CN105221259A - Centrifugal vuilt-up crankshaft energy-saving engine - Google Patents
Centrifugal vuilt-up crankshaft energy-saving engine Download PDFInfo
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Abstract
Centrifugal vuilt-up crankshaft energy-saving engine of the present invention, relates to various diesel oil, vapour oil and gas, single cylinder, twin-tub or multi-cylinder internal combustion engine.Be applicable to various passenger-cargo carriage and large heavy engineering machinery, especially Generator Set and boats and ships etc.Centrifugal vuilt-up crankshaft energy-saving engine comprises casing, work done driving mechanism and transfer mechanism; Casing comprises crankcase and cylinder sleeve body; Cylinder sleeve body is processed with 2 cylinders; Cylinder sleeve body is loaded on crankcase top; Driving mechanism is fixedly loaded in crankcase by dunnage; Piston is loaded in cylinder; Transfer mechanism is loaded on crankcase by bearing support II; Work done driving mechanism is connected by gear I, gear II and gear III with transfer mechanism.The present invention has novel structure, it is easy, with low cost to process, energy-conserving and environment-protective, effect advantages of higher, therefore belong to a kind of novel centrifugal type vuilt-up crankshaft energy-saving engine integrating Economy and practicability.
Description
Technical field
Centrifugal vuilt-up crankshaft energy-saving engine of the present invention, relates to various diesel oil, vapour oil and gas, single cylinder, twin-tub or multi-cylinder internal combustion engine.Be applicable to various passenger-cargo carriage and large heavy engineering machinery, especially Generator Set and boats and ships etc.
Background technique
Along with the development of global economy, the quantity of various fuel engine increases day by day, and the mankind and vegeto-animal existence in the harmful gas serious threat of discharge, and physical environment goes from bad to worse, and the storage volume of oil is limited.Before not having the appearance of corresponding substitute, energy-saving and emission-reduction protection of the environment has become the common recognition of the mankind, and the motor that I studies and current motor contrast; be characterized in: energy consumption is identical; output power is maximum, or perhaps power same consumption energy is minimum, can reach the effect of getting twice the result with half the effort.
Find after deliberation, so far, the history of existing 100 decades, in these hundred years, especially near decades, countries in the world MANUFACTURER, for reducing engine fuel consumption, constantly undergoes technological transformation to motor world inventions compression explosive motor.But traditional one-piece crankshaft, still behaves used so far.Modern people still take original one bent axle work done drive technology, are very clumsy in fact, because pressure energy is transformed into the drive technology of kinetic energy by one-piece crankshaft motor, seem to can't see the shadow that lever is got twice the result with half the effort.
Due to the available engine alignment of shafts in vertical cylinder in the heart, and in crankshaft & connecting, crank throw is changeless, and the power arm of force and the resistance arm of force are substantially identical.When making its work done, the pressure spot of the arm of force and the distance of the alignment of shafts, and the force bearing point when arm of force makes compression work are all the same with the distance of the alignment of shafts, and the principle not skilfully using lever is used as power merit and compression work.Especially main shaft diameter center is on the vertical centre of cylinder footpath, makes people can not realize starting function After Top Center, in less crank angle, utilizes the hope of maximum pressure work done with larger effective work done radius.
For above-mentioned the deficiencies in the prior art, study a kind of same consumption energy, output power increases, or output power same consumption energy reduces, and reaches the object of consumption reduction synergy.So design a kind of novel centrifugal vuilt-up crankshaft energy-saving engine, thus to make up the deficiencies in the prior art be very necessary.
Summary of the invention
In view of above-mentioned the deficiencies in the prior art, the object of the invention is a kind of novel centrifugal vuilt-up crankshaft energy-saving engine of research and design.In order to realize same consumption energy, output power increases; Output power is identical, and energy consumption reduces, and reaches the object of consumption reduction synergy.
Current explosive motor, no matter be with diesel oil, gasoline or rock gas are fuel, pressure energy is transformed into crankshaft structure and the work done transmission performance thereof of kinetic energy, be still traditional one crankshaft structure, its work done transmission performance is also still and traditional pressure energy is transformed into kinetic energy, directly to outer transmission torque again without other function.And the position relationship of bent axle and cylinder, be also still traditional main shaft radial center and cylinder axis, the position relationship at Shi Yige center.So piston is when work done, by connecting rod press link pin rotate around the alignment of shafts time, the centre distance of link pin center and main shaft is constant.
The present invention revolutionizes the structure of internal-combustion engine machine crankshaft, and the position relationship of bent axle and cylinder.Object is performance when increasing bent axle work done, and effective work done radius during increase work done initial point.Bent axle work done radius is changed with rotation, increases crank radius during engine power, reduce crank radius during engine compresses.
Technical solution of the present invention is achieved in that
Centrifugal vuilt-up crankshaft energy-saving engine of the present invention, is characterized in that described centrifugal vuilt-up crankshaft energy-saving engine comprises casing, work done driving mechanism and transfer mechanism; Casing comprises crankcase and cylinder sleeve body; Cylinder sleeve body is processed with 2 cylinders; Cylinder sleeve body is loaded on crankcase top; Driving mechanism is fixedly loaded in crankcase by dunnage; Piston is loaded in cylinder; Transfer mechanism is loaded on crankcase by bearing support II; Work done driving mechanism is connected by gear I, gear II and gear III with transfer mechanism;
Described work done driving mechanism comprises gear III, bearing support I, zanjon bearing II, dunnage I, location lock ring, zanjon bearing I, main shaft slideway I, main shaft slideway II, link pin sliding handle I, link pin sliding handle II, connecting rod ASSY, piston, bearing shell, dunnage II, gear II, hexagon socket head cap screw I, dunnage III, dunnage IV; Dunnage I and dunnage II are oppositely arranged; The inner side of dunnage I is processed with bearing groove, and bearing groove is built with zanjon bearing I and location lock ring; Bearing plate is pressed on zanjon bearing I outer ring, and is fastened on dunnage I by sunk screw by bearing plate; Main shaft slideway I is loaded in dunnage I, and be positioned on main shaft slideway I axle outside dunnage I and bearing support I and gear II are housed successively, zanjon bearing II passing hole jump ring is fixed in bearing support I; The inner side of dunnage II is processed with bearing groove, and bearing groove is built with zanjon bearing I and location lock ring; Bearing plate is pressed on zanjon bearing I outer ring, and is fastened in dunnage II by sunk screw by bearing plate; Main shaft slideway II is loaded in dunnage II; The both sides of link pin sliding handle I are loaded on main shaft slideway I respectively with on main shaft slideway II, and link pin sliding handle I is equipped with connecting rod ASSY, and the lower end of connecting rod ASSY is connected with the link pin of link pin sliding handle I, and upper end and piston pass through pinned connection; Dunnage III and dunnage IV are oppositely arranged; The inner side of dunnage III is processed with bearing groove, and bearing groove is built with zanjon bearing I and location lock ring; Bearing plate is pressed on zanjon bearing I outer ring, and is fastened in dunnage III by sunk screw by bearing plate; Main shaft slideway III is loaded in dunnage III.Main shaft slideway II is on the axial plane passing dunnage II outer wall, and be processed with a flat key groove, flat key groove is built with flat key; The spindle hole inwall of main shaft slideway III is processed with a flat key groove, matches with flat key; The main shaft of main shaft slideway II inserts in the spindle hole of main shaft slideway III, and is connected as one by hexagon socket head cap screw I; The outside axle of main shaft slideway III is equipped with gear III; The inner side of dunnage IV is processed with bearing groove, and bearing groove is built with zanjon bearing I and location lock ring; Bearing plate is pressed on zanjon bearing I outer ring, and is fastened in dunnage IV by sunk screw by bearing plate; Main shaft slideway IV is loaded in dunnage IV, and be positioned on main shaft slideway IV axle outside dunnage IV and bearing support I and gear II are housed successively, zanjon bearing II passing hole jump ring is fixed in bearing support I; The both sides of link pin sliding handle II are loaded on main shaft slideway III respectively with on main shaft slideway IV; The lower end of connecting rod ASSY is connected with the link pin of link pin sliding handle II, upper end and piston pass through pinned connection; The piston on connecting rod ASSY top is loaded in cylinder;
Transfer mechanism of the present invention comprises transmission shaft, gear I, zanjon bearing III, bearing support II, flange; The two ends of transmission shaft are loaded on crankcase by zanjon bearing III and bearing support II, and flange is equipped with in one end of transmission shaft, and the other end is equipped with anti-return nut; Transmission shaft is equipped with three gears I, is meshed with two gears II and a gear III respectively.
Main shaft slideway I of the present invention, main shaft slideway II, main shaft slideway III assemble with main shaft slideway IV coaxial core.
Between main shaft slideway I of the present invention and dunnage I, between main shaft slideway II and dunnage II, between main shaft slideway III and dunnage III, between main shaft slideway IV and dunnage IV, all bearing shell is housed.
Main shaft slideway I of the present invention, main shaft slideway II, main shaft slideway III, main shaft slideway IV assemble with dunnage I, dunnage II, dunnage III and dunnage IV bias respectively.
Link pin sliding handle I of the present invention is U-shaped structure with link pin sliding handle II; Its structure comprises a link pin and two cranks; The inner plane stem of link pin and two cranks is processed as one; Two crank outerplanars are each identical with crank length with a length, and the slide block that width is less than crank width is processed as one; The crank at link pin and two ends forms U-shaped structure; The another crank afterbody at link pin two ends, is respectively processed with a concentric locating pin-and-hole.
Location of the present invention lock ring is processed with bearing pin.
Main shaft slideway I of the present invention, main shaft slideway II, main shaft slideway III, main shaft slideway IV are processed with slide groove.
The slide block of link pin sliding handle I both sides of the present invention is placed in main shaft slideway I respectively with in the slide groove of main shaft slideway II, and the pin-and-hole of afterbody is enclosed within bearing pin; The slide block of link pin sliding handle II both sides is placed in main shaft slideway III respectively with in the slide groove of main shaft slideway IV, and the pin-and-hole on the tail end of top is enclosed within bearing pin.
Dunnage I of the present invention, dunnage II, dunnage III and dunnage IV are all processed with oil duct.
Centrifugal vuilt-up crankshaft energy-saving engine technology of the present invention, single cylinder, twin-tub and multi-cylinder engine motor that to be applicable to diesel oil, vapour oil and gas be fuel.
Work done transmission principle of the present invention:
Bent axle after the present invention improves is not one, and main shaft diameter center is center, higher cylinder footpath.Below for twin cylinder engine of the present invention unit, introduce the work done transport characteristics of this patent:
A link pin and two cranks are integrated, and the slide block of two crank outerplanars and processing is integrated, therefore at this general name link pin sliding handle.Single-cylinder engine needs two main shafts, and each main shaft one end and a crank are integrated, each crank plane machining concavity groove, and in groove, both sides are wear-resisting sliding surfaces, therefore referred to herein as main shaft slideway.Two main shaft slide grooves are in the face of groove face, respectively the outerplanar slide block of link pin sliding handle two overhung crank is contained in groove, make the outerplanar slide block of link pin two overhung crank, can in the slide groove of both sides simultaneously slide anteroposterior, so far, the bent axle that two main shaft slideways and a link pin sliding handle combine, referred to herein as vuilt-up crankshaft.
The main shaft at vuilt-up crankshaft two ends respectively from inside to outside, passes from the eccentric bearing hole of two dunnages.Two dunnage eccentric bearing hole centers are lateral run-out vertical cylinder center lines, deflection compression one side.Eccentric size is approximately about 40% of engine crank radius.
A set of zanjon bearing I is respectively press-fited with bearing outside diameter drive fit in two dunnage minute surface bearing grooves, high power engine respectively need press-fit two cover zanjon bearing I, and respectively press-fit one with bearing bore diameter drive fit and locate lock ring, two location lock rings respectively have an axial cylindrical alignment pin the outside plane of internal diameter, bearing and lock ring center, location and Shi Yige center, dunnage center are also on the vertical center line of cylinder footpath.
Link pin two ends sliding handle plane afterbody respectively has a positioning pin hole, during assembling, the main shaft at vuilt-up crankshaft two ends, while penetrating from eccentric bearing hole inside two dunnages respectively, both sides are located the alignment pin on lock ring, in point another positioning pin hole embedding two sliding handle afterbodys.Therefore two sliding handles be contained in the main shaft slide groove of the left and right sides are just defined, under the pining down of rear-end alignment pin, make to press link pin by connecting rod during piston work done, link pin passes through the sliding handle at two ends in the slide groove of both sides, and twisting main shaft slideway together rotates.While rotation, due to dunnage main bearing hole, it is the deflection compression one side at lateral run-out dunnage center.And alignment pin is really around dunnage central rotation, turn around so the main shaft slideway of link pin sliding handle twisting both sides often revolves, link pin sliding handle afterbody is under the pining down of alignment pin, and the slide block of link pin two ends sliding handle, in the slide groove of both sides, slide anteroposterior runs once.
When the downward work done of piston moves to horizontal 90 ° of crank angles, link pin sliding handle is pushed into the limit forward by alignment pin, make the centre distance of link pin center now and main shaft maximum, otherwise piston does compression work by lower dead center to top dead center, when moving to horizontal 90 ° of crank angles, link pin sliding handle is pulled back to the limit again by alignment pin, now link pin center and principal axis centre distance minimum.But the crank angle of piston when upper and lower stop, (link pin center) is on the vertical center line in cylinder footpath.And work done and be compressed to laterally 90 ° of crank angles time, the centre distance of link pin center and dunnage, namely the vertical centre point in cylinder footpath is all the same.The present invention that Here it is, to the final purpose of current internal-combustion engine technical innovation.
Advantage of the present invention is apparent, is mainly manifested in:
1, increase effective work done radius (crank radius), contrast with current motor, this motor adds the length of the power arm of force when work done, makes it under uniform pressure condition, due to the lengthening of the arm of force, just increases the torque that main shaft produces.
2, reduce compression work, contrast with current motor, this motor is when making compression work to horizontal 90 °, and crank radius is minimum, and under identical stress condition, because the stressed arm of force shortens, the arm of force produces anti-twisted moment to main shaft and is just lowered.
3, ignition advance angle is increased: contrast with current motor, according to this motor when making compression work, reduce the anti-twisted moment to main shaft, with when crank angle one crosses top dead center, under the advantage that effective work done radius is just larger, suitably strengthen compression pressure, reduce crank angle during work done initial point, make this start function in less crank angle, obtain maximum pressure work done with larger effective work done radius, this is that current motor cannot realize.
4, energy-saving and emission-reduction, contrast with the motor of current identical piston stroke and discharge capacity, with identical speed per hour hundred kilometric fuel consumption per, should reduce about 30% than current motor.
Below just with centrifugal vuilt-up crankshaft energy-saving engine (hereinafter referred to as centrifugal engine) of the present invention, doing a contrast with the current one bent axle petrol engine (hereinafter referred to as current motor) of identical piston stroke and discharge capacity is example:
1, effective work done radius is increased
First we have a talk what and be effective work done radius.Be no matter the explosive motor that what is fuel with, be all the pressure energy produced with fuel combustion, press link pin by piston rod, link pin twists main shaft by crank arm (crank) and rotates.This transmission principle pressure being transformed into torque by bent axle is exactly the principle of lever in fact.As same person presses lever, utilize the levers support point the other end to prize object, press leverage points with identical pressure longer apart from levers support point distance, the strong point of lever is stressed larger, and the power to the conveying of the strong point the other end is larger.If the distance certain apart from levers support point presses lever with specified pressure, if be 100 kilograms to the power of levers support point the other end conveying, so press lever at pressure spot apart from the levers support point distance place of doubling with identical pressure, to the power of levers support point the other end conveying, also should double 200 kilograms.
The pressure that motor produces with fuel combustion, presses link pin by piston rod, and link pin is by crank (cranking arm) twisting main axis.This work done principle is exactly the work done principle of lever in fact.The main shaft diameter center of engine crankshaft and the centre distance of connecting rod pin diameter are referred to as crank radius, distance when this connecting rod pin diameter and the work done of main shaft diameter center, just as the distance of pressure spot and the strong point when pressing lever work done.But the centre distance of connecting rod pin diameter and main shaft diameter is when work done, be not all effective work done distance, that is crank radius is not all effective work done radius in work.Its effective work done radius is along with piston is by top dead center, and crank angle when running to lower dead center work done changes and changes.Its real effectively work done radius, crank angle when utilizing maximum pressure work done from atdc, between the crank angle at the end of work done, no matter crankshaft rotating is to some corners, all should with wrist pin center and link pin central line, the distance in 90 ° with the alignment of shafts, is only effective work done radius of crank.
So centrifugal engine, contrast with the motor of current identical piston stroke, its effective work done radius is large especially.During the crank angle of especially After Top Center work done initial point (maximal pressure force).
2, compression work is reduced
Reducing compression work, being just reduction of motor when doing compression work, power spent when reaching the compression pressure required by motor.Due to the main shaft radial center of centrifugal engine, it is lateral run-out vertical cylinder center, deflection compression one side, and because sliding handle afterbody is under the pining down of locating stud, make outerplanar two slide blocks of two, link pin two ends crank, respectively in the main shaft slide groove of both sides, when twisting main shaft together rotates work done, often rotate a circle, two outerplanar two slide blocks of crank, in the main shaft slide groove of both sides, together slide anteroposterior runs once respectively.And vuilt-up crankshaft work done is when rotating to horizontal 90 ° of corners, it is pushed into the limit forward by the locating stud of sliding handle afterbody by link pin sliding handle, vuilt-up crankshaft work done is rotated to crank radius during horizontal 90 ° of corners maximum.Otherwise when vuilt-up crankshaft utilizes inertial force to do compression work rotation to horizontal 90 ° of corners, connecting rod sliding handle is pulled back to the limit by the locating stud of afterbody again, vuilt-up crankshaft is made to do compression work by lower dead center to top dead center minimum to crank radius during horizontal 90 ° of corners.When this is with regard to making vuilt-up crankshaft utilize the inertial force rotated to do compression work, shortens the length of the stressed arm of force, reducing compression work.When being especially compressed to apart from top dead center 18 ° of crank angle left and right, when wrist pin center and link pin and locating stud center three-core being aligned, piston compression adds the back pressure of catching fire in advance and producing, and most of pressure all passes through locating stud and the location lock ring of link pin sliding handle afterbody, is pressed on bearing inner race.At this moment the inertial rotation power of vuilt-up crankshaft, promotes location lock ring by the locating stud of sliding handle tail end and bearing inner race together rotates, and just can shift piston onto top dead center very easily.This reason can be compared to a personal go-cart push 100 kilogram weights goods go up a slope, more personal than one pickaback 100 kilogram weights goods go up a slope many easily.
3, ignition advance angle is increased
Increase ignition advance angle, be centrifugal engine when the crank angle that work done initial point is less, achieve larger effective work done radius, the dream of the maximum pressure work done utilizing fuel combustion to produce.
According to centrifugal engine when making compression work, there is less paying of compression work and obtain the feature of higher compression pressure, with compared with the effective work done radius during work done of small crankshaft corner, when being still greater than the normal crank angle work done of current motor, the feature of effective work done radius, we have reason suitably to increase compression pressure completely, by ignition advance angle on the basis of current motor normal ignition advance angle, and about 5 ° in advance.That is the current the highest work done pressure that sends of one crank-axle engine is between the crank angle of After Top Center 15 °-20 °.And the highest work done pressure that centrifugal engine sends, then should be produce between the crank angle of After Top Center 10 °-15 °.
More than speaking of as realizing shifting to an earlier date of ignition advance angle, suitably can increase compression pressure.Because when centrifugal engine makes compression work, there is paying with less compression work, exchange the feature of higher compression pressure for.That is centrifugal engine when doing compression work and current motor contrast, when centrifugal engine does compression work, compression pressure is reached current motor, power spent during the compression pressure 1.4Mpa required, approximately only account for current motor, power about 70 percent spent when doing identical compression pressure.
So centrifugal engine, be no more than current motor, under power condition spent when doing maximal pressure compression pressure, suitably should strengthen compression pressure, to guarantee density and the velocity of combustion of fuel molecule and oxygen molecule.
4, energy-saving and emission-reduction
Centrifugal engine is by above three aspect introductions, can find out, due to the structural behaviour of this motor vuilt-up crankshaft, and the position relationship of main shaft diameter center and cylinder axis all differs widely with current motor, the work done effect that final body reveals, power character Economy is all better than current motor.That is centrifugal starting contrasts with the motor of current identical piston stroke discharge capacity, and during work done under the condition of equal-wattage, the fuel consumption of this motor will far below current motor.
We are just with eccentric 17 millimeters of centrifugal engines below, special crankshaft structure and unique work done kind of drive, with the lever work done principle of getting twice the result with half the effort, realize the effect of energy-saving and emission-reduction, with current identical piston stroke 86 millimeters, with the four-stroke gasoline engine of same displacement, do and contrast with energy consumption effect.
People know, motor fuel burning produces work done initial point during maximum pressure, and the less pressure of crank angle After Top Center loss of energy is less, and the power sent is larger, and the power character of motor is better.But motor is difficult to realize this ideal at present.Because be no matter the motor that is fuel with gasoline, diesel oil or rock gas, fuel produces maximal pressure from taking fire to needs the time.With current petrolic work done drive mechanism and operating conditions, its work done initial point is the crank angle of After Top Center 15 °-20 °, the crank angle of atdc runs downwards along with piston and increases, and the volume of firing chamber runs downwards along with piston and increases, the volume of firing chamber is larger, and the nominal fuel maximum pressure range of decrease that should produce of burning is larger.The optimum pressure point of the maximum pressure work done utilizing constant engine fuel combustion to produce is exactly the crank angle of After Top Center about 10 °, and motor is when this crank angle, and combustion chamber volume does not have too large significant change.And when the crank angle of about 20 °, the volume of firing chamber obviously increases, the range of decrease of maximal pressure is also just larger.So during engine power, when nominal fuel burning produces maximum pressure, the size of crank angle is very large on the impact of engine performance.
In fact with the crankshaft structure of current motor and the kind of drive, maximal pressure force during work done, the crank angle selecting After Top Center 15 °-20 ° is rational.Because the motor that piston stroke is 86 millimeters, After Top Center during the crank angle of 15 °, actual effectively work done radius only has 14 millimeters.After Top Center during the crank angle of 20 °, effective work done radius just reaches 18 millimeters.And After Top Center the crank angle of 10 ° time effective work done radius only have 9 millimeters especially.So maximum pressure point selection during work done After Top Center the crank angle of 10 ° time, although obtain the maximum pressure that fuel combustion produces, but because effective work done radius is too little, do not reach the torque effect that high pressure and larger effective work done radius produce main shaft.Shifting to an earlier date on the contrary due to fuel combustion time, the back pressure caused increases the anti-twisted moment that main shaft produces, and sharp little fraud is large.So the setting of current gasoline engine spark advance angle, allow the firing time of a point a little later, make crank angle during work done slightly bigger.Although maximum pressure loss a bit like this, effectively work done radius increases and alleviates back pressure.Crank angle excessive unavoidable balance way when this is also current engine power.
Why the maximal pressure force of centrifugal engine is set between atdc 10-15 °, centrifugal engine is when making compression work to top dead center about 18 ° crank angles as previously described, compression adds the back pressure of catching fire in advance and producing, major part rides on locating stud by sliding handle tail end, and locating stud is together rotated by location lock ring and bearing inner race and piston is pushed into top dead center.So although ignition advance angle shifts to an earlier date about 5 ° than current motor, compression adds the back pressure of catching fire in advance and producing, and also can not exceed current motor normal ignition advance angle, and compression adds the negative effect of the back pressure produced of catching fire in advance.
The highest work done pressure spot of centrifugal engine, After Top Center 10 ° time effective work done radius be 26 millimeter, be substantially equivalent to during the identical crank angle of current motor 9 millimeters 3 times.And After Top Center 15 ° and 20 ° of crank angles time effective work done radius, be 30 and 34 millimeters respectively.When being the identical crank angle of current motor 14 millimeters and 18 millimeters average 2 times.
We are according to centrifugal engine below, and with After Top Center 10 °, 15 ° and 20 °, current motor, during this three crank angles, the multiple of effective work done radius is poor, pressure difference when converting work done to the principle of lever.The nominal fuel of centrifugal engine, the maximal pressure that After Top Center during this three crank angles, burning produces, especially the pressure that After Top Center during about 10 ° crank angles, burning produces, certainly higher than the pressure that burning during After Top Center 15 ° of crank angles produces.And After Top Center 15 ° of crank angles time burning produce pressure, more higher than during atdc 20 ° of crank angles burning produce pressure.If the nominal fuel of motor at present, the pressure that during crank angle of After Top Center 15 ° and 20 °, fuel combustion produces is on average the words of 5Mpa, so according to the effective work done radius of centrifugal engine when this two crank angles, 5Mpa just should be multiplied by the twice of effective work done radius.That is the nominal fuel of centrifugal engine, burning produces crank angle during maximal pressure, no matter After Top Center 10 ° or 15 °, pressure when work done moves to the crank angle of 15 ° and 20 °, all be equivalent to current motor when this two crank angle work done initial points, send about the twice 10Mpa of maximum pressure.In other words, centrifugal engine and current motor, when this two identical crank angles, although the pressure that fuel combustion produces is all 5Mpa, but due to effective work done radius of centrifugal engine, add one times than effective work done radius of current motor, add one times just as the distance of the pressure spot distance strong point of lever.So contrast with current motor, although it is stressed identical to crank arm, main shaft is formed to the moment of twisting, be twice than current motor.But the crank angle making centrifugal engine work done run, reaches current motor, from the crank angle that work done initial point to work done terminates, centrifugal engine need increase some piston strokes.
In addition because link pin is around dunnage center (vertical cylinder center line and main shaft cross central line joint), the circumference of rotation is not circular but irregular ellipse.But work done one side is from top dead center to lower dead center, and be the ellipse arc of rule, during upper and lower stop, link pin center and dunnage centre distance are 43 millimeters, and only has 39 millimeter when horizontal 90 °.When this reduces piston to lower dead center operation work done, do lateral resistance when circumference rotates by connecting rod promotion link pin.
By the motor of above two identical piston strokes and discharge capacity, the contrast of work done condition and work done effect, due to the main shaft diameter misalignment cylinder axis of centrifugal engine, with vuilt-up crankshaft, there is the function of skilful use pressure energy, with the work done kind of drive of getting twice the result with half the effort, improving the work done effect of engine power performance, is that current motor is beyond one's reach.People know, motor terminates whole work from work done initial point to work done, and the pressure that specified fuel combustion produces when engine power initial point is high and low, are very large on the power character impact of motor.For example, during engine power, nominal fuel is 5Mpa at the engine power initial point maximum pressure produced that all burns, when its work done move to laterally 90 ° of crank angles time, Pressure Drop is to 2.5Mpa.If with identical nominal fuel engine power initial point all burn produce maximum pressure be 10 ° of Mpa, when its work done moves to horizontal 90 ° of crank angles, pressure still drops to 2.5Mpa, or higher than 2.5Mpa, this is for current motor, may be the dream that cannot realize.And centrifugal engine achieves this dream.In detail a bit say, centrifugal engine is with the Organizational Structure of its work done transmission system, and the work done performance of bent axle, all creates very favourable condition to engine power and compression.Especially when work done initial point, contrast with current motor, effective work done radius obtains and is multiplied.That centrifugal engine burns with identical nominal fuel with current motor, at the work done initial point of centrifugal engine, the pressure produced during atdc 10 ° makes the torque produced main shaft of cranking arm, the work done initial point being equivalent to current motor After Top Center 15 ° time, more than 3 times when 10 ° of crank angles, about about 17Mpa.Average twice when 15 ° and 20 ° of crank angles, about about 10Mpa.This high pressure explosive force produced instantaneously at engine power initial point, significantly can improve the reason of engine power performance, and with the speed of the powder burning speed of shell, the reason directly having influence on artillery range is the same.The gunpowder of shell is faster in the speed of moment whole burning, and the range straggling of bullet is far away.On the contrary, the speed that the gunpowder of shell all burns is slower, and the range straggling of bullet shells is shorter.The motion speed of piston is fast and slow, and substantially depend on when work done initial point, the pressure produced instantaneously is high and low.And piston is under a load to lower pressure during lower dead center high speed operation to tens crank angle degrees, do not play a part too large to the motion speed of piston.
By above centrifugal engine, with the contrast of each work done condition of current motor, especially in the gap of the effective work done radius of work done initial point, cause the power arm of force of two motors, under identical work done pressure, the moment of torsion difference produced main shaft is great.So the centrifugal vuilt-up crankshaft energy-saving engine after improving, to utilize pressure energy efficiently, make motor to the target of high-power low emission, strided forward again major step.But by the contrast of each work done performance of above two motors and effect, centrifugal engine is under the condition of identical oil consumption, the percentage that the current motor of work ratio improves is how many, accurately cannot calculate, just can only can draw accurate data by room power measurer by experiment.Can only according to two each work done conditions of motor and performance at this, to the power effect that motor produces during work done, roughly the oil consumption of assessment two motors of property is poor.So two motors contrast in the mode of this estimation, centrifugal vuilt-up crankshaft energy-saving engine, deducts the power especially spent by optional feature, contrasts with the petrol engine of current identical piston stroke and discharge capacity, with identical speed per hour hundred kilometric fuel consumption per, about 30% should be reduced than current motor
The spread pattern of cylinder
This accompanying drawing 3 and accompanying drawing 4 are that two cylinder block are in transmission shaft radial side axially-aligned.If arrangement modes more than four cylinders, except two cylinder block are as except figure arrangement, another two cylinder block should arrange to axial at the opposite side of transmission shaft radial direction, form H type, and respective two gears II and a gear III, with being meshed with the gear I of three on transmission shaft.
For alleviating the weight of motor and shortening the length of motor, the motor larger to piston stroke, can attempt two cylinders, four cylinders, six cylinders and eight cylinders, twelve cylinder enine, take a link pin that the mode of two cover connecting rod ASSYs is installed, as shown in Figure 4, on a link pin between dunnage I and another dunnage II, a set of connecting rod ASSY is only installed and piston runs work done in a cylinder, so the motor larger to piston stroke, then should attempt under overstriking lengthens the condition of link pin, a link pin is installed two cover connecting rod ASSYs, make a link pin drive two cover connecting rod ASSYs simultaneously, make the upper and lower synchronous operation in two cylinders of two pistons on two connecting rod ASSYs.
The present invention has novel structure, it is easy, with low cost to process, energy-conserving and environment-protective, effect advantages of higher, it puts goods on the market in enormous quantities and will produce positive social benefit and significant economic benefit.
Accompanying drawing explanation
The present invention has 14 width accompanying drawings, wherein:
Accompanying drawing 1 is plan view of the present invention;
Accompanying drawing 2 is plan view of the present invention;
Accompanying drawing 3 is the K-K view of accompanying drawing 1;
Accompanying drawing 4 is the L-L view of accompanying drawing 3;
Accompanying drawing 5 is the P-P view of accompanying drawing 4;
Accompanying drawing 6 is the M-M view of accompanying drawing 4;
Accompanying drawing 7 is the N-N view of accompanying drawing 4;
Accompanying drawing 8 is main shaft slideway I plan view;
Accompanying drawing 9 is the right elevation of accompanying drawing 8;
Accompanying drawing 10 is link pin sliding handle I structural representation;
Accompanying drawing 11 is the plan view of accompanying drawing 10;
Accompanying drawing 12 is main shaft slideway I, link pin sliding handle I and main shaft slideway II assembly structure schematic diagram;
Accompanying drawing 13 is dunnage I structural representation; I
Accompanying drawing 14 is dunnage I, main shaft slideway I and link pin sliding handle assembly structure schematic diagram.
In the drawings: 1, flange 2, bearing support II 3, zanjon bearing III 4, live axle 5, gear I 6, gear II 7, bearing support I 8, zanjon bearing II 9, dunnage I 10, bearing groove 11, zanjon bearing I 12, main shaft slideway I 13, link pin sliding handle I 14, connecting rod ASSY 15, dunnage II 16, main shaft slideway II 17, gear III 18, dunnage III 19, main shaft slideway III 20, hexagon socket head cap screw I 21, link pin sliding handle II 22, dunnage IV 23, main shaft slideway IV 24, hole jump ring 25, bearing shell 26, oil duct 27, location lock ring 28, crankcase 29, cylinder sleeve body 30, piston 31, cylinder 32, slide groove 33, pin-and-hole 34, crank 35, slide block 36, link pin 37, bearing pin 38, flat key 39, bearing plate 40, sunk screw.
Embodiment
As shown in drawings, described centrifugal vuilt-up crankshaft energy-saving engine comprises casing, work done driving mechanism and transfer mechanism to specific embodiments of the invention; Casing comprises crankcase 28 and cylinder sleeve body 29; Cylinder sleeve body 29 is processed with 2 cylinders 31; Cylinder sleeve body 29 is loaded on crankcase 28 top; Driving mechanism is fixedly loaded in crankcase 28 by dunnage; Piston 30 is loaded in cylinder 31; Transfer mechanism is loaded on crankcase 28 by bearing support II 2; Work done driving mechanism is connected by gear I 5, gear II 6 and gear III 17 with transfer mechanism;
Work done driving mechanism comprises gear III 17, bearing support I 7, zanjon bearing II 8, dunnage I 9, location lock ring 27, zanjon bearing I 11, main shaft slideway I 12, main shaft slideway II 16, link pin sliding handle I 13, link pin sliding handle II 21, connecting rod ASSY 14, piston 30, bearing shell 25, dunnage II 15, gear II 6, hexagon socket head cap screw I 20, dunnage III 18, dunnage IV 22; Dunnage I 9 and dunnage II 15 are oppositely arranged; The inner side of dunnage I 9 is processed with bearing groove 10, and bearing groove 10 is built with zanjon bearing I 11 and location lock ring 27; Bearing plate 39 is pressed on zanjon bearing I 11 outer ring, and is fastened on dunnage I9 by sunk screw 40 by bearing plate 39; Main shaft slideway I 12 is loaded in dunnage I 9, and be positioned on main shaft slideway I 12 axle outside dunnage I 9 and bearing support I 7 and gear II 6 are housed successively, zanjon bearing II 8 passing hole jump ring 24 is fixed in bearing support I 7; The inner side of dunnage II 15 is processed with bearing groove 10, and bearing groove 10 is built with zanjon bearing I 11 and location lock ring 27; Bearing plate 39 is pressed on zanjon bearing I 11 outer ring, and is fastened in dunnage II 15 by sunk screw 40 by bearing plate 39; Main shaft slideway II 16 is loaded in dunnage II 15; The both sides of link pin sliding handle I 13 are loaded on main shaft slideway I 12 respectively with on main shaft slideway II 16, connecting rod ASSY 14 link pin sliding handle I 13 is equipped with, the lower end of connecting rod ASSY 14 is connected with the link pin 36 of link pin sliding handle I 13, and upper end and piston 30 pass through pinned connection; Dunnage III 18 and dunnage IV 22 are oppositely arranged; The inner side of dunnage III 18 is processed with bearing groove 10, and bearing groove 10 is built with zanjon bearing I 11 and location lock ring 27; Bearing plate 39 is pressed on zanjon bearing I 11 outer ring, and is fastened in dunnage III 18 by sunk screw 40 by bearing plate 39; Main shaft slideway III 19 is loaded in dunnage III 18.Main shaft slideway II 16 is on the axial plane passing dunnage II 15 outer wall, and be processed with a flat key groove, flat key groove is built with flat key 38; The spindle hole inwall of main shaft slideway III 19 is processed with a flat key groove, matches with flat key 38; The main shaft of main shaft slideway II 16 inserts in the spindle hole of main shaft slideway III 19, and is connected as one by hexagon socket head cap screw I 20; The outside axle of main shaft slideway III 19 is equipped with gear III 17; The inner side of dunnage IV 22 is processed with bearing groove 10, and bearing groove 10 is built with zanjon bearing I 11 and location lock ring 27; Bearing plate 39 is pressed on zanjon bearing I 11 outer ring, and is fastened in dunnage IV 22 by sunk screw 40 by bearing plate 39; Main shaft slideway IV 23 is loaded in dunnage IV 22, and be positioned on main shaft slideway IV 23 axle outside dunnage IV 22 and bearing support I 7 and gear II 6 are housed successively, zanjon bearing II 8 passing hole jump ring 24 is fixed in bearing support I 7; The both sides of link pin sliding handle II 21 are loaded on main shaft slideway III 19 respectively with on main shaft slideway IV 23; The lower end of connecting rod ASSY 14 is connected with the link pin 36 of link pin sliding handle II 21, and upper end and piston 30 pass through pinned connection; The piston 30 on connecting rod ASSY 14 top is loaded in cylinder 31;
Transfer mechanism comprises transmission shaft 4, gear I 5, zanjon bearing III 3, bearing support II 2, flange 1; The two ends of transmission shaft 4 are loaded on crankcase 28 by zanjon bearing III 3 and bearing support II 2, and flange 1 is equipped with in one end of transmission shaft 4, and the other end is equipped with anti-return nut; Transmission shaft 4 is equipped with three gears I 5, is meshed with two gears II 6 and a gear III 17 respectively.
Main shaft slideway I 12, main shaft slideway II 16, main shaft slideway III 19 assemble with main shaft slideway IV 23 coaxial core.
Between main shaft slideway I 12 and dunnage I 9, between main shaft slideway II 16 and dunnage II 15, between main shaft slideway III 19 and dunnage III 18, between main shaft slideway IV 23 and dunnage IV 22, bearing shell 25 is all housed.
Main shaft slideway I 12, main shaft slideway II 16, main shaft slideway III 19, main shaft slideway IV 23 assemble with dunnage I 9, dunnage II 15, dunnage III 18 and dunnage IV 22 bias respectively.
Link pin sliding handle I 13 and link pin sliding handle II 21 are U-shaped structure; Its structure comprises a link pin 36 and two cranks 34; The inner plane stem of link pin 36 and two cranks 34 is processed as one; Two crank 34 outerplanars are each identical with crank 34 length with a length, and the slide block 35 that width is less than crank 34 width is processed as one; Link pin 36 forms U-shaped structure with the crank 34 at two ends; The another crank afterbody at link pin 36 two ends, is respectively processed with a concentric locating pin-and-hole 33.
Location lock ring 27 is processed with bearing pin 37.
Main shaft slideway I 12, main shaft slideway II 16, main shaft slideway III 19, main shaft slideway IV 23 are processed with slide groove 32.
The slide block 35 of link pin sliding handle I 13 both sides is placed in main shaft slideway I 12 respectively with in the slide groove 32 of main shaft slideway II 16, and the pin-and-hole 33 of afterbody is enclosed within bearing pin 37; The slide block 35 of link pin sliding handle II 21 both sides is placed in main shaft slideway III 19 respectively with in the slide groove 32 of main shaft slideway IV 23, and the pin-and-hole 33 on the tail end of top is enclosed within bearing pin 37.
Dunnage I 9, dunnage II 15, dunnage III 18 and dunnage IV 22 are all processed with oil duct 26
The above; be only preferably embodiment of the present invention; but protection scope of the present invention is not limited thereto; allly be familiar with those skilled in the art in technical scope disclosed by the invention, be equal to replace or change according to technological scheme of the present invention and design of the present invention thereof and all should be encompassed within protection scope of the present invention.
Claims (9)
1. a centrifugal vuilt-up crankshaft energy-saving engine, is characterized in that described centrifugal vuilt-up crankshaft energy-saving engine comprises casing, work done driving mechanism and transfer mechanism; Casing comprises crankcase (28) and cylinder sleeve body (29); Cylinder sleeve body (29) is processed with 2 cylinders (31); Cylinder sleeve body (29) is loaded on crankcase (28) top; Driving mechanism is fixedly loaded in crankcase (28) by dunnage; Piston (30) is loaded in cylinder (31); Transfer mechanism is loaded on crankcase (28) by bearing support II (2); Work done driving mechanism is connected by gear I (5), gear II (6) and gear III (17) with transfer mechanism;
Described work done driving mechanism comprises gear III (17), bearing support I (7), zanjon bearing II (8), dunnage I (9), location lock ring (27), zanjon bearing I (11), main shaft slideway I (12), main shaft slideway II (16), link pin sliding handle I (13), link pin sliding handle II (21), connecting rod ASSY (14), piston (30), bearing shell (25), dunnage II (15), gear II (6), hexagon socket head cap screw I (20), dunnage III (18), dunnage IV (22), dunnage I (9) and dunnage II (15) are oppositely arranged, the inner side of dunnage I (9) is processed with bearing groove (10), and bearing groove (10) is built with zanjon bearing I (11) and location lock ring (27), bearing plate (39) is pressed on zanjon bearing I (11) outer ring, and is fastened on dunnage I (9) by sunk screw (40) by bearing plate (39), main shaft slideway I (12) is loaded in dunnage I (9), be positioned on main shaft slideway I (12) axle outside dunnage I (9) and bearing support I (7) and gear II (6) are housed successively, zanjon bearing II (8) passing hole jump ring (24) is fixed in bearing support I (7), the inner side of dunnage II (15) is processed with bearing groove (10), and bearing groove (10) is built with zanjon bearing I (11) and location lock ring (27), bearing plate (39) is pressed on zanjon bearing I (11) outer ring, and is fastened in dunnage II (15) by sunk screw (40) by bearing plate (39), main shaft slideway II (16) is loaded in dunnage II (15), the both sides of link pin sliding handle I (13) are loaded on main shaft slideway I (12) respectively with on main shaft slideway II (16), connecting rod ASSY (14) link pin sliding handle I (13) is equipped with, the lower end of connecting rod ASSY (14) is connected with the link pin (36) of link pin sliding handle I (13), and upper end and piston (30) pass through pinned connection, dunnage III (18) and dunnage IV (22) are oppositely arranged, the inner side of dunnage III (18) is processed with bearing groove (10), and bearing groove (10) is built with zanjon bearing I (11) and location lock ring (27), bearing plate (39) is pressed on zanjon bearing I (11) outer ring, and is fastened in dunnage III (18) by sunk screw (40) by bearing plate (39), main shaft slideway III (19) is loaded in dunnage III (18).Main shaft slideway II (16) is on the axial plane passing dunnage II (15) outer wall, and be processed with a flat key groove, flat key groove is built with flat key (38); The spindle hole inwall of main shaft slideway III (19) is processed with a flat key groove, matches with flat key (38); The main shaft of main shaft slideway II (16) inserts in the spindle hole of main shaft slideway III (19), and is connected as one by hexagon socket head cap screw I (20); The outside axle of main shaft slideway III (19) is equipped with gear III (17); The inner side of dunnage IV (22) is processed with bearing groove (10), and bearing groove (10) is built with zanjon bearing I (11) and location lock ring (27); Bearing plate (39) is pressed on zanjon bearing I (11) outer ring, and is fastened in dunnage IV (22) by sunk screw (40) by bearing plate (39); Main shaft slideway IV (23) is loaded in dunnage IV (22), be positioned on main shaft slideway IV (23) axle outside dunnage IV (22) and bearing support I (7) and gear II (6) are housed successively, zanjon bearing II (8) passing hole jump ring (24) is fixed in bearing support I (7); The both sides of link pin sliding handle II (21) are loaded on main shaft slideway III (19) respectively with on main shaft slideway IV (23); The lower end of connecting rod ASSY (14) is connected with the link pin (36) of link pin sliding handle II (21), and upper end and piston (30) pass through pinned connection; The piston (30) on connecting rod ASSY (14) top is loaded in cylinder (31);
Described transfer mechanism comprises transmission shaft (4), gear I (5), zanjon bearing III (3), bearing support II (2), flange (1); The two ends of transmission shaft (4) are loaded on crankcase (28) by zanjon bearing III (3) and bearing support II (2), flange (1) is equipped with in one end of transmission shaft (4), and the other end is equipped with anti-return nut; Transmission shaft (4) is equipped with three gears I (5), is meshed with two gears II (6) and a gear III (17) respectively.
2. centrifugal vuilt-up crankshaft energy-saving engine according to claim 1, is characterized in that described main shaft slideway I (12), main shaft slideway II (16), main shaft slideway III (19) assemble with main shaft slideway IV (23) coaxial core.
3. centrifugal vuilt-up crankshaft energy-saving engine according to claim 1, is characterized in that between described main shaft slideway I (12) and dunnage I (9), between main shaft slideway II (16) and dunnage II (15), between main shaft slideway III (19) and dunnage III (18), between main shaft slideway IV (23) and dunnage IV (22), bearing shell (25) is all housed.
4. centrifugal vuilt-up crankshaft energy-saving engine according to claim 1, is characterized in that described main shaft slideway I (12), main shaft slideway II (16), main shaft slideway III (19), main shaft slideway IV (23) assemble with dunnage I (9), dunnage II (15), dunnage III (18) and dunnage IV (22) bias respectively.
5. centrifugal vuilt-up crankshaft energy-saving engine according to claim 1, is characterized in that described link pin sliding handle I (13) is U-shaped structure with link pin sliding handle II (21); Its structure comprises a link pin (36) and two cranks (34); Link pin (36) is processed as one with the inner plane stem of two cranks (34); Two crank (34) outerplanars are each identical with crank (34) length with a length, and the slide block (35) that width is less than crank (34) width is processed as one; Link pin (36) forms U-shaped structure with the crank (34) at two ends; The another crank afterbody at link pin (36) two ends, is respectively processed with a concentric locating pin-and-hole (33).
6. centrifugal vuilt-up crankshaft energy-saving engine according to claim 1, is characterized in that described location lock ring (27) is processed with bearing pin (37).
7. centrifugal vuilt-up crankshaft energy-saving engine according to claim 1, is characterized in that described main shaft slideway I (12), main shaft slideway II (16), main shaft slideway III (19), main shaft slideway IV (23) are processed with slide groove (32).
8. centrifugal vuilt-up crankshaft energy-saving engine according to claim 5, it is characterized in that the slide block (35) of described link pin sliding handle I (13) both sides is placed in main shaft slideway I (12) respectively with in the slide groove (32) of main shaft slideway II (16), the pin-and-hole (33) of afterbody is enclosed within bearing pin (37); The slide block (35) of link pin sliding handle II (21) both sides is placed in main shaft slideway III (19) respectively with in the slide groove (32) of main shaft slideway IV (23), and the pin-and-hole (33) on the tail end of top is enclosed within bearing pin (37).
9. centrifugal vuilt-up crankshaft energy-saving engine according to claim 1, is characterized in that described dunnage I (9), dunnage II (15), dunnage III (18) and dunnage IV (22) are all processed with oil duct (26).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510694563.XA CN105221259B (en) | 2015-07-08 | 2015-10-21 | Centrifugal vuilt-up crankshaft energy-saving engine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2015103975489 | 2015-07-08 | ||
| CN201510397548.9A CN104963772A (en) | 2015-07-08 | 2015-07-08 | Centrifugal combined crankshaft energy-saving engine |
| CN201510694563.XA CN105221259B (en) | 2015-07-08 | 2015-10-21 | Centrifugal vuilt-up crankshaft energy-saving engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105221259A true CN105221259A (en) | 2016-01-06 |
| CN105221259B CN105221259B (en) | 2017-11-07 |
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|---|---|---|---|
| CN201510397548.9A Pending CN104963772A (en) | 2015-07-08 | 2015-07-08 | Centrifugal combined crankshaft energy-saving engine |
| CN201510694563.XA Active CN105221259B (en) | 2015-07-08 | 2015-10-21 | Centrifugal vuilt-up crankshaft energy-saving engine |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201510397548.9A Pending CN104963772A (en) | 2015-07-08 | 2015-07-08 | Centrifugal combined crankshaft energy-saving engine |
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| RU2115805C1 (en) * | 1996-08-06 | 1998-07-20 | Юрий Сергеевич Ткаченко | Piston machine |
| JP2000130101A (en) * | 1998-10-29 | 2000-05-09 | Nikko:Kk | Four-stroke internal combustion engine |
| RU2280771C2 (en) * | 2004-05-19 | 2006-07-27 | Владимир Александрович Ворогушин | Motion converting device |
| CN101629515A (en) * | 2009-08-18 | 2010-01-20 | 刘佳骏 | Automatically varied crank-link mechanism of four-stroke internal combustion engine |
| JP2010261575A (en) * | 2009-04-30 | 2010-11-18 | Yutaka Abe | Link device to put connecting rod mounting shaft in double speed rotation |
| WO2013122380A1 (en) * | 2012-02-14 | 2013-08-22 | Maeng Ho Jae | Apparatus for varying compression ratio |
| CN205064096U (en) * | 2015-07-08 | 2016-03-02 | 刘丕财 | Energy -conserving engine of centrifugal vuilt -up crankshaft |
-
2015
- 2015-07-08 CN CN201510397548.9A patent/CN104963772A/en active Pending
- 2015-10-21 CN CN201510694563.XA patent/CN105221259B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| RU2115805C1 (en) * | 1996-08-06 | 1998-07-20 | Юрий Сергеевич Ткаченко | Piston machine |
| JP2000130101A (en) * | 1998-10-29 | 2000-05-09 | Nikko:Kk | Four-stroke internal combustion engine |
| RU2280771C2 (en) * | 2004-05-19 | 2006-07-27 | Владимир Александрович Ворогушин | Motion converting device |
| JP2010261575A (en) * | 2009-04-30 | 2010-11-18 | Yutaka Abe | Link device to put connecting rod mounting shaft in double speed rotation |
| CN101629515A (en) * | 2009-08-18 | 2010-01-20 | 刘佳骏 | Automatically varied crank-link mechanism of four-stroke internal combustion engine |
| WO2013122380A1 (en) * | 2012-02-14 | 2013-08-22 | Maeng Ho Jae | Apparatus for varying compression ratio |
| CN205064096U (en) * | 2015-07-08 | 2016-03-02 | 刘丕财 | Energy -conserving engine of centrifugal vuilt -up crankshaft |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105221259B (en) | 2017-11-07 |
| CN104963772A (en) | 2015-10-07 |
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