CN101555827B

CN101555827B - Arc cylinder load response engine

Info

Publication number: CN101555827B
Application number: CN2008101775401A
Authority: CN
Inventors: 靳北彪
Original assignee: Individual
Current assignee: Individual
Priority date: 2008-11-21
Filing date: 2008-11-21
Publication date: 2012-02-01
Anticipated expiration: 2028-11-21
Also published as: CN101555827A

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 repre sented 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 property 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 property is good, and volume is little, in light weight with reciprocating-piston engine.Yet, because mostly free piston engine 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 property 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 with 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; But all these were consulted with the applicant but the disclosed scheme of patent do not mentioned at this paper 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 in the manufacturing of commercialization motor, be used widely.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 property 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 efficient is high, 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 DENG, 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, and 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.

The object of the 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, the arc Cylinder engine of adjustment air displacement (stroke) and geometrical compression ratio, just so-called arc cylinder load response engine is to improve efficient, low emission property 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 said cylinder is made as arc; The section of said cylinder is made as circular or non-circular; One or more said pistons are set in said cylinder; The piston link of said piston is located at outside the combustion chamber sealing section of said cylinder, and the center of circle that said cylinder and said piston are made as with said cylinder axis camber line is center of circle rotation and relative swing formula, or is made as stationary phase to swing type; All said cylinders that are provided with clockwise are made as cylinder block A in the said cylinder; All said cylinders that are provided with counterclockwise are made as cylinder block B, and all said pistons that are provided with clockwise are made as piston set A in the said piston, and all said pistons that are provided with counterclockwise are made as piston set B; Between the cylinder system B of the cylinder system A of said cylinder block A representative and said cylinder block B representative, adjustable pivot angle control gear is set, between the oscillation system of the oscillation system of all said cylinder representatives and all said piston representatives, the adjustable travel control gear is set; Or between the piston system B of the piston system A of said piston set A representative and said piston set B representative, adjustable pivot angle control gear is set, between the oscillation system of the oscillation system of all said cylinder representatives and all said piston representatives, the adjustable travel control gear is set; Or between the piston system D of the piston system C of the said piston set A representative of half and the said piston set B representative of half, said adjustable pivot angle control gear is set, between system that the piston system D of the piston system C of the said piston set A representative of half and the said piston set B representative of half is constituted and said cylinder, said adjustable travel control gear is set; Or between the cylinder system D of the cylinder system C of the said cylinder block A representative of half and the said cylinder block B representative of half, said pivot angle control gear is set, between the system that cylinder system D constituted of the cylinder system C of the said cylinder block A representative of half and the said cylinder block B representative of half and said piston, said adjustable travel control gear is set.

A said piston is set in a said cylinder; End at said cylinder is provided with cylinder head; Constitute the unit cylinder; At least two said unit of opposite disposed cylinder constitutes multicylinder engine on the circumference of the center of said cylinder camber line place; In said multicylinder engine; Said cylinder block A is made as through cylinder connection piece and half line shaft A jointing type, and said cylinder block B is made as through cylinder connection piece again through said adjustable pivot angle control gear and said half line shaft A jointing type, and all said pistons are made as through said piston link and said half line shaft B jointing type; Respectively between the said piston link of the said cylinder connection piece of said cylinder system A and said piston system A, and between the said piston link of the said cylinder connection piece of said cylinder system B and said piston system B said adjustable travel control gear is set; Or all said cylinders are made as through said cylinder connection piece and said half line shaft A jointing type; Said piston set A is made as through said piston link and said half line shaft B jointing type; Said piston set B is made as through said piston link again through said adjustable pivot angle control gear and said half line shaft B jointing type; Respectively between the said piston link of the said cylinder connection piece of said cylinder system A and said piston system A, and between the said piston link of the said cylinder connection piece of said cylinder system B and said piston system B said adjustable travel control gear is set; Or the center of circle that all said cylinders are made as with said cylinder axis camber line is that the center of circle is driven rotary or fixed; The said piston set A of half is made as through said piston link and said half line shaft A jointing type; The said piston set B of half be made as through said piston link with after said adjustable pivot angle control gear is connected again with said half line shaft A jointing type; The said piston set A of half is made as through other said piston link and said half line shaft B jointing type in addition; The said piston set B of half is made as after the said adjustable pivot angle control gear of other said piston link and another is connected and said half line shaft B jointing type again in addition; Respectively between said piston link and said cylinder connection piece, and said adjustable travel control gear is set between said piston link and the said cylinder connection piece.

Two said pistons of opposite disposed constitute cylinder in-block in the said cylinder; In the multicylinder engine that said cylinder in-block constitutes by two or more; It is that the center of circle is driven rotary or fixed that all said cylinders are made as with its center of circle, camber line place, center; The said piston set A of half is made as through said piston link and said half line shaft A jointing type; The said piston set B of half be made as through said piston link with after said adjustable pivot angle control gear is connected again with said half line shaft A jointing type; The said piston set A of half is made as through other said piston link and said half line shaft B jointing type in addition; The said piston set B of half is made as after the said adjustable pivot angle control gear of other said piston link and another is connected and said half line shaft B jointing type again in addition, on said piston link between two adjacent said pistons of top and said piston link, said adjustable travel control gear is set.

In a said cylinder, between two said pistons of opposite disposed the diaphragm type cylinder head is set; Said diaphragm type cylinder head and said cylinder seal and with said cylinder at a distance from being divided into two said firing chambers; Constitute dividing plate cylinder cap cylinder in-block; And formation dividing plate cylinder cap formula two cylinder; In said dividing plate cylinder cap two cylinders or multicylinder engine; All said cylinders are made as and said half line shaft A jointing type, and said piston set A is made as through its said piston link and said half line shaft B jointing type, and said piston set B is made as through its said piston link again through said adjustable pivot angle control gear and said half line shaft B jointing type; Between the said cylinder connection piece of the said piston link of said piston set A and said cylinder block A, said adjustable travel control gear is set, and between the said cylinder connection piece of the said piston link of said piston set B and said cylinder block B, said adjustable travel control gear is set; Or all said cylinders to be made as with the center of circle, its center camber line place be that the center of circle is driven rotary or fixed; The said piston set A of half is made as through said piston link and said half line shaft A jointing type; The said piston set B of half be made as through said piston link with after said adjustable pivot angle control gear is connected again with said half line shaft A jointing type; The said piston set A of half is made as through other said piston link and said half line shaft B jointing type in addition; The said piston set B of half is made as after the said adjustable pivot angle control gear of other said piston link and another is connected and said half line shaft B jointing type again in addition; Between the said cylinder connection piece of the said piston link of said piston set A and said cylinder block A, said adjustable travel control gear is set, between the said cylinder connection piece of the said piston link of said piston set B and said cylinder block B, said adjustable travel control gear is set.

Said adjustable pivot angle control gear is made as mechanical adjustable pivot angle control gear; The adjustable pivot angle control gear of said machinery is made as the adjustable pivot angle control gear of the leading screw that is made up 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; Said adjustable travel control gear is made as said mechanical adjustable travel control gear formula; Said mechanical adjustable travel control gear is made as the two connecting rod adjustable travel control gear formulas that are made up of connecting rod A, connecting rod B, free bearing pin and controlled end bearing pin, or is made as the three connecting rod adjustable travel control gear formulas that are made up of said connecting rod A, said connecting rod B, connecting rod C, free bearing pin and said controlled end bearing pin.

Said adjustable pivot angle control gear is made as hydraulically adjustable pivot angle control gear; Said hydraulically adjustable pivot angle control gear is made as the adjustable pivot angle control gear of the oil hydraulic cylinder that is made up 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 up of oil hydraulic cylinder and two connecting rods; Said adjustable travel control gear is made as said hydraulically adjustable travel control device formula; Said hydraulically adjustable travel control device is made as the single hydraulic cylinder two connecting rod adjustable travel control gear formulas that are made up of end bearing pin, free end bearing pin, said connecting rod A and oil hydraulic cylinder connecting rod A; Or be made as the double hydraulic cylinder two connecting rod adjustable travel control gear formulas that constitute by end bearing pin, free end bearing pin, said oil hydraulic cylinder connecting rod A and oil hydraulic cylinder connecting rod B; Or be made as the single hydraulic cylinder three connecting rod adjustable travel control gear formulas that constitute by end bearing pin, free end bearing pin, said oil hydraulic cylinder connecting rod A, said connecting rod A and said connecting rod B, or be made as the double hydraulic cylinder three connecting rod adjustable travel control gear formulas that constitute by end bearing pin, free end bearing pin, said oil hydraulic cylinder connecting rod A, said connecting rod A and oil hydraulic cylinder connecting rod B.

The control power of the adjustable pivot angle control gear of said leading screw, the adjustable pivot angle control gear of said eccentric shaft and the adjustable pivot angle control gear of said cam is made as hydraulic type or electrodynamic type; Said 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 said horizontal moving type controlled end bearing pin and the controlled end of said eccentric shaft type bearing pin is made as hydraulic type or electrodynamic type; At said two connecting rod adjustable travel control gear; Said three connecting rod adjustable travel control gear; Said single hydraulic cylinder two connecting rod adjustable travel control gear, said double hydraulic cylinder two connecting rod adjustable travel control gear are provided with the bearing pin spring on the connecting rod free end of the said push and pull system of said single hydraulic cylinder three connecting rod adjustable travel control gear and said double hydraulic cylinder three connecting rod adjustable travel control gear or the free end bearing pin; The inertia body; Slip inertia body, rotary inertia body and/or inertia body car are provided with slip inertia body adjustment spring between the fixed end of the connecting rod of said slip inertia body and said push and pull system and/or the free end; Said rotary inertia body is connected with contiguous connecting rod through rotary inertia body adjustment spring, and said inertia body car is connected with vehicle-mounted inertia body through energy-storaging spring; Said two connecting rod adjustable travel control gear; Said three connecting rod adjustable travel control gear; Said single hydraulic cylinder two connecting rod adjustable travel control gear; Said double hydraulic cylinder two connecting rod adjustable travel control gear; Said single hydraulic cylinder three connecting rod adjustable travel control gear, said double hydraulic cylinder three connecting rod adjustable travel control gear, said bearing pin spring, said inertia body, said slip inertia body adjustment spring, said slip inertia body, said rotary inertia body, said rotary inertia body adjustment spring, said inertia body car, said energy-storaging spring and said 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 said cylinder representative and said piston representative; Or swing cooperating agency is set between the oscillation system of the oscillation system of said piston set A representative and said piston set B representative; The said cooperating agency of swinging is made as the moment of momentum flowing type swing cooperating agency that is made up of two free rotary inertia structures and moment of momentum hysteresis spring separately, and said moment of momentum flowing type is swung in the cooperating agency can establish the vibration damping structure body.

The center of circle said cylinder and said piston being made as with said cylinder axis camber line is in the structure of center of circle rotation and relative swing formula; On the oscillation system of the oscillation system of all said cylinder representatives and all said piston representatives, the hydraulic pressure anti kickback attachment is set respectively; Or on the oscillation system of the oscillation system of said piston set A representative and said piston set B representative, said hydraulic pressure anti kickback attachment is set respectively; Said 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; Said 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; Said load loop is made as the lubrication system of said arc cylinder load response engine or is made as the cooling system of said arc cylinder load response engine; Said check valve is made as free style or controlled formula; The control mechanism of said control valve and the said check valve of controlled formula is made as mechanical type or electronic electromagnetic; Said half line shaft B in the oscillation system of all said piston representatives is made as the line shaft jointing type with said oil hydraulic pump; Said half line shaft A in the oscillation system of all said cylinder representatives is made as the line shaft jointing type with another said oil hydraulic pump, or half line shaft A in the oscillation system of said piston set A representative is made as the line shaft jointing type with said oil hydraulic pump, and the said half line shaft B in the oscillation system of said piston set B representative is made as the line shaft jointing type with another said oil hydraulic pump.

Said half line shaft A is made as a differential gear jointing type with differential mechanism; Said half line shaft B is made as another differential gear jointing type with said differential mechanism; The planetary pinion shell of said differential mechanism is made as pto, and said arc cylinder load response engine and said differential mechanism are made as parallel-axis type or close coupled type.

The oscillation system of said piston representative is meant, said piston and follower thereof, for example, said piston link, said half line shaft, differential side gear etc.; The oscillation system of said cylinder representative is meant, said cylinder and follower thereof, for example, said cylinder connection piece, said half line shaft, differential side gear etc.; The oscillation system of said cylinder block A representative is meant, said cylinder block A and follower thereof, for example, said cylinder connection piece, said half line shaft, differential side gear etc.; The oscillation system of said cylinder block B representative is meant, said cylinder block B and follower thereof, for example, said cylinder connection piece, said half line shaft, differential side gear etc.; The oscillation system of said piston set A representative is meant, said piston set A and follower thereof, for example, the link of said piston set A, said half line shaft, differential side gear etc.; The oscillation system of said piston B representative is meant, said piston set B and follower thereof, for example, the link of said piston set B, said half line shaft, differential side gear etc.Other said systems by that analogy.Said cylinder and said piston are made as stationary phase swing type are meant, one type in said cylinder and the said piston is made as the fixed another kind of swing type that is made as.

The disclosed arc cylinder load response engine of the present invention; Through the adjustable pivot angle control gear of said machinery, said hydraulically adjustable pivot angle control gear, said mechanical adjustable travel control gear and/or said hydraulically adjustable travel control device are set, realize that the geometrical compression ratio of said 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, like 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 said push and pull system during in collinear point; Said piston begins reversing motion, and the free end of said push and pull system must leave collinear point as early as possible, otherwise said push and pull system will influence the motion that said piston leaves lower dead center; Influence the external output torque of said arc cylinder load response engine when the blast stroke begins, and then cause said arc cylinder load response engine decrease in efficiency.Said three bar linkage structures can make the free end of the said push and pull system that is in collinear point leave collinear point quickly than said two bar linkage structures, but said three bar linkage structures are more complicated than said two bar linkage structures, 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 opposite-oriented movement the 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 receive rightabout pulling force.In like manner; When two ends of push and pull system to separately near opposite-oriented movement the 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 receive 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 said 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 said 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 said arc cylinder load response engine of four-stroke, a said arc cylinder load response engine can be provided with a plurality of said push and pull system, to satisfy the needs of each free-piston of control.Said bearing pin spring, said slip inertia body adjustment spring, said inertia body, said slip inertia body, said slip inertia body adjustment spring, said rotary inertia body, said rotary inertia body adjustment spring, said inertia car, said through energy-storaging spring and said vehicle-mounted inertia body; Can be provided with one or morely according to situation, also can according to circumstances use separately or use simultaneously.

Said 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 said free bearing pin can leave the collinear point with the end bearing pin more quickly; Thereby said free-piston the blast stroke when beginning external moment bigger, improve the efficient of motor.

Said inertia body is exactly the object with certain inertia, and said inertia body also can be arranged on the free end of connecting rod, through adjusting the quality of said inertia body, can make the push and pull system operation more steady.

Said slip inertia body adjustment spring is arranged on the spring on the connecting rod; One end of slip inertia body adjustment spring is connected with the fixed end of connecting rod; Also can be connected with the free end of connecting rod; As long as the effect of said slip inertia body adjustment spring is that said slip inertia body is moved to the fixed end direction of connecting rod, the other end of said slip inertia body adjustment spring acts on said slip inertia body, and said 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 away from collinear point the time, have big inertia, near collinear point, have less inertia.Therefore, said connecting rod free end can leave collinear point more quickly.

Said rotary inertia body is arranged on the connecting rod free end or the rotary eccentric inertia body on the said free end bearing pin.Said rotary inertia body is connected with said rotary inertia body adjustment spring.Because the effect of inertial force, this structure can make the free end of connecting rod when being in collinear point, receives said rotary inertia body and obtains to continue thrust forward through the indirectly-acting of said rotation spring.Therefore, said connecting rod free end can leave collinear point more quickly.

Said inertia body car is arranged on the inertia body carrier member on the connecting rod free end or on the said free end bearing pin.Said inertia body car is provided with said energy-storaging spring, and an end of said energy-storaging spring is connected with said inertia body car, and the other end of said energy-storaging spring is connected with said 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, receives said vehicle-mounted inertia body and obtains to continue thrust forward through the indirectly-acting of said energy-storaging spring.Therefore, said connecting rod free end can leave collinear point more quickly.

Because when the operation of said arc cylinder load response engine, the free end of said push and pull system can high-speed motion, and the resistance of the free end high-speed motion that can reduce said push and pull system through being provided with of vacuum chamber improves the efficient of motor.

According to the information of engine throttle, rotating speed and load, after COMPUTER CALCULATION, become the action command of said adjustable pivot angle control gear and said adjustable travel control gear.Move respectively according to said adjustable pivot angle control gear of dependent instruction and said adjustable travel control gear, and then realize that air displacement (stroke) and the compression ratio of said arc cylinder load response engine are simultaneously adjustable.The power source of controlling said adjustable pivot angle control gear and said 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.Said 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 said oscillation system and said inertia structure, between two impact member, damping block is set.When swing takes place oscillation system, two oscillation systems will interlock and receive moment of momentum hysteresis spring action, because have only the system of swing forwards just to receive moment of momentum hysteresis spring action, the system of swing then receives the direct effect of inertia structure backward.The inertia of adjustment inertia structure and the Hooke coefficient of moment of momentum hysteresis spring 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; Like ratchet, roller cam formula ratchet and roller friction type ratchet, or adopt noncircular gear or bent axle to accomplish this conversion.The former poor reliability, and the latter makes piston when the blast stroke begins, lose moment to line shaft.Therefore the present mechanical type anti kickback attachment or the conversion of mechanical type rotating power are difficult in the reality uses.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.Said hydraulic pressure anti kickback attachment is exactly can only advance and can not fall back to a direction through 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 said 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, said hydraulic type anti-inversion organization is made as the oil hydraulic pump formula that inlet is provided with control valve.Said control valve is made as self-controlled type (being free style) check valve, controlled formula check valve or other Controlled valves; As receive valve-control spherical etc.; As long as can the inlet of oil hydraulic pump be opened close by logical relation (being equivalent to the relation in correct time); Promptly (when entering the mouth the feed liquor body) opened 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.Said half line shaft or its link of said motor are connected with the line shaft of said oil hydraulic pump, just can reach the purpose of anti-reversing.Say 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 disclosed motor of the present invention are connected back (each system respectively connects a pump) respectively with the line shaft of said zero load anti-reversing oil hydraulic pump; Oscillation system can't reverse; Can only rotate forward; Thereby accomplish of the conversion of swing power, make directly outputting rotary power of said arc cylinder load response engine to rotating power.In order to make full use of the energy of oil hydraulic pump, said hydraulic type anti-inversion organization also can be made as the anti-reversing of load oil hydraulic pump formula.Said 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 said load loop is made as the lubrication system of said arc cylinder load response engine or is made as the cooling system of said arc cylinder load response engine.So can omit oil pump or the water pump and the power thereof of motor.Said oil hydraulic pump can be made as gear type, plunger type, blade type, rotator type or other forms.

For the rotating power that makes said 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 the disclosed motor of the present 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 said cylinder cap, said diaphragm type cylinder head, said cylinder.The control of valve can be made as cammingly, electromagnetic type or hydraulic type.

Disclosed motor can be used as DENG 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: said engine efficiency is high, 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 said arc cylinder load response engine of two said unit cylinders formations;

Fig. 2 is another embodiment of the said arc cylinder load response engine of two said unit cylinders formations;

Fig. 3 is first embodiment of the said arc cylinder load response engine of four said unit cylinders formations;

Fig. 4 is second embodiment of the said arc cylinder load response engine of four said unit cylinders formations;

Fig. 5 is an embodiment of the said arc cylinder load response engine of six said unit cylinders formations;

Fig. 6 is the 3rd embodiment of the said arc cylinder load response engine of four said unit cylinders formations;

Fig. 7 is an embodiment of the said arc cylinder load response engine of said cylinder in-block formation;

Fig. 8 is another embodiment of the said arc cylinder load response engine of said cylinder in-block formation;

Fig. 9 is an embodiment of the said arc cylinder load response engine of said dividing plate cylinder cap cylinder in-block formation;

Figure 10 is another embodiment of the said arc cylinder load response engine of said dividing plate cylinder cap cylinder in-block formation;

Figure 11 is an embodiment who is provided with the said arc cylinder load response engine of said hydraulically adjustable pivot angle control gear;

Figure 12 is an embodiment who is provided with the said arc cylinder load response engine of the adjustable pivot angle control gear of said leading screw;

Figure 13 is an embodiment who is provided with the said arc cylinder load response engine of the adjustable pivot angle control gear of said eccentric shaft;

Figure 14 is an embodiment who is provided with the said arc cylinder load response engine of adjustable pivot angle control gear of said cam and said two connecting rod adjustable travel control gear;

Figure 15 is provided with said three connecting rod adjustable travel control gear, an embodiment of the said arc cylinder load response engine of adjustable pivot angle control gear of said oil hydraulic cylinder two connecting rods and said controlled end bearing pin;

Figure 16 is another embodiment who is provided with the said arc cylinder load response engine of said controlled end bearing pin;

Figure 17 is an embodiment who is provided with the said arc cylinder load response engine of said single hydraulic cylinder two connecting rod adjustable travel control gear;

Figure 18 is an embodiment who is provided with the said arc cylinder load response engine of said double hydraulic cylinder two connecting rod adjustable travel control gear;

Figure 19 is an embodiment who is provided with the said arc cylinder load response engine of said single hydraulic cylinder three connecting rod adjustable travel control gear;

Figure 20 is an embodiment who is provided with the said arc cylinder load response engine of said double hydraulic cylinder three connecting rod adjustable travel control gear;

Figure 21 is an embodiment who is provided with the said arc cylinder load response engine of said bearing pin spring;

Figure 22 is an embodiment who is provided with the said arc cylinder load response engine of said inertia body;

Figure 23 is an embodiment who is provided with the said arc cylinder load response engine of said slip inertia body adjustment spring;

Figure 23 is that said mechanical adjustable travel control gear or said hydraulically adjustable travel control device are arranged on an embodiment in the vacuum chamber;

Figure 24 is an embodiment who is provided with the said arc cylinder load response engine of said rotary inertia body;

Figure 25 is an embodiment who is provided with the said arc cylinder load response engine of said 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 adjustment spring

12304. slip inertia body 12305. rotary inertia bodies 12306. rotary inertia bodies adjustment 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 accompanying drawing and specific embodiment the object of the invention is elaborated:

Please with reference to Fig. 1,2,3, arc cylinder load response engine shown in 4 and 5; Comprise: cylinder 1, piston 2; The center line of said cylinder 1 is made as arc; The section of said cylinder 1 is made as circular or non-circular, and one or more said pistons 2 are set in said cylinder 1, and the piston link 3 of said piston 2 is located at outside firing chamber 4 seal sections of said cylinder 1; Said cylinder 1 is center of circle rotation and relative swing formula with the center of circle that said piston 2 is made as with said cylinder 1 center camber line 101; Or be made as stationary phase to swing type, and all said cylinders 1 that are provided with clockwise are made as cylinder block A501 in the said cylinder 1, and all said cylinders 1 that are provided with counterclockwise are made as cylinder block B502; All said pistons 2 that are provided with clockwise are made as piston set A601 in the said piston 2; All said pistons 2 that are provided with counterclockwise are made as piston set B602, between the cylinder system B5020 of the cylinder system A5010 of said cylinder block A501 representative and said cylinder block B502 representative, adjustable pivot angle control gear 600 are set, and between the oscillation system 18 of the oscillation system 19 of all said cylinder 1 representatives and all said piston 2 representatives, adjustable travel control gear 700 are set; Or between the piston system B6020 of the piston system A6010 of said piston set A601 representative and said piston set B602 representative, adjustable pivot angle control gear 600 is set, between the oscillation system 18 of the oscillation system 19 of all said cylinder 1 representatives and all said piston 2 representatives, adjustable travel control gear 700 is set; Or between the piston system D6006 of the piston system C6005 of the said piston set A601 representative of half and the said piston set B602 representative of half, said adjustable pivot angle control gear 600 is set, between system that the piston system D6006 of the piston system C6005 of the said piston set A601 representative of half and the said piston set B602 representative of half is constituted and said cylinder 1, said adjustable travel control gear 700 is set; Or between the cylinder system D5006 of the cylinder system C5005 of the said cylinder block A501 representative of half and the said cylinder block B502 representative of half, said pivot angle control gear 600 is set, between the system that cylinder system D5006 constituted of the cylinder system C5005 of the said cylinder block A501 representative of half and the said cylinder block B502 representative of half and said piston 2, said adjustable travel control gear 700 is set.

Please with reference to Fig. 1,2,3,4, arc cylinder load response engine shown in 5 and 6; A said piston 2 is set in a said cylinder 1; In the end of said cylinder 1 cylinder head 5 is set; Constitute unit cylinder 9; At least two said unit of opposite disposed cylinder 9 constitutes multicylinder engine on the circumference of the center of said cylinder 1 camber line place; In said multicylinder engine; Said cylinder block A501 is made as through cylinder connection piece 6601 and half line shaft A6 jointing type, and said cylinder block B502 is made as through cylinder connection piece 6602 again through said adjustable pivot angle control gear 600 and said half line shaft A6 jointing type, and all said pistons 2 are made as through said piston link 3 and said half line shaft B7 jointing type; Respectively between the said piston link 3001 of the said cylinder connection piece 6601 of said cylinder system A5010 and said piston system A6010, and between the said piston link 3002 of the said cylinder connection piece 6602 of said cylinder system B5020 and said piston system B6020 said adjustable travel control gear 700 is set; Or all said cylinders 1 are made as through said cylinder connection piece 66 and said half line shaft A6 jointing type; Said piston set A601 is made as through said piston link 3001 and said half line shaft B7 jointing type; Said piston set B602 is made as through said piston link 3002 again through said adjustable pivot angle control gear 600 and said half line shaft B7 jointing type; Respectively between the said piston link 3001 of the said cylinder connection piece 6601 of said cylinder system A5010 and said piston system A6010, and between the said piston link 3002 of the said cylinder connection piece 6602 of said cylinder system B5020 and said piston system B6020 said adjustable travel control gear 700 is set; Or the center of circle that all said cylinders 1 are made as with said cylinder 1 center camber line 101 is that the center of circle is driven rotary or fixed; The said piston set A601 of half is made as through said piston link 3001 and said half line shaft A6 jointing type; The said piston set B602 of half be made as through said piston link 3002 with after said adjustable pivot angle control gear 600 is connected again with said half line shaft A6 jointing type; The said piston set A601 of half is made as through other said piston link 3001 and said half line shaft B7 jointing type in addition; The said piston set B602 of half is made as after the said adjustable pivot angle control gear 600 of other said piston link 3002 and another is connected and said half line shaft B7 jointing type again in addition; Respectively between said piston link 3001 and said cylinder connection piece 6601, and said adjustable travel control gear 700 is set between said piston link 3002 and the said cylinder connection piece 6602.

Please with reference to arc cylinder load response engine shown in Fig. 7 and 8; Two said pistons 2 of opposite disposed constitute cylinder in-block 11 in the said cylinder 1; In the multicylinder engine that said cylinder in-block 11 constitutes by two or more; It is that the center of circle is driven rotary or fixed that all said cylinders 1 are made as with its center of circle, camber line place, center; The said piston set A601 of half is made as through said piston link 3001 and said half line shaft A6 jointing type; The said piston set B602 of half be made as through said piston link 3002 with after said adjustable pivot angle control gear 600 is connected again with said half line shaft A6 jointing type; The said piston set A601 of half is made as through other said piston link 3001 and said half line shaft B7 jointing type in addition; The said piston set B602 of half is made as after the said adjustable pivot angle control gear 600 of other said piston link 3002 and another is connected and said half line shaft B7 jointing type again in addition, on the said piston link between two adjacent said pistons 2 of top 3001 and said piston link 3002, said adjustable travel control gear 700 is set.

Please with reference to Fig. 9,10, arc cylinder load response engine shown in 11 and 12; In a said cylinder 1, between two said pistons 2 of opposite disposed diaphragm type cylinder head 12 is set; Said diaphragm type cylinder head 12 and said cylinder 1 sealing and with said cylinder 1 at a distance from being divided into two said firing chambers 4; Constitute dividing plate cylinder cap cylinder in-block 13; And formation dividing plate cylinder cap formula two cylinder; In said dividing plate cylinder cap two cylinders or multicylinder engine; All said cylinders 1 are made as and said half line shaft A6 jointing type, and said piston set A601 is made as through its said piston link 3001 and said half line shaft B7 jointing type, and said piston set B602 is made as through its said piston link 3002 again through said adjustable pivot angle control gear 600 and said half line shaft B7 jointing type; Between the said cylinder connection piece 6601 of the said piston link 3001 of said piston set A601 and said cylinder block A501, said adjustable travel control gear 700 is set, and between the said cylinder connection piece 6602 of the said piston link 3002 of said piston set B602 and said cylinder block B502, said adjustable travel control gear 700 is set; Or all said cylinders 1 to be made as with the center of circle, its center camber line place be that the center of circle is driven rotary or fixed; The said piston set A601 of half is made as through said piston link 3001 and said half line shaft A6 jointing type; The said piston set B602 of half be made as through said piston link 3002 with after said adjustable pivot angle control gear 600 is connected again with said half line shaft A6 jointing type; The said piston set A601 of half is made as through other said piston link 3001 and said half line shaft B7 jointing type in addition; The said piston set B602 of half is made as after the said adjustable pivot angle control gear 600 of other said piston link 3002 and another is connected and said half line shaft B7 jointing type again in addition; Between the said cylinder connection piece 6601 of the said piston link 3001 of said piston set A601 and said cylinder block A501, said adjustable travel control gear 700 is set, between the said cylinder connection piece 6602 of the said piston link 3002 of said piston set B602 and said cylinder block B502, said adjustable travel control gear 700 is set.

Please with reference to Figure 12,13, arc cylinder load response engine shown in 14 and 15; Said adjustable pivot angle control gear 600 is made as mechanical adjustable pivot angle control gear 601; The adjustable pivot angle control gear 601 of said machinery is made as adjustable pivot angle control gear 6011 formulas of the leading screw that is made up 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; Said adjustable travel control gear 700 is made as said mechanical adjustable travel control gear 701; Said mechanical adjustable travel control gear 701 is made as two connecting rod adjustable travel control gear (7011) formulas that are made up of connecting rod A70101, connecting rod B70102, free bearing pin 70202 and controlled end bearing pin 70103, or is made as three connecting rod adjustable travel control gear, 7012 formulas that are made up of said connecting rod A (70101), said connecting rod B70102, connecting rod C70104, free bearing pin 70202 and said controlled end bearing pin 70103.

Please with reference to Figure 10,15,17,18, arc cylinder load response engine shown in 19 and 20; Said adjustable pivot angle control gear 600 is made as hydraulically adjustable pivot angle control gear 602; Said 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 up 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; Said adjustable travel control gear 700 is made as said hydraulically adjustable travel control device 702; Said hydraulically adjustable travel control device 702 is made as single hydraulic cylinder two connecting rod adjustable travel control gear 7021 formulas that are made up of end bearing pin 70201, free end bearing pin 70202, said connecting rod A70101 and oil hydraulic cylinder connecting rod A70203; Or be made as double hydraulic cylinder two connecting rod adjustable travel control gear 7022 formulas that constitute by end bearing pin 70201, free end bearing pin 70202, said oil hydraulic cylinder connecting rod A70203 and oil hydraulic cylinder connecting rod B70204; Or be made as single hydraulic cylinder three connecting rod adjustable travel control gear 7023 formulas that constitute by end bearing pin 70201, free end bearing pin 70202, the said connecting rod A70101 of said oil hydraulic cylinder connecting rod A70203 and said connecting rod B70102, or be made as double hydraulic cylinder three connecting rod adjustable travel control gear 7024 formulas that constitute by end bearing pin 70201, free end bearing pin 70202, said oil hydraulic cylinder connecting rod A70203, said connecting rod A70101 and oil hydraulic cylinder connecting rod B70204.

Please with reference to Figure 15,16,21,22,23,24, arc cylinder load response engine shown in 25 and 26; The control power of the adjustable pivot angle control gear of said leading screw 6011, the adjustable pivot angle control gear 6012 of said eccentric shaft and the adjustable pivot angle control gear 6013 of said cam is made as hydraulic type or electrodynamic type; Said 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 said horizontal moving type bearing pin 701031 and the controlled end of said eccentric shaft type bearing pin 701032 is made as hydraulic type or electrodynamic type; At said two connecting rod adjustable travel control gear 7011; Said three connecting rod adjustable travel control gear 7012; Said single hydraulic cylinder two connecting rod adjustable travel control gear 7021; Said double hydraulic cylinder two connecting rod adjustable travel control gear 7022; Bearing pin spring 12301 is set, inertia body 12302, slip inertia body 12304 on the connecting rod free end 122 of the said push and pull system of said single hydraulic cylinder three connecting rod adjustable travel control gear 7023 and said double hydraulic cylinder three connecting rod adjustable travel control gear 7024 or the free end bearing pin 70202; Rotary inertia body 12305 and/or inertia body car 12307; Slip inertia body adjustment spring 12303 is set between the fixed end of the connecting rod of said slip inertia body 12304 and said push and pull system and/or the free end, and said rotary inertia body 12305 is connected with contiguous connecting rod through rotary inertia body adjustment spring 12306, and said inertia body car 12307 is connected with vehicle-mounted inertia body 12309 through energy-storaging spring 12308; Said two connecting rod adjustable travel control gear 7011; Said three connecting rod adjustable travel control gear 7012; Said single hydraulic cylinder two connecting rod adjustable travel control gear 7021; Said double hydraulic cylinder two connecting rod adjustable travel control gear 7022; Said single hydraulic cylinder three connecting rod adjustable travel control gear 7023, said double hydraulic cylinder three connecting rod adjustable travel control gear 7024, said bearing pin spring 12301, said inertia body 12302, said slip inertia body adjustment spring 12303, said slip inertia body 12304, said rotary inertia body 12305, said slip inertia body adjustment spring 12306, said inertia body car 12307, said energy-storaging spring 12308 and said vehicle-mounted inertia body 12309 are simultaneously or be arranged on separately in the vacuum chamber 12310.

Please with reference 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 said cylinder 1 representative and said piston 2 representatives; Or swing cooperating agency 1819 is set between the oscillation system 182 of the oscillation system 181 of said piston set A601 representative and said piston set B602 representative; Said swing cooperating agency 1819 is made as the moment of momentum flowing type swing cooperating agency 2021 that is made up of with separately moment of momentum hysteresis spring 21 two free

rotary inertia structures

201 and 202, and said moment of momentum flowing type swings that cooperating agency 2021 is interior can to establish vibration damping structure body 22.

Please with reference to arc cylinder load response engine shown in Figure 33 and 34; The center of circle said cylinder 1 and said piston 2 being made as with said cylinder 1 center camber line 101 is in the structure of center of circle rotation and relative swing formula; On the oscillation system 18 of the oscillation system of all said cylinder 1 representatives 19 and all said piston 2 representatives, hydraulic pressure anti kickback attachment 36 is set respectively; Or on the oscillation system 182 of oscillation system of said piston set A601 representative 181 and said piston set B602 representative, said hydraulic pressure anti kickback attachment 36 is set respectively; Said 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; Said 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; Said load loop is made as the lubrication system 33 of said arc cylinder load response engine or is made as the cooling system 34 of said arc cylinder load response engine; Said check valve 116 is made as free style or controlled formula; The control mechanism of said control valve 126 and the said check valve 116 of controlled formula is made as mechanical type or electronic electromagnetic; Said half line shaft B7 in the oscillation system 18 of all said piston 2 representatives is made as line shaft 271 jointing types with said oil hydraulic pump; Said half line shaft A6 in the oscillation system 19 of all said cylinder 1 representatives is made as line shaft 272 jointing types with another said oil hydraulic pump, or half line shaft A6 in the oscillation system 181 of said piston set A601 representative is made as line shaft 271 jointing types with said oil hydraulic pump, and the said half line shaft B7 in the oscillation system 182 of said piston set B602 representative is made as line shaft 272 jointing types with another said oil hydraulic pump.

Please with reference to arc cylinder load response engine shown in Figure 35 and 36; Said half line shaft A6 is made as differential gear 28 jointing types with differential mechanism 30; Said half line shaft B7 is made as another differential gear 29 jointing types with said differential mechanism 30; The planetary pinion shell 31 of said differential mechanism 30 is made as pto 32, and said arc cylinder load response engine and said differential mechanism 30 are made as parallel-axis type or close coupled type.

Claims

1. arc cylinder load response engine; Comprise: cylinder (1), piston (2); It is characterized in that: the center line of said cylinder (1) is made as arc; The section of said cylinder (1) is made as circular or non-circular; One or more said pistons (2) are set in said cylinder (1); The piston link (3) of said piston (2) is located at outside firing chamber (4) seal section of said cylinder (1), and the center of circle that said cylinder (1) and said piston (2) are made as with said cylinder (1) center camber line (101) is center of circle rotation and relative swing formula, or is made as stationary phase to swing type; All said cylinders (1) that are provided with clockwise are made as cylinder block A (501) in the said cylinder (1); All said cylinders (1) that are provided with counterclockwise are made as cylinder block B (502), and all said pistons (2) that are provided with clockwise are made as piston set A (601) in the said piston (2), and all said 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 said cylinder block A (501) representative and said 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 said cylinder (1) representatives and all said piston (2) representatives, adjustable travel control gear (700) is set; Or between the piston system B (6020) of the piston system A (6010) of said piston set A (601) representative and said 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 said cylinder (1) representatives and all said 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 said piston set A of half (601) representative and the said piston set B of half (602) representative, said adjustable pivot angle control gear (600) is set, between system that the piston system D (6006) of the piston system C (6005) of the said piston set A of half (601) representative and the said piston set B of half (602) representative is constituted and said cylinder (1), said adjustable travel control gear (700) is set; Or between the cylinder system D (5006) of the cylinder system C (5005) of the said cylinder block A of half (501) representative and the said cylinder block B of half (502) representative, said pivot angle control gear (600) is set, between system that the cylinder system D (5006) of the cylinder system C (5005) of the said cylinder block A of half (501) representative and the said cylinder block B of half (502) representative is constituted and said piston (2), said adjustable travel control gear (700) is set.

2. arc cylinder load response engine according to claim 1; It is characterized in that: a said piston (2) is set in a said cylinder (1); In the end of said cylinder (1) cylinder head (5) is set; Constitute unit cylinder (9); At least two said unit of opposite disposed cylinder (9) constitutes multicylinder engine on the circumference of the center of said cylinder (1) camber line place; In said multicylinder engine; Said cylinder block A (501) is made as through first cylinder connection piece (6601) and half line shaft A (6) jointing type, and said cylinder block B (502) is made as through second cylinder connection piece (6602) again through said adjustable pivot angle control gear (600) and half line shaft A (6) jointing type, and all said pistons (2) are made as through said piston link (3) and half line shaft B (7) jointing type; Respectively between the said piston link (3001) of the said cylinder connection piece (6601) of said cylinder system A (5010) and said piston system A (6010), and between the said piston link (3002) of the said cylinder connection piece (6602) of said cylinder system B (5020) and said piston system B (6020) said adjustable travel control gear (700) is set; Or all said cylinders (1) are made as through said cylinder connection piece (66) and said half line shaft A (6) jointing type; Said piston set A (601) is made as through said first piston link (3001) and said half line shaft B (7) jointing type; Said piston set B (602) is made as through the said second piston link (3002) again through said adjustable pivot angle control gear (600) and said half line shaft B (7) jointing type; Respectively between the said piston link (3001) of the said cylinder connection piece (6601) of said cylinder system A (5010) and said piston system A (6010), and between the said piston link (3002) of the said cylinder connection piece (6602) of said cylinder system B (5020) and said piston system B (6020) said adjustable travel control gear (700) is set; Or the center of circle that all said cylinders (1) are made as with said cylinder (1) center camber line (101) is that the center of circle is driven rotary or fixed; The said piston set A of half (601) is made as through said first piston link (3001) and said half line shaft A (6) jointing type; The said piston set B of half (602) be made as through the said second piston link (3002) with after said adjustable pivot angle control gear (600) is connected again with said half line shaft A (6) jointing type; The said piston set A of half (601) is made as through other said first piston link (3001) and said half line shaft B (7) jointing type in addition; In addition the said piston set B of half (602) be made as through the other said second piston link (3002) with after another said adjustable pivot angle control gear (600) is connected again with said half line shaft B (7) jointing type; Respectively between said first piston link (3001) and said cylinder connection piece (6601), and between said second piston link (3002) and the said cylinder connection piece (6602) said adjustable travel control gear (700) is set.

3. arc cylinder load response engine according to claim 1 is characterized in that: a said cylinder

(1) two said pistons of interior opposite disposed (2) constitute cylinder in-block (11); In the multicylinder engine that said cylinder in-block (11) constitutes by two or more; It is that the center of circle is driven rotary or fixed that all said cylinders (1) are made as with its center of circle, camber line place, center; The said piston set A of half (601) is made as through said first piston link (3001) and said half line shaft A (6) jointing type; The said piston set B of half (602) be made as through the said second piston link (3002) with after said adjustable pivot angle control gear (600) is connected again with said half line shaft A (6) jointing type; The said piston set A of half (601) is made as through other said first piston link (3001) and said half line shaft B (7) jointing type in addition; In addition the said piston set B of half (602) be made as through the other said second piston link (3002) with after another said adjustable pivot angle control gear (600) is connected again with said half line shaft B (7) jointing type, on said piston link (3001) between adjacent two the said pistons (2) in top and said piston link (3002), said adjustable travel control gear (700) is set.

4. arc cylinder load response engine according to claim 1; It is characterized in that: in a said cylinder (1), between two said pistons (2) of opposite disposed diaphragm type cylinder head (12) is set; Said diaphragm type cylinder head (12) is with said cylinder (1) sealing and with separated two the said firing chambers (4) that are divided into of said cylinder (1); Constitute dividing plate cylinder cap cylinder in-block (13); And formation dividing plate cylinder cap formula two cylinder; In said dividing plate cylinder cap two cylinders or multicylinder engine; All said cylinders (1) are made as and said half line shaft A (6) jointing type; Said piston set A (601) is made as through its said piston link (3001) and said half line shaft B (7) jointing type; Said piston set B (602) is made as through its said second piston link (3002) again through said adjustable pivot angle control gear (600) and said half line shaft B (7) jointing type, between said first cylinder connection piece (6601) of the said piston link (3001) of said piston set A (601) and said cylinder block A (501), said adjustable travel control gear (700) is set, and between said second cylinder connection piece (6602) of the said piston link (3002) of said piston set B (602) and said cylinder block B (502), said adjustable travel control gear (700) is set; Or all said cylinders (1) to be made as with the center of circle, its center camber line place be that the center of circle is driven rotary or fixed; The said piston set A of half (601) is made as through said first piston link (3001) and said half line shaft A (6) jointing type; The said piston set B of half (602) be made as through the said second piston link (3002) with after said adjustable pivot angle control gear (600) is connected again with said half line shaft A (6) jointing type; The said piston set A of half (601) is made as through other said first piston link (3001) and said half line shaft B (7) jointing type in addition; In addition the said piston set B of half (602) be made as through the other said second piston link (3002) with after another said adjustable pivot angle control gear (600) is connected again with said half line shaft B (7) jointing type; Between said first cylinder connection piece (6601) of the said piston link (3001) of said piston set A (601) and said cylinder block A (501), said adjustable travel control gear (700) is set, between said second cylinder connection piece (6602) of the said piston link (3002) of said piston set B (602) and said cylinder block B (502), said adjustable travel control gear (700) is set.

5. like claim 1,2,3 or 4 said arc cylinder load response engines; It is characterized in that: said adjustable pivot angle control gear (600) is made as mechanical adjustable pivot angle control gear (601); The adjustable pivot angle control gear of said machinery (601) is made as the adjustable pivot angle control gear of leading screw (6011) formula that is made up 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); Said adjustable travel control gear (700) is made as said mechanical adjustable travel control gear (701); Said mechanical adjustable travel control gear (701) is made as two connecting rod adjustable travel control gear (7011) formulas that are made up of connecting rod A (70101), connecting rod B (70102), free bearing pin (70202) and controlled end bearing pin (70103), or is made as three connecting rod adjustable travel control gear (7012) formulas that are made up of said connecting rod A (70101), said connecting rod B (70102), connecting rod C (70104), free bearing pin (70202) and said controlled end bearing pin (70103).

6. like claim 1,2,3 or 4 said arc cylinder load response engines; It is characterized in that: said adjustable pivot angle control gear (600) is made as hydraulically adjustable pivot angle control gear (602) formula; Said 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 up 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); Said adjustable travel control gear (700) is made as said hydraulically adjustable travel control device (702) formula; Said hydraulically adjustable travel control device (702) is made as single hydraulic cylinder two connecting rod adjustable travel control gear (7021) formulas that are made up of end bearing pin (70201), free end bearing pin (70202), said connecting rod A (70101) and oil hydraulic cylinder connecting rod A (70203); Or be made as double hydraulic cylinder two connecting rod adjustable travel control gear (7022) formulas that constitute by end bearing pin (70201), free end bearing pin (70202), said oil hydraulic cylinder connecting rod A (70203) and oil hydraulic cylinder connecting rod B (70204); Or be made as single hydraulic cylinder three connecting rod adjustable travel control gear (7023) formulas that constitute by end bearing pin (70201), free end bearing pin (70202), the said connecting rod A of said oil hydraulic cylinder connecting rod A (70203) (70101) and said connecting rod B (70102), or be made as double hydraulic cylinder three connecting rod adjustable travel control gear (7024) formulas that constitute by end bearing pin (70201), free end bearing pin (70202), said oil hydraulic cylinder connecting rod A (70203), said connecting rod A (70101) and oil hydraulic cylinder connecting rod B (70204).

7. like claim 1,2,3 or 4 said arc cylinder load response engines; It is characterized in that: the control power of the adjustable pivot angle control gear of said leading screw (6011), the adjustable pivot angle control gear of said eccentric shaft (6012) and the adjustable pivot angle control gear of said cam (6013) is made as hydraulic type or electrodynamic type; Said 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 said horizontal moving type bearing pin (701031) and the controlled end of said eccentric shaft type bearing pin (701032) is made as hydraulic type or electrodynamic type; At said two connecting rod adjustable travel control gear (7011); Said three connecting rod adjustable travel control gear (7012); Said single hydraulic cylinder two connecting rod adjustable travel control gear (7021); Said double hydraulic cylinder two connecting rod adjustable travel control gear (7022); On the connecting rod free end (122) of the said push and pull system of said single hydraulic cylinder three connecting rod adjustable travel control gear (7023) and said 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) are provided with slip inertia body adjustment spring (12303) between the fixed end of the connecting rod of said slip inertia body (12304) and said push and pull system and/or the free end; Said rotary inertia body (12305) is connected with contiguous connecting rod through rotary inertia body adjustment spring (12306), and said inertia body car (12307) is connected with vehicle-mounted inertia body (12309) through energy-storaging spring (12308); Said two connecting rod adjustable travel control gear (7011); Said three connecting rod adjustable travel control gear (7012); Said single hydraulic cylinder two connecting rod adjustable travel control gear (7021); Said double hydraulic cylinder two connecting rod adjustable travel control gear (7022), said single hydraulic cylinder three connecting rod adjustable travel control gear (7023), said double hydraulic cylinder three connecting rod adjustable travel control gear (7024), said bearing pin spring (12301), said inertia body (12302), said slip inertia body adjustment spring (12303), said slip inertia body (12304), said rotary inertia body (12305), said rotary inertia body are adjusted spring (12306), said inertia body car (12307), said energy-storaging spring (12308) and said vehicle-mounted inertia body (12309) while or are arranged on separately in the vacuum chamber (12310).

8. like claim 1,2,3 or 4 said 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 said cylinder (1) representative and said piston (2) representative; Or swing cooperating agency (1819) is set between the oscillation system (182) of the oscillation system (181) of said piston set A (601) representative and said piston set B (602) representative; Said swing cooperating agency (1819) is made as the moment of momentum flowing type swing cooperating agency (2021) that is made up 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 said moment of momentum flowing type swing cooperating agency (2021).

9. like claim 1,2,3 or 4 said arc cylinder load response engines; It is characterized in that: the center of circle said cylinder (1) and said piston (2) being made as with said cylinder (1) center camber line (101) is in the structure of center of circle rotation and relative swing formula; On the oscillation system (18) of the oscillation system (19) of all said cylinder (1) representatives and all said piston (2) representatives, hydraulic pressure anti kickback attachment (36) is set respectively; Or on the oscillation system (182) of the oscillation system (181) of said piston set A (601) representative and said piston set B (602) representative, said hydraulic pressure anti kickback attachment (36) is set respectively; Said 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); Said 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; Said load loop is made as the lubrication system (33) of said arc cylinder load response engine or is made as the cooling system (34) of said arc cylinder load response engine; Said check valve (116) is made as free style or controlled formula; The control mechanism of said control valve (126) and the said check valve of controlled formula (116) is made as mechanical type or electronic electromagnetic; Said half line shaft B (7) in the oscillation system (18) of all said piston (2) representatives is made as line shaft (271) jointing type with said oil hydraulic pump; Said half line shaft A (6) in the oscillation system (19) of all said cylinder (1) representatives is made as line shaft (272) jointing type with another said oil hydraulic pump; Or half line shaft A (6) in the oscillation system (181) of said piston A (601) representative is made as line shaft (271) jointing type with said oil hydraulic pump, and the said half line shaft B (7) in the oscillation system (182) of said piston set B (602) representative is made as line shaft (272) jointing type with another said oil hydraulic pump.

10. like claim 1,2,3 or 4 said arc cylinder load response engines; It is characterized in that: said half line shaft A (6) is made as a differential gear (28) jointing type with differential mechanism (30); Said half line shaft B (7) is made as another differential gear (29) jointing type with said differential mechanism (30); The planetary pinion shell (31) of said differential mechanism (30) is made as pto (32), and said arc cylinder load response engine and said differential mechanism (30) are made as parallel-axis type or close coupled type.