oscillation system of the oscillation system of all described cylinder representatives and all described piston representatives, the adjustable travel control gear is set; Or between the piston system D of the piston system C of the described piston set A representative of half and the described piston set B representative of half, described adjustable pivot angle control gear is set, between system that the piston system D of the piston system C of the described piston set A representative of half and the described piston set B representative of half is constituted and described cylinder, described adjustable travel control gear is set; Or between the cylinder system D of the cylinder system C of the described cylinder block A representative of half and the described cylinder block B representative of half, described pivot angle control gear is set, between the system that cylinder system D constituted of the cylinder system C of the described cylinder block A representative of half and the described cylinder block B representative of half and described piston, described adjustable travel control gear is set.
A described piston is set in a described cylinder, end at described cylinder is provided with cylinder head, constitute the unit cylinder, at least two described unit of opposite disposed cylinder constitutes multicylinder engine on the circumference of camber line place, the center of described cylinder, in described multicylinder engine, described cylinder block A is made as through cylinder connection piece and half line shaft A jointing type, described cylinder block B is made as through cylinder connection piece again through described adjustable pivot angle control gear and described half line shaft A jointing type, all described pistons are made as through described piston link and described half line shaft B jointing type, respectively between the described piston link of the described cylinder connection piece of described cylinder system A and described piston system A, and between the described piston link of the described cylinder connection piece of described cylinder system B and described piston system B described adjustable travel control gear is set; Or all described cylinders are made as through described cylinder connection piece and described half line shaft A jointing type, described piston set A is made as through described piston link and described half line shaft B jointing type, described piston set B is made as through described piston link again through described adjustable pivot angle control gear and described half line shaft B jointing type, respectively between the described piston link of the described cylinder connection piece of described cylinder system A and described piston system A, and between the described piston link of the described cylinder connection piece of described cylinder system B and described piston system B described adjustable travel control gear is set; Or the center of circle that all described cylinders are made as with described cylinder axis camber line is that the center of circle is driven rotary or fixed, the described piston set A of half is made as through described piston link and described half line shaft A jointing type, the described piston set B of half be made as through described piston link with after described adjustable pivot angle control gear is connected again with described half line shaft A jointing type, the described piston set A of half is made as through other described piston link and described half line shaft B jointing type in addition, the described piston set B of half is made as after the described adjustable pivot angle control gear of other described piston link and another is connected and described half line shaft B jointing type again in addition, respectively between described piston link and described cylinder connection piece, and described adjustable travel control gear is set between described piston link and the described cylinder connection piece.
Two described pistons of opposite disposed constitute cylinder in-block in the described cylinder, in the multicylinder engine that described cylinder in-block constitutes by two or more, it is that the center of circle is driven rotary or fixed that all described cylinders are made as with its center of circle, camber line place, center, the described piston set A of half is made as through described piston link and described half line shaft A jointing type, the described piston set B of half be made as through described piston link with after described adjustable pivot angle control gear is connected again with described half line shaft A jointing type, the described piston set A of half is made as through other described piston link and described half line shaft B jointing type in addition, the described piston set B of half is made as after the described adjustable pivot angle control gear of other described piston link and another is connected and described half line shaft B jointing type again in addition, on described piston link between two adjacent described pistons of top and described piston link described adjustable travel control gear is set.
In a described cylinder, between two described pistons of opposite disposed the diaphragm type cylinder head is set, described diaphragm type cylinder head and described cylinder seal and with described cylinder every being divided into two described firing chambers, constitute dividing plate cylinder cap cylinder in-block, and formation dividing plate cylinder cap formula two cylinder, in described dividing plate cylinder cap two cylinders or multicylinder engine, all described cylinders are made as and described half line shaft A jointing type, described piston set A is made as through its described piston link and described half line shaft B jointing type, described piston set B is made as through its described piston link again through described adjustable pivot angle control gear and described half line shaft B jointing type, between the described cylinder connection piece of the described piston link of described piston set A and described cylinder block A, described adjustable travel control gear is set, and between the described cylinder connection piece of the described piston link of described piston set B and described cylinder block B, described adjustable travel control gear is set; Or all described cylinders to be made as with its center of circle, camber line place, center be that the center of circle is driven rotary or fixed, the described piston set A of half is made as through described piston link and described half line shaft A jointing type, the described piston set B of half be made as through described piston link with after described adjustable pivot angle control gear is connected again with described half line shaft A jointing type, the described piston set A of half is made as through other described piston link and described half line shaft B jointing type in addition, the described piston set B of half is made as after the described adjustable pivot angle control gear of other described piston link and another is connected and described half line shaft B jointing type again in addition, between the described cylinder connection piece of the described piston link of described piston set A and described cylinder block A, described adjustable travel control gear is set, between the described cylinder connection piece of the described piston link of described piston set B and described cylinder block B, described adjustable travel control gear is set.
Described adjustable pivot angle control gear is made as mechanical adjustable pivot angle control gear, the adjustable pivot angle control gear of described machinery is made as the adjustable pivot angle control gear of the leading screw that is made of controlled leading screw formula, or be made as the adjustable pivot angle control gear of the eccentric shaft that constitutes by controlled eccentric shaft formula, or be made as the adjustable pivot angle control gear of the cam that constitutes by controlled cam formula, described adjustable travel control gear is made as described mechanical adjustable travel control gear formula, described mechanical adjustable travel control gear is made as by connecting rod A, connecting rod B, the two connecting rod adjustable travel control gear formulas that free bearing pin and controlled end bearing pin constitute, or be made as by described connecting rod A, described connecting rod B, connecting rod C, the three connecting rod adjustable travel control gear formulas that free bearing pin and described controlled end bearing pin constitute.
Described adjustable pivot angle control gear is made as hydraulically adjustable pivot angle control gear, described hydraulically adjustable pivot angle control gear is made as the adjustable pivot angle control gear of the oil hydraulic cylinder that is made of oil hydraulic cylinder formula, or is made as the adjustable pivot angle control gear of the oil hydraulic cylinder two connecting rods formula that is made of oil hydraulic cylinder and two connecting rods; Described adjustable travel control gear is made as described hydraulically adjustable travel control device formula, described hydraulically adjustable travel control device is made as by the end bearing pin, the free end bearing pin, the single hydraulic cylinder two connecting rod adjustable travel control gear formulas that described connecting rod A and oil hydraulic cylinder connecting rod A constitute, or be made as by the end bearing pin, the free end bearing pin, the double hydraulic cylinder two connecting rod adjustable travel control gear formulas that described oil hydraulic cylinder connecting rod A and oil hydraulic cylinder connecting rod B constitute, or be made as by the end bearing pin, the free end bearing pin, described oil hydraulic cylinder connecting rod A, the single hydraulic cylinder three connecting rod adjustable travel control gear formulas that described connecting rod A and described connecting rod B constitute, or be made as by the end bearing pin, the free end bearing pin, described oil hydraulic cylinder connecting rod A, the double hydraulic cylinder three connecting rod adjustable travel control gear formulas that described connecting rod A and oil hydraulic cylinder connecting rod B constitute.
The control power of the adjustable pivot angle control gear of described leading screw, the adjustable pivot angle control gear of described eccentric shaft and the adjustable pivot angle control gear of described cam is made as hydraulic type or electrodynamic type; Described controlled end bearing pin is made as horizontal moving type controlled end bearing pin or is made as the controlled end of eccentric shaft type bearing pin, the control power of described horizontal moving type controlled end bearing pin and the controlled end of described eccentric shaft type bearing pin is made as hydraulic type or electrodynamic type, at described two connecting rod adjustable travel control gear, described three connecting rod adjustable travel control gear, described single hydraulic cylinder two connecting rod adjustable travel control gear, described double hydraulic cylinder two connecting rod adjustable travel control gear, on the connecting rod free end of the described push and pull system of described single hydraulic cylinder three connecting rod adjustable travel control gear and described double hydraulic cylinder three connecting rod adjustable travel control gear or the free end bearing pin bearing pin spring is set, the inertia body, slip inertia body, rotary inertia body and/or inertia body car, slip inertia body is set between the fixed end of the connecting rod of described slip inertia body and described push and pull system and/or the free end adjusts spring, described rotary inertia body is adjusted spring through the rotary inertia body and is connected with the connecting rod of vicinity, and described inertia body car is connected with vehicle-mounted inertia body through energy-storaging spring; Described two connecting rod adjustable travel control gear, described three connecting rod adjustable travel control gear, described single hydraulic cylinder two connecting rod adjustable travel control gear, described double hydraulic cylinder two connecting rod adjustable travel control gear, described single hydraulic cylinder three connecting rod adjustable travel control gear, described double hydraulic cylinder three connecting rod adjustable travel control gear, described bearing pin spring, described inertia body, described slip inertia body is adjusted spring, described slip inertia body, described rotary inertia body, described rotary inertia body is adjusted spring, described inertia body car, described energy-storaging spring and described vehicle-mounted inertia body are simultaneously or be arranged in the vacuum chamber separately.
Swing cooperating agency is set between the oscillation system of the oscillation system of described cylinder representative and described piston representative, or swing cooperating agency is set between the oscillation system of the oscillation system of described piston set A representative and described piston set B representative, the described cooperating agency of swinging is made as the moment of momentum flowing type swing cooperating agency that is made of two free rotary inertia structures and moment of momentum hysteresis spring separately, and described moment of momentum flowing type is swung in the cooperating agency can establish the vibration damping structure body.
In the center of circle that described cylinder and described piston is made as with described cylinder axis camber line is in center of circle rotation and the relative shuttle-type structure, on the oscillation system of the oscillation system of all described cylinder representatives and all described piston representatives, the hydraulic pressure anti kickback attachment is set respectively, or on the oscillation system of the oscillation system of described piston set A representative and described piston set B representative, described hydraulic pressure anti kickback attachment is set respectively, described hydraulic type anti kickback attachment is made as inlet and is provided with the oil hydraulic pump that check valve or inlet are provided with control valve, described oil hydraulic pump is made as the zero load anti-reversing oil hydraulic pump formula that the liquid gateway directly is communicated with, or be made as liquid outlet and the anti-reversing of load oil hydraulic pump formula arranged through what load loop was communicated with the liquid inlet, described load loop is made as the lubrication system of described arc cylinder load response engine or is made as the cooling system of described arc cylinder load response engine, described check valve is made as free style or controlled formula, the control mechanism of described control valve and the described check valve of controlled formula is made as mechanical type or electronic electromagnetic, described half line shaft B in the oscillation system of all described piston representatives is made as the line shaft jointing type with described oil hydraulic pump, described half line shaft A in the oscillation system of all described cylinder representatives is made as the line shaft jointing type with another described oil hydraulic pump, or half line shaft A in the oscillation system of described piston set A representative is made as the line shaft jointing type with described oil hydraulic pump, and the described half line shaft B in the oscillation system of described piston set B representative is made as the line shaft jointing type with another described oil hydraulic pump.
Described half line shaft A is made as a differential gear jointing type with differential mechanism, described half line shaft B is made as another differential gear jointing type with described differential mechanism, the planetary pinion shell of described differential mechanism is made as pto, and described arc cylinder load response engine and described differential mechanism are made as parallel-axis type or close coupled type.
The oscillation system of described piston representative is meant, described piston and follower thereof, for example, described piston link, described half line shaft, differential side gear etc.; The oscillation system of described cylinder representative is meant, described cylinder and follower thereof, for example, described cylinder connection piece, described half line shaft, differential side gear etc.; The oscillation system of described cylinder block A representative is meant, described cylinder block A and follower thereof, for example, described cylinder connection piece, described half line shaft, differential side gear etc.; The oscillation system of described cylinder block B representative is meant, described cylinder block B and follower thereof, for example, described cylinder connection piece, described half line shaft, differential side gear etc.; The oscillation system of described piston set A representative is meant, described piston set A and follower thereof, for example, the link of described piston set A, described half line shaft, differential side gear etc.; The oscillation system of described piston B representative is meant, described piston set B and follower thereof, for example, the link of described piston set B, described half line shaft, differential side gear etc.Other described systems by that analogy.Described cylinder and described piston are made as stationary phase swing type are meant, the class in described cylinder and the described piston is made as the fixed another kind of swing type that is made as.
Arc cylinder load response engine disclosed in this invention, by the adjustable pivot angle control gear of described machinery, described hydraulically adjustable pivot angle control gear, described mechanical adjustable travel control gear and/or described hydraulically adjustable travel control device are set, realize that the geometrical compression ratio of described arc cylinder load response engine and air displacement are simultaneously adjustable.Pivot angle control gear and travel control device can be made as various ways, as mechanical type, hydraulic type and electromagnetic type.But comparatively speaking, mechanical type and hydraulic type are more simple and direct effectively.
In mechanical type range-adjustable control gear, when the free end of described push and pull system during in collinear point, described piston begins reversing motion, the free end of described push and pull system must leave collinear point as early as possible, otherwise described push and pull system will influence the motion that described piston leaves lower dead center, influence the external output torque of described arc cylinder load response engine when the blast stroke begins, and then cause described arc cylinder load response engine decrease in efficiency.Described three bar linkage structures can make the free end of the described push and pull system that is in collinear point leave collinear point quickly than described two bar linkage structures, but described three bar linkage structures are than described two bar linkage structure complexity, and manufacture cost is also high.So-called collinear point are exactly when all bearing pins of push and pull system all are on the same straight line, the position of the residing point of free bearing pin.
For the free end of realizing push and pull system can leave collinear point apace, the present invention is provided with all kinds of inertia bodies in push and pull system.When two ends of push and pull system to separately away from the opposite direction motion time, because there is the existence of all kinds of inertia bodies that are provided with among inertia and the present invention in the free part in two connecting rods, three connecting rods and the many push and pull system, the two ends of push and pull system will be subjected to rightabout pulling force.In like manner, when two ends of push and pull system during to close separately opposite direction motion, because there is the existence of all kinds of inertia bodies that are provided with among inertia and the present invention in the free part in two connecting rods, three connecting rods and the many push and pull system, the two ends of push and pull system will be subjected to rightabout pulling force.Therefore, there is the motion that the push and pull system of inertia can two ends of control link system in free end, makes the motion of two ends more steady, can be so that the motion of described free-piston is more steady.Adjust the length of connecting rod or the link position of adjustment push and pull system end, just can adjust the stroke of free-piston.That is to say that push and pull system among the present invention and linkage structure thereof not only can make the stroke of described arc cylinder load response engine and geometrical compression ratio controllable, can also make the motor operation more steady.
No matter in two-stroke still at the described arc cylinder load response engine of four-stroke, a described arc cylinder load response engine can be provided with a plurality of described push and pull system, to satisfy the needs of each free-piston of control.Described bearing pin spring, described slip inertia body are adjusted spring, described inertia body, described slip inertia body, described slip inertia body adjustment spring, described rotary inertia body, described rotary inertia body adjustment spring, described inertia car, described through energy-storaging spring and described vehicle-mounted inertia body, can be provided with one or morely according to situation, also can according to circumstances use separately or use simultaneously.
Described bearing pin spring just is arranged on the spring on the bearing pin, being provided with of it can make the push and pull system operation more steady, also can make described free bearing pin can leave collinear point with the end bearing pin more quickly, thereby described free-piston the blast stroke when beginning external moment bigger, improve the efficient of motor.
Described inertia body is exactly the object with certain inertia, and described inertia body also can be arranged on the free end of connecting rod, by adjusting the quality of described inertia body, can make the push and pull system operation more steady.
Described slip inertia body adjustment spring is arranged on the spring on the connecting rod, the end that slip inertia body is adjusted spring is connected with the fixed end of connecting rod, also can be connected with the free end of connecting rod, as long as it is that described slip inertia body is moved to the fixed end direction of connecting rod that described slip inertia body is adjusted the effect of spring, the other end that described slip inertia body is adjusted spring acts on described slip inertia body, and described slip inertia body is had away from the free-ended trend of connecting rod.Because the effect of inertial force, this structure can make the free end of connecting rod have big inertia away from collinear point the time, have less inertia near collinear point.Therefore, described connecting rod free end can leave collinear point more quickly.
Described rotary inertia body is arranged on the connecting rod free end or the rotary eccentric inertia body on the described free end bearing pin.Described rotary inertia body is adjusted spring with described rotary inertia body and is connected.Because the effect of inertial force, this structure can make the free end of connecting rod when being in collinear point, is subjected to described rotary inertia body and obtains continuation thrust forward through the indirectly-acting of described rotation spring.Therefore, described connecting rod free end can leave collinear point more quickly.
Described inertia body car is arranged on the inertia body carrier member on the connecting rod free end or on the described free end bearing pin.Described inertia body car is provided with described energy-storaging spring, and an end of described energy-storaging spring is connected with described inertia body car, and the other end of described energy-storaging spring is connected with described vehicle-mounted inertia body.Because the effect of inertial force, this structure can make the free end of connecting rod when being in collinear point, is subjected to described vehicle-mounted inertia body and obtains continuation thrust forward through the indirectly-acting of described energy-storaging spring.Therefore, described connecting rod free end can leave collinear point more quickly.
Because when the operation of described arc cylinder load response engine, the free end of described push and pull system can high-speed motion, and the resistance of the free end high-speed motion that can reduce described push and pull system by being provided with of vacuum chamber improves the efficient of motor.
According to the information of engine throttle, rotating speed and load, become the action command of described adjustable pivot angle control gear and described adjustable travel control gear as calculated after the computer.Move respectively according to described adjustable pivot angle control gear of dependent instruction and described adjustable travel control gear, and then realize that the air displacement (stroke) of described arc cylinder load response engine and compression ratio are simultaneously adjustable.The power source of controlling described adjustable pivot angle control gear and described adjustable travel control gear can be made as electrodynamic type, hydraulic electric control formula.
For coordinating two relation such as Stroke Control and anti-collisioves etc. between the oscillation system, swing cooperating agency can be set between these two systems.So-called moment of momentum flowing type swing cooperating agency is provided with moment of momentum hysteresis spring between oscillation system A and the inertia structure A with certain rotary inertia that freely rotates, between the oscillation system B and the inertia structure B with certain rotary inertia of freely rotating moment of momentum hysteresis spring is set.Described inertia structure can be a flywheel, but different with Chinese patent 200720035408.8, and in Chinese patent 200720035408.8, flywheel directly connects firmly with oscillation system, and flywheel is in free state among the present invention.For preventing the bump of described oscillation system and described inertia structure, between two impact member, damping block is set.When swing takes place oscillation system, two oscillation systems will interlock and be subjected to moment of momentum hysteresis spring action, because have only the system of swing forwards just to be subjected to moment of momentum hysteresis spring action, Bai Dong system then is subjected to the direct effect of inertia structure backward.Adjust the inertia of inertia structure and the Hooke coefficient of moment of momentum hysteresis spring and mate different motors.
For realizing swing power or claiming of the conversion of pulse power to rotating power, all kinds of schemes so far all are to adopt the mechanical type anti-inversion organization, as ratchet, roller cam formula ratchet and roller friction type ratchet, or adopt noncircular gear or bent axle to finish this conversion.The former poor reliability, and the latter makes piston lose moment to line shaft when the blast stroke begins.Therefore the present mechanical type anti kickback attachment or the conversion of mechanical type rotating power are difficult to use in practice.The present invention is provided with the hydraulic pressure anti kickback attachment for realizing swing power or claiming the conversion of pulse power to rotating power.Described hydraulic pressure anti kickback attachment is exactly can only advance and can not fall back to a direction by two systems that fluid pressure can rotate relative swing again jointly.So just directly realized swing power or claimed of the conversion of pulse power to rotating power.This conversion is different fully with the oil hydraulic pump hydraulic motor system in the free piston engine that extensively adopts at present.Oil hydraulic pump hydraulic motor system in the free piston engine need with the oil hydraulic pump and the oil hydraulic motor of engine power coupling, be equivalent to be provided with in the power system dynamic power machine that three power equate, be motor, oil hydraulic pump and oil hydraulic motor, not only the cost high efficiency is also lower.The oil hydraulic pump that described hydraulic pressure anti kickback attachment among the present invention then only need be provided with control valve in very little liquid inlet gets final product, and cost is inefficient high.
Among the present invention, described hydraulic type anti-inversion organization is made as the oil hydraulic pump formula that inlet is provided with control valve.Described control valve is made as self-controlled type (being free style) check valve, controlled formula check valve or other Controlled valves, as be subjected to valve-control spherical etc., as long as can the inlet of oil hydraulic pump be opened close by logical relation (being equivalent to the timing relation), promptly (when entering the mouth the feed liquor body) opens the oil hydraulic pump inlet when oil hydraulic pump rotates forward, when oil hydraulic pump will turn round the oil hydraulic pump inlet closed.Because inlet is provided with such valve, liquid can only advance and can not go out, so the line shaft of oil hydraulic pump can not reverse.Described half line shaft or its link of described motor are connected with the line shaft of described oil hydraulic pump, just can reach the purpose of anti-reversing.From oil hydraulic circuit, can be made as zero load loop or two kinds of load loops are arranged.The structure of zero load anti-reversing oil hydraulic pump is at the place, liquid inlet of oil hydraulic pump control valve to be set, and the liquid gateway of pump directly is communicated with.Rotatable two oscillation systems in the motor disclosed in this invention are connected back (each system respectively connects a pump) respectively with the line shaft of described zero load anti-reversing oil hydraulic pump, oscillation system can't reverse, can only rotate forward, thereby finish of the conversion of swing power, make directly outputting rotary power of described arc cylinder load response engine to rotating power.In order to make full use of the energy of oil hydraulic pump, described hydraulic type anti-inversion organization also can be made as the anti-reversing of load oil hydraulic pump formula.Described have load to prevent that the reversing hydraulic pump structure is that inlet is provided with the oil hydraulic pump of the liquid gateway of control valve through the load loop connection, and described load loop is made as the lubrication system of described arc cylinder load response engine or is made as the cooling system of described arc cylinder load response engine.So can omit oil pump or the water pump and the power thereof of motor.Described oil hydraulic pump can be made as gear type, plunger type, blade type, rotator type or other forms.
For the rotating power that makes described arc Cylinder engine is exported steadily reliable, oscillation system is set to a differential gear jointing type with differential mechanism among the present invention, another oscillation system is made as another differential gear jointing type with differential mechanism, the differential pinion gear housing is made as pto.
Disclosed arc cylinder load response engine among the present invention, its intake duct, air outlet flue and oil circuit adopt the rotational slide joint to connect with gas handling system, vent systems and oil supply system respectively, and spark plug then adopts carbon brush or remote sensing form to connect.The valve of motor disclosed in this invention can adopt into row's common type list valve, or adopts and advance to arrange separately placed type dual valve or many valves.Valve can be arranged on the cylinder sleeve or piston of described cylinder cap, described diaphragm type cylinder head, described cylinder.The control of valve can be made as cammingly, electromagnetic type or hydraulic type.
Disclosed motor can be used as diesel engine among the present invention, also can be used as petrol engine, and two-stroke and four-stroke all can.
The present invention has following useful effect: described engine efficiency height, discharge, volume is little, low cost of manufacture, will open up a new road for the manufacturing of high-efficiency environment friendly h type engine h.
Description of drawings
Fig. 1 is an embodiment of the described arc cylinder load response engine of two described unit cylinders formations;
Fig. 2 is another embodiment of the described arc cylinder load response engine of two described unit cylinders formations;
Fig. 3 is first embodiment of the described arc cylinder load response engine of four described unit cylinders formations;
Fig. 4 is second embodiment of the described arc cylinder load response engine of four described unit cylinders formations;
Fig. 5 is an embodiment of the described arc cylinder load response engine of six described unit cylinders formations;
Fig. 6 is the 3rd embodiment of the described arc cylinder load response engine of four described unit cylinders formations;
Fig. 7 is an embodiment of the described arc cylinder load response engine of described cylinder in-block formation;
Fig. 8 is another embodiment of the described arc cylinder load response engine of described cylinder in-block formation;
Fig. 9 is an embodiment of the described arc cylinder load response engine of described dividing plate cylinder cap cylinder in-block formation;
Figure 10 is another embodiment of the described arc cylinder load response engine of described dividing plate cylinder cap cylinder in-block formation;
Figure 11 is an embodiment who is provided with the described arc cylinder load response engine of described hydraulically adjustable pivot angle control gear;
Figure 12 is an embodiment who is provided with the described arc cylinder load response engine of the adjustable pivot angle control gear of described leading screw;
Figure 13 is an embodiment who is provided with the described arc cylinder load response engine of the adjustable pivot angle control gear of described eccentric shaft;
Figure 14 is an embodiment who is provided with the described arc cylinder load response engine of adjustable pivot angle control gear of described cam and described two connecting rod adjustable travel control gear;
Figure 15 is provided with described three connecting rod adjustable travel control gear, an embodiment of the described arc cylinder load response engine of adjustable pivot angle control gear of described oil hydraulic cylinder two connecting rods and described controlled end bearing pin;
Figure 16 is another embodiment who is provided with the described arc cylinder load response engine of described controlled end bearing pin;
Figure 17 is an embodiment who is provided with the described arc cylinder load response engine of described single hydraulic cylinder two connecting rod adjustable travel control gear;
Figure 18 is an embodiment who is provided with the described arc cylinder load response engine of described double hydraulic cylinder two connecting rod adjustable travel control gear;
Figure 19 is an embodiment who is provided with the described arc cylinder load response engine of described single hydraulic cylinder three connecting rod adjustable travel control gear;
Figure 20 is an embodiment who is provided with the described arc cylinder load response engine of described double hydraulic cylinder three connecting rod adjustable travel control gear;
Figure 21 is an embodiment who is provided with the described arc cylinder load response engine of described bearing pin spring;
Figure 22 is an embodiment who is provided with the described arc cylinder load response engine of described inertia body;
Figure 23 is provided with the embodiment that described slip inertia body is adjusted the described arc cylinder load response engine of spring;
Figure 23 is that described mechanical adjustable travel control gear or described hydraulically adjustable travel control device are arranged on an embodiment in the vacuum chamber;
Figure 24 is an embodiment who is provided with the described arc cylinder load response engine of described rotary inertia body;
Figure 25 is an embodiment who is provided with the described arc cylinder load response engine of described inertia body car;
Figure 26 is a K view enlarged view;
Figure 27 is that the present invention swings the schematic representation that cooperating agency arranges;
Figure 28 is that moment of momentum flowing type of the present invention is swung cooperating agency's structural representation;
Figure 29 is that the C-C of Figure 24 is to sectional view;
Figure 30 is that the D-D of Figure 24 is to sectional view;
Figure 31 is the example structure schematic representation that has the vibration damping structure body in the moment of momentum flowing type swing cooperating agency;
Figure 32 is the sectional view that has the vibration damping structure body in another moment of momentum flowing type swing cooperating agency;
Figure 33 is the zero load oil hydraulic pump anti kickback attachment of a present invention structural representation;
Figure 34 is that the present invention has load oil hydraulic pump anti kickback attachment structural representation;
Figure 35 is the example structure schematic representation that arc cylinder running shaft of the present invention and differential mechanism output shaft are arranged in parallel;
Figure 36 is the example structure schematic representation of arc cylinder running shaft of the present invention and differential mechanism output shaft coaxial arrangement.
Embodiment
Accompanying drawing number
1. cylinder 101. center camber lines 2. pistons 3. piston links 4. firing chambers
501. cylinder block A 5010. cylinder system A 5020. cylinder system B 502. cylinder block B
600. adjustable pivot angle control gear 601. piston set A 602. piston set B 19. oscillation systems
18. oscillation system 700. adjustable travel control gear 6010. piston system A 6020. piston system B
6005. piston system C 6006. piston system D 5005. cylinder system C 5006. cylinder system D
5. cylinder head 9. unit cylinders 6601. cylinder connection pieces 6602. cylinder connection pieces
3001. piston link 3002. piston links 66. cylinder connection pieces 11. cylinder in-blocks
6. half line shaft A, 7. half line shaft B, 12. diaphragm type cylinder head
13. dividing plate cylinder cap cylinder in-block 60101. controlled leading screw 60102. controlled eccentric shafts
60103. the adjustable pivot angle control gear of controlled cam 6010 mechanical type pivot angle control gear, 6011. leading screws
6012. the adjustable pivot angle control gear of adjustable pivot angle control gear 6013. cams of eccentric shaft
701. mechanical adjustable travel control gear 70101. connecting rod A 70102. connecting rod B
70104. connecting rod C 70202. free bearing pin 70103. controlled end bearing pins
7011. two connecting rod adjustable travel control gear, 7012. three connecting rod adjustable travel control gear
6020. hydraulically adjustable pivot angle control gear 60201. oil hydraulic cylinders
6021. adjustable pivot angle control gear 60202. 2 connecting rods of oil hydraulic cylinder
6022. the adjustable pivot angle control gear 702. hydraulically adjustable travel control devices of oil hydraulic cylinder two connecting rods
70201. end bearing pin 70202. free end bearing pins 70203. oil hydraulic cylinder connecting rod A
7021. single hydraulic cylinder two connecting rod adjustable travel control gear 70204. oil hydraulic cylinder connecting rod B
7022. double hydraulic cylinder two connecting rod adjustable travel control gear
7023. single hydraulic cylinder three connecting rod adjustable travel control gear
7024. the controlled end of double hydraulic cylinder three connecting rod adjustable travel control gear 701031. horizontal moving types bearing pin
701032. the connecting rod free end of the controlled end of eccentric shaft type bearing pin 122. push and pull system
12301. bearing pin spring 12302. inertia bodies 12303. slip inertia bodies are adjusted spring
12304. slip inertia body 12305. rotary inertia bodies 12306. rotary inertia bodies are adjusted spring
12307. inertia body car 12308. energy-storaging springs 12309. vehicle-mounted inertia bodies
12310. vacuum chamber 1819. swing cooperating agency 181. oscillation systems, 182. oscillation systems
201. rotary inertia structure 202. rotary inertia structures 21. moment of momentum hysteresis springs
2021. moment of momentum flowing type swing cooperating agency 22. vibration damping structure bodies, 36. hydraulic pressure anti kickback attachments
116. check valve 126. control valves 127. oil hydraulic pumps 1271. zero load anti-reversing oil hydraulic pumps
1272. the line shaft of the anti-reversing of load oil hydraulic pump 33. lubrication systems 34. cooling systems 271. oil hydraulic pumps is arranged
272. line shaft 28. differential gears 29. differential gears 30. differential mechanisms of oil hydraulic pump
31. planetary pinion shell 32. ptos
Below in conjunction with the drawings and specific embodiments purpose of the present invention is elaborated:
Please refer to Fig. 1,2,3, arc cylinder load response engine shown in 4 and 5, comprise: cylinder 1, piston 2, the center line of described cylinder 1 is made as arc, the section of described cylinder 1 is made as circular or non-circular, one or more described pistons 2 are set in described cylinder 1, the piston link 3 of described piston 2 is located at outside firing chamber 4 seal sections of described cylinder 1, described cylinder 1 is center of circle rotation and relative swing type with the center of circle that described piston 2 is made as with described cylinder 1 center camber line 101, or be made as stationary phase to swing type, all described cylinders 1 that are provided with clockwise are made as cylinder block A501 in the described cylinder 1, all described cylinders 1 that are provided with counterclockwise are made as cylinder block B502, all described pistons 2 that are provided with clockwise are made as piston set A601 in the described piston 2, all described pistons 2 that are provided with counterclockwise are made as piston set B602, between the cylinder system B5020 of the cylinder system A5010 of described cylinder block A501 representative and described cylinder block B502 representative, adjustable pivot angle control gear 600 is set, between the oscillation system 18 of the oscillation system 19 of all described cylinder 1 representatives and all described piston 2 representatives, adjustable travel control gear 700 is set; Or between the piston system B6020 of the piston system A6010 of described piston set A601 representative and described piston set B602 representative, adjustable pivot angle control gear 600 is set, between the oscillation system 18 of the oscillation system 19 of all described cylinder 1 representatives and all described piston 2 representatives, adjustable travel control gear 700 is set; Or between the piston system D6006 of the piston system C6005 of the described piston set A601 representative of half and the described piston set B602 representative of half, described adjustable pivot angle control gear 600 is set, between system that the piston system D6006 of the piston system C6005 of the described piston set A601 representative of half and the described piston set B602 representative of half is constituted and described cylinder 1, described adjustable travel control gear 700 is set; Or between the cylinder system D5006 of the cylinder system C5005 of the described cylinder block A501 representative of half and the described cylinder block B502 representative of half, described pivot angle control gear 600 is set, between the system that cylinder system D5006 constituted of the cylinder system C5005 of the described cylinder block A501 representative of half and the described cylinder block B502 representative of half and described piston 2, described adjustable travel control gear 700 is set.
Please refer to Fig. 1,2,3,4, arc cylinder load response engine shown in 5 and 6, a described piston 2 is set in a described cylinder 1, in the end of described cylinder 1 cylinder head 5 is set, constitute unit cylinder 9, at least two described unit of opposite disposed cylinder 9 constitutes multicylinder engine on the circumference of camber line place, the center of described cylinder 1, in described multicylinder engine, described cylinder block A501 is made as through cylinder connection piece 6601 and half line shaft A6 jointing type, described cylinder block B502 is made as through cylinder connection piece 6602 again through described adjustable pivot angle control gear 600 and described half line shaft A6 jointing type, all described pistons 2 are made as through described piston link 3 and described half line shaft B7 jointing type, respectively between the described piston link 3001 of the described cylinder connection piece 6601 of described cylinder system A5010 and described piston system A6010, and between the described piston link 3002 of the described cylinder connection piece 6602 of described cylinder system B5020 and described piston system B6020 described adjustable travel control gear 700 is set; Or all described cylinders 1 are made as through described cylinder connection piece 66 and described half line shaft A6 jointing type, described piston set A601 is made as through described piston link 3001 and described half line shaft B7 jointing type, described piston set B602 is made as through described piston link 3002 again through described adjustable pivot angle control gear 600 and described half line shaft B7 jointing type, respectively between the described piston link 3001 of the described cylinder connection piece 6601 of described cylinder system A5010 and described piston system A6010, and between the described piston link 3002 of the described cylinder connection piece 6602 of described cylinder system B5020 and described piston system B6020 described adjustable travel control gear 700 is set; Or the center of circle that all described cylinders 1 are made as with described cylinder 1 center camber line 101 is that the center of circle is driven rotary or fixed, the described piston set A601 of half is made as through described piston link 3001 and described half line shaft A6 jointing type, the described piston set B602 of half be made as through described piston link 3002 with after described adjustable pivot angle control gear 600 is connected again with described half line shaft A6 jointing type, the described piston set A601 of half is made as through other described piston link 3001 and described half line shaft B7 jointing type in addition, the described piston set B602 of half is made as after the described adjustable pivot angle control gear 600 of other described piston link 3002 and another is connected and described half line shaft B7 jointing type again in addition, respectively between described piston link 3001 and described cylinder connection piece 6601, and described adjustable travel control gear 700 is set between described piston link 3002 and the described cylinder connection piece 6602.
Please refer to arc cylinder load response engine shown in Fig. 7 and 8, two described pistons 2 of opposite disposed constitute cylinder in-block 11 in the described cylinder 1, in the multicylinder engine that described cylinder in-block 11 constitutes by two or more, it is that the center of circle is driven rotary or fixed that all described cylinders 1 are made as with its center of circle, camber line place, center, the described piston set A601 of half is made as through described piston link 3001 and described half line shaft A6 jointing type, the described piston set B602 of half be made as through described piston link 3002 with after described adjustable pivot angle control gear 600 is connected again with described half line shaft A6 jointing type, the described piston set A601 of half is made as through other described piston link 3001 and described half line shaft B7 jointing type in addition, the described piston set B602 of half is made as after the described adjustable pivot angle control gear 600 of other described piston link 3002 and another is connected and described half line shaft B7 jointing type again in addition, on described piston link 3001 between two adjacent described pistons 2 of top and described piston link 3002 described adjustable travel control gear 700 is set.
Please refer to Fig. 9,10, arc cylinder load response engine shown in 11 and 12, in a described cylinder 1, between two described pistons 2 of opposite disposed diaphragm type cylinder head 12 is set, described diaphragm type cylinder head 12 and described cylinder 1 sealing and with described cylinder 1 every being divided into two described firing chambers 4, constitute dividing plate cylinder cap cylinder in-block 13, and formation dividing plate cylinder cap formula two cylinder, in described dividing plate cylinder cap two cylinders or multicylinder engine, all described cylinders 1 are made as and described half line shaft A6 jointing type, described piston set A601 is made as through its described piston link 3001 and described half line shaft B7 jointing type, described piston set B602 is made as through its described piston link 3002 again through described adjustable pivot angle control gear 600 and described half line shaft B7 jointing type, between the described cylinder connection piece 6601 of the described piston link 3001 of described piston set A601 and described cylinder block A501, described adjustable travel control gear 700 is set, and between the described cylinder connection piece 6602 of the described piston link 3002 of described piston set B602 and described cylinder block B502, described adjustable travel control gear 700 is set; Or all described cylinders 1 to be made as with its center of circle, camber line place, center be that the center of circle is driven rotary or fixed, the described piston set A601 of half is made as through described piston link 3001 and described half line shaft A6 jointing type, the described piston set B602 of half be made as through described piston link 3002 with after described adjustable pivot angle control gear 600 is connected again with described half line shaft A6 jointing type, the described piston set A601 of half is made as through other described piston link 3001 and described half line shaft B7 jointing type in addition, the described piston set B602 of half is made as after the described adjustable pivot angle control gear 600 of other described piston link 3002 and another is connected and described half line shaft B7 jointing type again in addition, between the described cylinder connection piece 6601 of the described piston link 3001 of described piston set A601 and described cylinder block A501, described adjustable travel control gear 700 is set, between the described cylinder connection piece 6602 of the described piston link 3002 of described piston set B602 and described cylinder block B502, described adjustable travel control gear 700 is set.
Please refer to Figure 12,13, arc cylinder load response engine shown in 14 and 15, described adjustable pivot angle control gear 600 is made as mechanical adjustable pivot angle control gear 601, the adjustable pivot angle control gear 601 of described machinery is made as adjustable pivot angle control gear 6011 formulas of the leading screw that is made of controlled leading screw 60101, or be made as adjustable pivot angle control gear 6012 formulas of the eccentric shaft that constitutes by controlled eccentric shaft 60102, or be made as adjustable pivot angle control gear 6013 formulas of the cam that constitutes by controlled cam 60103, described adjustable travel control gear 700 is made as described mechanical adjustable travel control gear 701, described mechanical adjustable travel control gear 701 is made as by connecting rod A70101, connecting rod B70102, two connecting rod adjustable travel control gear (7011) formulas that free bearing pin 70202 and controlled end bearing pin 70103 constitute, or be made as by described connecting rod A (70101), described connecting rod B70102, connecting rod C70104, three connecting rod adjustable travel control gear, 7012 formulas that free bearing pin 70202 and described controlled end bearing pin 70103 constitute.
Please refer to Figure 10,15,17,18, arc cylinder load response engine shown in 19 and 20, described adjustable pivot angle control gear 600 is made as hydraulically adjustable pivot angle control gear 602, described hydraulically adjustable pivot angle control gear 602 is made as adjustable pivot angle control gear 6021 formulas of the oil hydraulic cylinder that is made of oil hydraulic cylinder 60201, or be made as adjustable pivot angle control gear 6022 formulas of oil hydraulic cylinder two connecting rods that constitute by oil hydraulic cylinder 60201 and two connecting rods 60202, described adjustable travel control gear 700 is made as described hydraulically adjustable travel control device 702, described hydraulically adjustable travel control device 702 is made as by end bearing pin 70201, free end bearing pin 70202, single hydraulic cylinder two connecting rod adjustable travel control gear 7021 formulas that described connecting rod A70101 and oil hydraulic cylinder connecting rod A70203 constitute, or be made as by end bearing pin 70201, free end bearing pin 70202, double hydraulic cylinder two connecting rod adjustable travel control gear 7022 formulas that described oil hydraulic cylinder connecting rod A70203 and oil hydraulic cylinder connecting rod B70204 constitute, or be made as by end bearing pin 70201, free end bearing pin 70202, single hydraulic cylinder three connecting rod adjustable travel control gear 7023 formulas that described connecting rod A70101 of described oil hydraulic cylinder connecting rod A70203 and described connecting rod B70102 constitute, or be made as by end bearing pin 70201, free end bearing pin 70202, described oil hydraulic cylinder connecting rod A70203, double hydraulic cylinder three connecting rod adjustable travel control gear 7024 formulas that described connecting rod A70101 and oil hydraulic cylinder connecting rod B70204 constitute.
Please refer to Figure 15,16,21,22,23,24, arc cylinder load response engine shown in 25 and 26, the adjustable pivot angle control gear 6011 of described leading screw, the control power of adjustable pivot angle control gear 6012 of described eccentric shaft and the adjustable pivot angle control gear 6013 of described cam is made as hydraulic type or electrodynamic type, described controlled end bearing pin 70103 is made as the controlled end of horizontal moving type bearing pin 701031 or is made as the controlled end of eccentric shaft type bearing pin 701032, the control power of the controlled end of described horizontal moving type bearing pin 701031 and the controlled end of described eccentric shaft type bearing pin 701032 is made as hydraulic type or electrodynamic type, at described two connecting rod adjustable travel control gear 7011, described three connecting rod adjustable travel control gear 7012, described single hydraulic cylinder two connecting rod adjustable travel control gear 7021, described double hydraulic cylinder two connecting rod adjustable travel control gear 7022, on the connecting rod free end 122 of the described push and pull system of described single hydraulic cylinder three connecting rod adjustable travel control gear 7023 and described double hydraulic cylinder three connecting rod adjustable travel control gear 7024 or the free end bearing pin 70202 bearing pin spring 12301 is set, inertia body 12302, slip inertia body 12304, rotary inertia body 12305 and/or inertia body car 12307, slip inertia body is set between the fixed end of the connecting rod of described slip inertia body 12304 and described push and pull system and/or the free end adjusts spring 12303, described rotary inertia body 12305 is adjusted spring 12306 through the rotary inertia body and is connected with the connecting rod of vicinity, and described inertia body car 12307 is connected with vehicle-mounted inertia body 12309 through energy-storaging spring 12308; Described two connecting rod adjustable travel control gear 7011, described three connecting rod adjustable travel control gear 7012, described single hydraulic cylinder two connecting rod adjustable travel control gear 7021, described double hydraulic cylinder two connecting rod adjustable travel control gear 7022, described single hydraulic cylinder three connecting rod adjustable travel control gear 7023, described double hydraulic cylinder three connecting rod adjustable travel control gear 7024, described bearing pin spring 12301, described inertia body 12302, described slip inertia body is adjusted spring 12303, described slip inertia body 12304, described rotary inertia body 12305, described slip inertia body is adjusted spring 12306, described inertia body car 12307, described energy-storaging spring 12308 and described vehicle-mounted inertia body 12309 are simultaneously or be arranged on separately in the vacuum chamber 12310.
Please refer to Figure 27,28,29,30, arc cylinder load response engine shown in 31 and 32, swing cooperating agency 1819 is set between the oscillation system 18 of the oscillation system 19 of described cylinder 1 representative and described piston 2 representatives, or swing cooperating agency 1819 is set between the oscillation system 182 of the oscillation system 181 of described piston set A601 representative and described piston set B602 representative, described swing cooperating agency 1819 is made as by two free rotary inertia structures 201 and 202 and the moment of momentum flowing type swing cooperating agency 2021 that constitutes of separately moment of momentum hysteresis spring 21, and described moment of momentum flowing type swing cooperating agency 2021 is interior can to establish vibration damping structure body 22.
Please refer to arc cylinder load response engine shown in Figure 33 and 34, in the center of circle that described cylinder 1 and described piston 2 is made as with described cylinder 1 center camber line 101 is in center of circle rotation and the relative shuttle-type structure, on the oscillation system 18 of the oscillation system 19 of all described cylinder 1 representatives and all described piston 2 representatives, hydraulic pressure anti kickback attachment 36 is set respectively, or on the oscillation system 182 of the oscillation system 181 of described piston set A601 representative and described piston set B602 representative, described hydraulic pressure anti kickback attachment 36 is set respectively, described hydraulic type anti kickback attachment 36 is made as to enter the mouth to be provided with check valve 116 or to enter the mouth and is provided with the oil hydraulic pump 127 of control valve 126, described oil hydraulic pump 127 is made as zero load anti-reversing oil hydraulic pump 1271 formulas that the liquid gateway directly is communicated with, or be made as liquid outlet and the anti-reversing of load oil hydraulic pump 1272 formulas arranged through what load loop was communicated with the liquid inlet, described load loop is made as the lubrication system 33 of described arc cylinder load response engine or is made as the cooling system 34 of described arc cylinder load response engine, described check valve 116 is made as free style or controlled formula, the control mechanism of described control valve 126 and the described check valve 116 of controlled formula is made as mechanical type or electronic electromagnetic, described half line shaft B7 in the oscillation system 18 of all described piston 2 representatives is made as line shaft 271 jointing types with described oil hydraulic pump, described half line shaft A6 in the oscillation system 19 of all described cylinder 1 representatives is made as line shaft 272 jointing types with another described oil hydraulic pump, or half line shaft A6 in the oscillation system 181 of described piston set A601 representative is made as line shaft 271 jointing types with described oil hydraulic pump, and the described half line shaft B7 in the oscillation system 182 of described piston set B602 representative is made as line shaft 272 jointing types with another described oil hydraulic pump.
Please refer to arc cylinder load response engine shown in Figure 35 and 36, described half line shaft A6 is made as differential gear 28 jointing types with differential mechanism 30, described half line shaft B7 is made as another differential gear 29 jointing types with described differential mechanism 30, the planetary pinion shell 31 of described differential mechanism 30 is made as pto 32, and described arc cylinder load response engine and described differential mechanism 30 are made as parallel-axis type or close coupled type.

Claims (10)

1. arc cylinder load response engine, comprise: cylinder (1), piston (2), it is characterized in that: the center line of described cylinder (1) is made as arc, the section of described cylinder (1) is made as circular or non-circular, one or more described pistons (2) are set in described cylinder (1), the piston link (3) of described piston (2) is located at outside firing chamber (4) seal section of described cylinder (1), described cylinder (1) is center of circle rotation and relative swing type with the center of circle that described piston (2) is made as with described cylinder (1) center camber line (101), or be made as stationary phase to swing type, all described cylinders (1) that are provided with clockwise are made as cylinder block A (501) in the described cylinder (1), all described cylinders (1) that are provided with counterclockwise are made as cylinder block B (502), all described pistons (2) that are provided with clockwise are made as piston set A (601) in the described piston (2), all described pistons (2) that are provided with counterclockwise are made as piston set B (602), between the cylinder system B (5020) of the cylinder system A (5010) of described cylinder block A (501) representative and described cylinder block B (502) representative, adjustable pivot angle control gear (600) is set, between the oscillation system (18) of the oscillation system (19) of all described cylinder (1) representatives and all described piston (2) representatives, travel control device (700) is set; Or between the piston system B (6020) of the piston system A (6010) of described piston set A (601) representative and described piston set B (602) representative, adjustable pivot angle control gear (600) is set, between the oscillation system (18) of the oscillation system (19) of all described cylinder (1) representatives and all described piston (2) representatives, adjustable travel control gear (700) is set; Or between the piston system D (6006) of the piston system C (6005) of the described piston set A of half (601) representative and the described piston set B of half (602) representative, described adjustable pivot angle control gear (600) is set, between system that the piston system D (6006) of the piston system C (6005) of the described piston set A of half (601) representative and the described piston set B of half (602) representative is constituted and described cylinder (1), described adjustable travel control gear (700) is set; Or between the cylinder system D (5006) of the cylinder system C (5005) of the described cylinder block A of half (501) representative and the described cylinder block B of half (502) representative, described pivot angle control gear (600) is set, between system that the cylinder system D (5006) of the cylinder system C (5005) of the described cylinder block A of half (501) representative and the described cylinder block B of half (502) representative is constituted and described piston (2), described adjustable travel control gear (700) is set.
2. arc cylinder load response engine according to claim 1, it is characterized in that: a described piston (2) is set in a described cylinder (1), in the end of described cylinder (1) cylinder head (5) is set, constitute unit cylinder (9), at least two described unit of opposite disposed cylinder (9) constitutes multicylinder engine on the circumference of the camber line place, center of described cylinder (1), in described multicylinder engine, described cylinder block A (501) is made as through cylinder connection piece (6601) and half line shaft A (6) jointing type, described cylinder block B (502) is made as through cylinder connection piece (6602) again through described adjustable pivot angle control gear (600) and described half line shaft A (6) jointing type, all described pistons (2) are made as through described piston link (3) and described half line shaft B (7) jointing type, respectively between the described piston link (3001) of the described cylinder connection piece (6601) of described cylinder system A (5010) and described piston system A (6010), and between the described piston link (3002) of the described cylinder connection piece (6602) of described cylinder system B (5020) and described piston system B (6020) described adjustable travel control gear (700) is set; Or all described cylinders (1) are made as through described cylinder connection piece (66) and described half line shaft A (6) jointing type, described piston set A (601) is made as through described piston link (3001) and described half line shaft B (7) jointing type, described piston set B (602) is made as through described piston link (3002) again through described adjustable pivot angle control gear (600) and described half line shaft B (7) jointing type, respectively between the described piston link (3001) of the described cylinder connection piece (6601) of described cylinder system A (5010) and described piston system A (6010), and between the described piston link (3002) of the described cylinder connection piece (6602) of described cylinder system B (5020) and described piston system B (6020) described adjustable travel control gear (700) is set; Or the center of circle that all described cylinders (1) are made as with described cylinder (1) center camber line (101) is that the center of circle is driven rotary or fixed, the described piston set A of half (601) is made as through described piston link (3001) and described half line shaft A (6) jointing type, the described piston set B of half (602) be made as through described piston link (3002) with after described adjustable pivot angle control gear (600) is connected again with described half line shaft A (6) jointing type, the described piston set A of half (601) is made as through other described piston link (3001) and described half line shaft B (7) jointing type in addition, the described piston set B of half (602) is made as after the described adjustable pivot angle control gear of other described piston link (3002) and another (600) is connected and described half line shaft B (7) jointing type again in addition, respectively between described piston link (3001) and described cylinder connection piece (6601), and between described piston link (3002) and the described cylinder connection piece (6602) described adjustable travel control gear (700) is set.
3. arc cylinder load response engine according to claim 1, it is characterized in that: a described cylinder (1) two described pistons of interior opposite disposed (2) constitute cylinder in-block (11), in the multicylinder engine that described cylinder in-block (11) constitutes by two or more, it is that the center of circle is driven rotary or fixed that all described cylinders (1) are made as with its center of circle, camber line place, center, the described piston set A of half (601) is made as through described piston link (3001) and described half line shaft A (6) jointing type, the described piston set B of half (602) be made as through described piston link (3002) with after described adjustable pivot angle control gear (600) is connected again with described half line shaft A (6) jointing type, the described piston set A of half (601) is made as through other described piston link (3001) and described half line shaft B (7) jointing type in addition, the described piston set B of half (602) is made as after the described adjustable pivot angle control gear of other described piston link (3002) and another (600) is connected and described half line shaft B (7) jointing type again in addition, on described piston link (3001) between adjacent two the described pistons (2) in top and described piston link (3002) described adjustable travel control gear (700) is set.
4. arc cylinder load response engine according to claim 1, it is characterized in that: in a described cylinder (1), between two described pistons (2) of opposite disposed diaphragm type cylinder head (12) is set, the sealing of described diaphragm type cylinder head (12) and described cylinder (1) and with described cylinder (1) every being divided into two described firing chambers (4), constitute dividing plate cylinder cap cylinder in-block (13), and formation dividing plate cylinder cap formula two cylinder, in described dividing plate cylinder cap two cylinders or multicylinder engine, all described cylinders (1) are made as and described half line shaft A (6) jointing type, described piston set A (601) is made as through its described piston link (3001) and described half line shaft B (7) jointing type, described piston set B (602) is made as through its described piston link (3002) again through described adjustable pivot angle control gear (600) and described half line shaft B (7) jointing type, between the described cylinder connection piece (6601) of the described piston link (3001) of described piston set A (601) and described cylinder block A (501), described adjustable travel control gear (700) is set, and between the described cylinder connection piece (6602) of the described piston link (3002) of described piston set B (602) and described cylinder block B (502), described adjustable travel control gear (700) is set; Or all described cylinders (1) to be made as with its center of circle, camber line place, center be that the center of circle is driven rotary or fixed, the described piston set A of half (601) is made as through described piston link (3001) and described half line shaft A (6) jointing type, the described piston set B of half (602) be made as through described piston link (3002) with after described adjustable pivot angle control gear (600) is connected again with described half line shaft A (6) jointing type, the described piston set A of half (601) is made as through other described piston link (3001) and described half line shaft B (7) jointing type in addition, the described piston set B of half (602) is made as after the described adjustable pivot angle control gear of other described piston link (3002) and another (600) is connected and described half line shaft B (7) jointing type again in addition, between the described cylinder connection piece (6601) of the described piston link (3001) of described piston set A (601) and described cylinder block A (501), described adjustable travel control gear (700) is set, between the described cylinder connection piece (6602) of the described piston link (3002) of described piston set B (602) and described cylinder block B (502), described adjustable travel control gear (700) is set.
5. as claim 1,2,3 and 4 described arc cylinder load response engines, it is characterized in that: described adjustable pivot angle control gear (600) is made as mechanical adjustable pivot angle control gear (601), the adjustable pivot angle control gear of described machinery (601) is made as the adjustable pivot angle control gear of leading screw (6011) formula that is made of controlled leading screw (60101), or be made as the adjustable pivot angle control gear of eccentric shaft (6012) formula that constitutes by controlled eccentric shaft (60102), or be made as the adjustable pivot angle control gear of cam (6013) formula that constitutes by controlled cam (60103), described adjustable travel control gear (700) is made as described mechanical adjustable travel control gear (701), described mechanical adjustable travel control gear (701) is made as by connecting rod A (70101), connecting rod B (70102), two connecting rod adjustable travel control gear (7011) formulas that free bearing pin (70202) and controlled end bearing pin (70103) constitute, or be made as by described connecting rod A (70101), described connecting rod B (70102), connecting rod C (70104), three connecting rod adjustable travel control gear (7012) formulas that free bearing pin (70202) and described controlled end bearing pin (70103) constitute.
6. as claim 1,2,3 and 4 described arc cylinder load response engines, it is characterized in that: described adjustable pivot angle control gear (600) is made as hydraulically adjustable pivot angle control gear (602) formula, described hydraulically adjustable pivot angle control gear (602) is made as the adjustable pivot angle control gear of oil hydraulic cylinder (6021) formula that is made of oil hydraulic cylinder (60201), or be made as the adjustable pivot angle control gear of oil hydraulic cylinder two connecting rods (6022) formula that constitutes by oil hydraulic cylinder (60201) and two connecting rods (60202), described adjustable travel control gear (700) is made as described hydraulically adjustable travel control device (702) formula, described hydraulically adjustable travel control device (702) is made as by end bearing pin (70201), free end bearing pin (70202), single hydraulic cylinder two connecting rod adjustable travel control gear (7021) formulas that described connecting rod A (70101) and oil hydraulic cylinder connecting rod A (70203) constitute, or be made as by end bearing pin (70201), free end bearing pin (70202), double hydraulic cylinder two connecting rod adjustable travel control gear (7022) formulas that described oil hydraulic cylinder connecting rod A (70203) and oil hydraulic cylinder connecting rod B (70204) constitute, or be made as by end bearing pin (70201), free end bearing pin (70202), single hydraulic cylinder three connecting rod adjustable travel control gear (7023) formulas that described connecting rod A of described oil hydraulic cylinder connecting rod A (70203) (70101) and described connecting rod B (70102) constitute, or be made as by end bearing pin (70201), free end bearing pin (70202), described oil hydraulic cylinder connecting rod A (70203), double hydraulic cylinder three connecting rod adjustable travel control gear (7024) formulas that described connecting rod A (70101) and oil hydraulic cylinder connecting rod B (70204) constitute.
7. as claim 1,2,3,4,5 and 6 described arc cylinder load response engines, it is characterized in that: the adjustable pivot angle control gear of described leading screw (6011), the control power of the adjustable pivot angle control gear of adjustable pivot angle control gear of described eccentric shaft (6012) and described cam (6013) is made as hydraulic type or electrodynamic type, described controlled end bearing pin (70103) is made as the controlled end of horizontal moving type bearing pin (701031) or is made as the controlled end of eccentric shaft type bearing pin (701032), and the control power of the controlled end of described horizontal moving type bearing pin (701031) and the controlled end of described eccentric shaft type bearing pin (701032) is made as hydraulic type or electrodynamic type; At described two connecting rod adjustable travel control gear (7011), described three connecting rod adjustable travel control gear (7012), described single hydraulic cylinder two connecting rod adjustable travel control gear (7021), described double hydraulic cylinder two connecting rod adjustable travel control gear (7022), on the connecting rod free end (122) of the described push and pull system of described single hydraulic cylinder three connecting rod adjustable travel control gear (7023) and described double hydraulic cylinder three connecting rod adjustable travel control gear (7024) or the free end bearing pin (70202) bearing pin spring (12301) is set, inertia body (12302), slip inertia body (12304), rotary inertia body (12305) and/or inertia body car (12307), slip inertia body is set between the fixed end of the connecting rod of described slip inertia body (12304) and described push and pull system and/or the free end adjusts spring (12303), described rotary inertia body (12305) is adjusted spring (12306) through the rotary inertia body and is connected with the connecting rod of vicinity, and described inertia body car (12307) is connected with vehicle-mounted inertia body (12309) through energy-storaging spring (12308); Described two connecting rod adjustable travel control gear (7011), described three connecting rod adjustable travel control gear (7012), described single hydraulic cylinder two connecting rod adjustable travel control gear (7021), described double hydraulic cylinder two connecting rod adjustable travel control gear (7022), described single hydraulic cylinder three connecting rod adjustable travel control gear (7023), described double hydraulic cylinder three connecting rod adjustable travel control gear (7024), described bearing pin spring (12301), described inertia body (12302), described slip inertia body is adjusted spring (12303), described slip inertia body (12304), described rotary inertia body (12305), described rotary inertia body is adjusted spring (12306), described inertia body car (12307), described energy-storaging spring (12308) and described vehicle-mounted inertia body (12309) are simultaneously or be arranged on separately in the vacuum chamber (12310).
8. as claim 1,2,3,4,5,6 and 7 described arc cylinder load response engines, it is characterized in that: swing cooperating agency (1819) is set between the oscillation system (18) of the oscillation system (19) of described cylinder (1) representative and described piston (2) representative, or swing cooperating agency (1819) is set between the oscillation system (182) of the oscillation system (181) of described piston set A (601) representative and described piston set B (602) representative, described swing cooperating agency (1819) is made as the moment of momentum flowing type swing cooperating agency (2021) that is made of two free rotary inertia structures (201 and 202) and moment of momentum hysteresis spring (21) separately, can establish vibration damping structure body (22) in the described moment of momentum flowing type swing cooperating agency (2021).
9. as claim 1,2,3,4,5,6,7 and 8 described arc cylinder load response engines, it is characterized in that: in the center of circle that described cylinder (1) and described piston (2) is made as with described cylinder (1) center camber line (101) is in center of circle rotation and the relative shuttle-type structure, on the oscillation system (18) of the oscillation system (19) of all described cylinder (1) representatives and all described piston (2) representatives, hydraulic pressure anti kickback attachment (36) is set respectively, or on the oscillation system (182) of the oscillation system (181) of described piston set A (601) representative and described piston set B (602) representative, described hydraulic pressure anti kickback attachment (36) is set respectively, described hydraulic type anti kickback attachment (36) is made as to enter the mouth to be provided with check valve (116) or to enter the mouth and is provided with the oil hydraulic pump (127) of control valve (126), described oil hydraulic pump (127) is made as zero load anti-reversing oil hydraulic pump (1271) formula that the liquid gateway directly is communicated with, or be made as liquid outlet and the anti-reversing of load oil hydraulic pump (1272) formula arranged through what load loop was communicated with the liquid inlet, described load loop is made as the lubrication system (33) of described arc cylinder load response engine or is made as the cooling system (34) of described arc cylinder load response engine, described check valve (116) is made as free style or controlled formula, the control mechanism of described control valve (126) and the described check valve of controlled formula (116) is made as mechanical type or electronic electromagnetic, described half line shaft B (7) in the oscillation system (18) of all described piston (2) representatives is made as line shaft (271) jointing type with described oil hydraulic pump, described half line shaft A (6) in the oscillation system (19) of all described cylinder (1) representatives is made as line shaft (272) jointing type with another described oil hydraulic pump, or half line shaft A (6) in the oscillation system (181) of described piston set A (601) representative is made as line shaft (271) jointing type with described oil hydraulic pump, and the described half line shaft B (7) in the oscillation system (182) of described piston set B (602) representative is made as line shaft (272) jointing type with another described oil hydraulic pump.
10. as arc cylinder load response engine as described in the claim 1,2,3,4,5,6,7,8 and 9, it is characterized in that: described half line shaft A (6) is made as a differential gear (28) jointing type with differential mechanism (30), described half line shaft B (7) is made as another differential gear (29) jointing type with described differential mechanism (30), the planetary pinion shell (31) of described differential mechanism (30) is made as pto (32), and described arc cylinder load response engine and described differential mechanism (30) are made as parallel-axis type or close coupled type.
CN2008101775401A 2008-11-21 2008-11-21 Arc cylinder load response engine Expired - Fee Related CN101555827B (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102135032A (en) * 2010-01-25 2011-07-27 张志雄 Reciprocating two-stroke internal combustion engine with dual-surface piston arc-shaped cylinder
CN103850783A (en) * 2014-03-28 2014-06-11 冯亦龙 Rotating shaft type rotor engine
CN108798893A (en) * 2018-08-08 2018-11-13 西南交通大学 Cylinder and piston connecting rod unit

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4068985A (en) * 1976-04-06 1978-01-17 Baer John S Rotary engine or pump construction
DE19901110C2 (en) * 1999-01-14 2002-06-06 Herbert Huettlin Oscillating piston engine
CN1186524C (en) * 2001-10-26 2005-01-26 张长春 Self-balanced rotor engine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102135032A (en) * 2010-01-25 2011-07-27 张志雄 Reciprocating two-stroke internal combustion engine with dual-surface piston arc-shaped cylinder
CN103850783A (en) * 2014-03-28 2014-06-11 冯亦龙 Rotating shaft type rotor engine
CN108798893A (en) * 2018-08-08 2018-11-13 西南交通大学 Cylinder and piston connecting rod unit

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