CN104727936A - Double-piston rotor type internal combustion engine - Google Patents
Double-piston rotor type internal combustion engine Download PDFInfo
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- CN104727936A CN104727936A CN201510029762.9A CN201510029762A CN104727936A CN 104727936 A CN104727936 A CN 104727936A CN 201510029762 A CN201510029762 A CN 201510029762A CN 104727936 A CN104727936 A CN 104727936A
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Abstract
The invention discloses a double-piston rotor type internal combustion engine. A first rotor is composed of a rotary shaft disc, first pistons and a first rotating shaft; the bottom face of a cover board is connected with the end faces of the first pistons; a second rotor is composed of a second rotating shaft and second pistons; an upper end disc and a lower end disc of a disc-shaped part are connected with a combustion chamber shell and a flange plate of a gear case respectively; a first cylindrical gear installed at the shaft end of the first rotating shaft is alternately meshed with incomplete cylindrical gears of a first gear shaft and a second gear shaft; a second cylindrical gear installed at the shaft end of the second rotary shaft is alternately meshed with the incomplete cylindrical gears of the first gear shaft and the second gear shaft; a cylindrical gear of a cylindrical gear shaft is meshed with cylindrical gears of the first gear shaft and a power output gear shaft; an oval-shaped gear of an oval-shaped gear shaft is meshed with oval-shaped gears of the second gear shaft and the power output gear shaft. The double-piston rotor type internal combustion engine is low in oil consumption, high in power to weight ratio, large in torque, simple and compact in structure, low in vibration, long in service life, easy to design and easy to manufacture.
Description
Technical field
The present invention relates to technical field of internal combustion engines, particularly rotary-piston class double-piston rotary internal combustion engine.
Background technique
Heat engine is the device of mechanical energy by thermal power transfer, and internal-combustion engine is an important kind of heat engine, and internal-combustion engine mainly comprises ignition system, combustion system, transmission system, cooling system, oil supply system, lubrication system etc.
Since about 1898 Christian era crankshaft connecting rod type internal-combustion engine invention so far, in surface car, shipping and various power equipment, crankshaft connecting rod type internal-combustion engine obtains to be applied the most widely, and greatly accelerates the historical progress of the mankind.The basic functional principle of crankshaft connecting rod type internal-combustion engine, that the pressurized gas that piston is burnt in cylinder promote to move up and down, and drive crankshaft rotating by connecting rod, the straight reciprocating motion of piston is converted to the unidirectional rotary motion of bent axle, thus realize heat to power output and the Power output of crankshaft connecting rod type internal-combustion engine.
The key technical indexes evaluating internal-combustion engine has power to weight ratio (power/weight ratio also adopts cylinder power per liter index sometimes), oil consumption rate, anufacturability, working service life-span etc.For crankshaft connecting rod type internal-combustion engine, it is that crankshaft connecting rod type transmission system by piston, connecting rod and bent axle triplicity completes that engine power exports.This internal-combustion engine mainly contains following structural disadvantage:
1, crankshaft connecting rod type pass that mixed gas in cylinder of internal-combustion engine is maximum at pressure, volume minimum in period of combustion short, piston is now descending, makes incomplete combustion, and exhaust gas concentration is high, and work doing efficiency is low.Existing crankshaft connecting rod type internal-combustion engine is in order to improve engine performance, all in the premature ignition in various degree of piston arrives budc or oil spout, object be in order to allow mixed gas burn sooner when combustion chamber volume is minimum, more complete, thus larger power stage can be obtained, and reduce the discharging waste gas concentration of motor, but do like this and also create certain negative effect: because of premature ignition, in-cylinder pressure sharply raises, block piston stroking upward, add compression negative work, and easily cause combustion knock phenomenon.This contradiction exists all the time in existing crankshaft connecting rod type internal-combustion engine.
2, in crankshaft connecting rod type internal combustion engine operation process, connecting rod is to the force direction periodically-varied of piston, and when engine power exports maximum, connecting rod also reaches near maximum value along cylinder wall surface Normal direction the active force of piston, cause the frictional power loss between piston and cylinder very large thus, and easily cause the damage that between piston and cylinder, surface causes because of friction.
3, in the operation process of crankshaft connecting rod type internal-combustion engine, piston is in a kind of to-and-fro motion state all the time, during air inlet, piston enters compression stroke again very soon in lower dead center moment, thus the more fresh mixed oil gas of more time inspiration is not had when cylinder body volume is maximum, during exhaust, piston enters intake stroke again very soon to top dead center moment, thus when making volume of cylinder minimum, do not have the more time to allow waste gas farthest discharge, these situations finally all affect more fresh mixed oil gas and enter cylinder, thus cause engine breathing efficiency low, the raising of HP, hp/litre is made to be subject to certain impact.
4, crankshaft & connecting is not axisymmetric parts, and the vibration caused by crankshaft & connecting in internal combustion engine operation process is large, noise is large; Crankshaft & connecting has much difficulty in healing weighing apparatus, and its manufacturing process is more complicated, and cost is high; In use, piston, crankshaft & connecting etc. are easy to wear, and maintenance expenses is high; Adopt the internal-combustion engine limit speed of crankshaft-link rod low, seriously constrain the raising of motor power to weight ratio.
5, the complex structure such as closure, crankshaft-link rod of crankshaft connecting rod type internal-combustion engine, takes up room large, causes engine structure compact not.
Since entering for 20th century, manifesting of energy crisis, and environmental pollution problem is intensification, facilitates the design improvement work to crankshaft connecting rod type internal-combustion engine.At present, through the design improvement in multiple stages such as pressurized combustion, EFI improvement, the technical performance index of crankshaft connecting rod type internal-combustion engine has reached ultimate attainment substantially, but the restriction of the structural disadvantage by above-mentioned crankshaft connecting rod type internal-combustion engine, want the internal-combustion engine obtaining better technical performance index, only have and adopt new internal combustion (IC) Engine Design scheme.
As far back as 20 beginnings of the century, there is a kind of internal-combustion engine being called as triangle rotor type motor, and obtained afterwards and apply comparatively widely.Compared with crankshaft connecting rod type internal-combustion engine, triangle rotor type motor have employed the IC engine transmission system design of gear-driven form, and the axial symmetry of gear drive is better, and Engine Limit rotating speed is high, therefore the power to weight ratio of motor is more outstanding, and structure is also more compact.But triangle rotor type motor also also exists some shortcomings part.Such as cylinder combustion burning is insufficient, oil consumption is excessive, and output shaft torque is too small, cylinder seal difficulty etc.This is because the swelling pressure that rotary polygonal piston engine cylinder combustion gas acts on rotor side surface are divided into two power, try hard to recommend dynamic output shaft for one and rotate, and another power point to output shaft center, thus cause the output torque of complete machine too small; Make rate of combustion too low because its cylinder is long and narrow, excessive oil consumption; Because use the cylinder of special shape, result in the difficulty that cylinder manufacturing and cylinder seal manufacture and design.The some problem that above-mentioned triangle rotor type motor exists, causes it day by day serious today to be difficult to promote the use of in energy crisis and environmental pollution problem on a large scale.
Enter 21 century, on the one hand, the angle from social demand:
1, energy crisis is more remarkable, and environmental problem is on the rise, and the emission standard of internal-combustion engine improves constantly, thus impels the mankind to find the internal-combustion engine technology of energy-conserving and environment-protective more.
2, in car and boat power plant field, especially huge in market family-sized car field, by the restriction of battery flying power, battery security, charging public utility construction degree of coverage etc., the family-sized car market share of pure motorized motions is still very low for a comparatively long period of time, and the green power device practicality becoming the family-sized car of future city society etc. is selected by the internal-combustion engine of oily electric mixed form.
3, at military technological field, the battlefield surroundings of Future Information, the Innovation Input that various unmanned vehicle is equipped will be promoted further, other power plant such as relative aero-turbine, internal-combustion engine, with technical advantages such as its obvious low oil consumption, long lifetime, low costs, will continue to occupy one seat in unmanned vehicle power plant field.
4, other aspects, as industry, model plane motion industry, air sport industry etc. are patrolled and examined in personal aircraft industry, aviation plant protection industry, aviation, internal-combustion engine is by continuity its important power plant role and status.
On the other hand, from the angle of internal-combustion engine technology development:
1, crankshaft connecting rod type internal-combustion engine is through some design improvement, and its technical performance reaches the limit of substantially, and its technical performance index power to weight ratio, oil consumption rate, anufacturability, working service life-span etc. are difficult to reach higher requirement.
2, triangle rotor type motor is a breakthrough of internal-combustion engine technology, but the technology weaknesses such as its high oil consumption, low output torque, sealing difficulty make it be difficult to become the main body of internal-combustion engine technology of new generation.
Although 3, triangle rotor type motor has many technology weaknesses, but the brand new form that it adopts, open new design philosophy, open the beginning of " rotary-piston class internal-combustion engine ", be expected to the many structural disadvantage solving crankshaft connecting rod type internal-combustion engine, so in today of 21 century, there is the patent of invention of more " rotary-piston class internal-combustion engine ".But just so far, in such patent of invention, some patents are the mutation of crankshaft connecting rod type internal-combustion engine, its structure still retain the component of crankshaft-link rod shape, the performance that have impact on internal-combustion engine realizes; Some patent structure designs are too complicated, have impact on the power to weight ratio of internal-combustion engine, anufacturability, working service life-span etc.; Some patents lack necessary Quantitative design and analysis, create according to its conceptual design the technical performance that in fact product does not reach patent nominal.
In sum: 21 century needs the technical order such as a kind of power to weight ratio, oil consumption rate, anufacturability, working service life-span to have the internal-combustion engine technology of important breakthrough, and " rotary-piston class internal-combustion engine " likely becomes the internal-combustion engine technology of new generation meeting these technical requirements.
Summary of the invention
The object of this invention is to provide double-piston rotary internal combustion engine, use for reference the excellent design theory of " rotary-piston ", by fundamental difference in crankshaft connecting rod type internal-combustion engine, also the heating power Transfer Structure Design of triangle rotor type motor is significantly different from, realize the important breakthrough of internal-combustion engine in the key technical indexes such as power to weight ratio, oil consumption rate, anufacturability, working service life-spans, to meet the user demand of mankind's combustion motor technology.
The present invention takes following technological scheme to realize above-mentioned purpose.Double-piston rotary internal combustion engine, comprise the first rotor, cover plate, the second rotor, dish, burning chamber shell and gear-box, the first rotor is Y-shaped, be made up of rotating shaft dish, first piston body and the first turning axle, the center of rotating shaft dish one side is provided with the first turning axle, rotating shaft dish another side is provided with two first piston bodies around the first turning axle axisymmetrical, and the axle head of the first turning axle is provided with keyway, and the axle center of the first turning axle is provided with axis hole;
Cover plate is garden plate-like, and the centre of cover plate is provided with the boss of band central through bore, and the periphery of cover plate is provided with chimb; The bottom surface of cover plate is connected with first piston body end face;
Second rotor is T-shaped, is made up of the second turning axle and the second piston body, and one end of the second turning axle is symmetrically arranged with two the second piston bodies, and the termination of the other end of the second turning axle is provided with keyway, and first piston body is equal with the outer circumference diameter of the second piston body;
The Pan Zhou center of dish is provided with axis hole, and the two ends of dish axle are connected with end plate and lower end plate, and upper end plate periphery and lower end plate periphery are provided with screw; Second turning axle is threaded onto in the axis hole of the first turning axle, and the first turning axle and the second turning axle are all threaded onto in the axis hole at Pan Zhou center, is set with burning chamber shell outside first piston body and the second piston body;
Burning chamber shell is in falling peviform, periphery at the bottom of the room of burning chamber shell is provided with flange plate, flange plate is provided with screw, burning chamber shell periphery is provided with porting, on burning chamber shell, the offside of porting is provided with the pilot hole of spark plug/oil sprayer, and spark plug/oil sprayer is fixedly installed in pilot hole; The upper end plate of dish is adjacent with the rotating shaft dish of the first rotor, and the screw of the upper end plate of dish and the screw of burning chamber shell flange plate are bolted;
Gear-box is peviform, and be provided with axis hole in the middle of bottom it, the periphery of gear-box upper end case mouth is provided with flange plate, and flange plate is provided with screw and is bolted with the valve snail hole, lower end of dish; Bottom gear-box, axis hole is provided with power output gear axle, the both sides of power output gear axle are provided with oval gear axle and cylindrical gear shaft, power output gear axle is provided with an oval gear and a cylindrical gears, oval gear on power output gear axle engages with the oval gear on oval gear axle, and the cylindrical gears on power output gear axle engages with the cylindrical gears in cylindrical gear shaft; First gear shaft is provided with a complete cylindrical gears and two incomplete cylindrical gearss, the second gear shaft is provided with an oval gear and two incomplete cylindrical gearss; Cylindrical gears in cylindrical gear shaft engages with the complete cylindrical gears on the first gear shaft; Oval gear on oval gear axle engages with the oval gear on the second gear shaft; The shaft with keyway end of the second turning axle and the first turning axle is all positioned at gear-box, the axle head of the first turning axle is equipped with the first cylindrical gears, the axle head of the second turning axle is equipped with the second cylindrical gears, first cylindrical gears alternately engages with the incomplete cylindrical gears of the first gear shaft and the incomplete cylindrical gears of the second gear shaft, and the second cylindrical gears alternately engages with the incomplete cylindrical gears of the first gear shaft and the incomplete cylindrical gears of the second gear shaft.
The gear teeth of two incomplete cylindrical gearss of described first gear shaft are axially complementary.
The gear teeth of two incomplete cylindrical gearss of described second gear shaft are axially complementary.
Described dish can be individual layer card, and be provided with axis hole in the middle of card, card periphery offers screw.
Burning chamber shell in the present invention, the first rotor, cover plate, second rotor is jointly separated out four and is isolated from each other and the cylinder of variable volume, in internal combustion engine operation process, observe from power output gear shaft to the first rotor and bitrochanteric drive connection, uniform rotation campaign on power output gear axle is respectively through two-way, one tunnel is the alternately engagement driving conversion of " power output gear axle-oval gear axle-the second gear shaft-the first cylindrical gears/the second cylindrical gears " of two the oval gear groups including into series relationship, another road is the alternately engagement driving conversion of " power output gear axle-cylindrical gear shaft-the first gear shaft-the second cylindrical gears/the first cylindrical gears " of constant ratio, finally convert the first rotor and the bitrochanteric periodicity variable speed motion with fixed skew to.Make the volume periodicity increase and decrease successively of four cylinders thus, and be periodically in air-breathing, compression, acting, exhaust stroke successively, thus cylinder of internal-combustion engine produces circulation merit, and by power output gear axially outer outputting power.
Double-piston rotary internal combustion engine provided by the present invention, has following beneficial effect:
1, significantly can reduce engine consumption, thus improve fuel economy, and improve engine exhaust emission.
2, the power to weight ratio of motor can significantly be improved.
3, engine structure is simple, and anufacturability is good.
4, engine luggine and noise level low, smooth running, moving element is few, thus the motor working service life-span is long.
5, engine structure is compact.
6, engine power output torque is large.
7, the multiple design parameter adjustable of motor.
8, only need very little structural design adjustment, the present invention can change into high performance pump.
Accompanying drawing explanation
Fig. 1 is perspective view of the present invention.
Fig. 2 is stereochemical structure decomposing schematic representation of the present invention.
Fig. 3 is the perspective view of the first rotor of the present invention.
Fig. 4 is the perspective view of cover plate of the present invention.
Fig. 5 is the perspective view of the first rotor of the present invention and cover plate combination.
Fig. 6 is bitrochanteric perspective view of the present invention.
Fig. 7 is the perspective view of dish of the present invention.
Fig. 8 is the plan view of burning chamber shell of the present invention.
Fig. 9 be in Fig. 8 A-A to sectional structure schematic diagram.
Figure 10 is the perspective view of the first gear shaft of the present invention.
Figure 11 is the perspective view of the second gear shaft of the present invention.
Figure 12 is rotor motion of the present invention and volume of cylinder change schematic diagram (power output gear Shaft angle is 0 ° of moment).
Figure 13 is rotor motion of the present invention and volume of cylinder change schematic diagram (power output gear Shaft angle is 90 ° of moment).
Figure 14 is rotor motion of the present invention and volume of cylinder change schematic diagram (power output gear Shaft angle is 180 ° of moment).
Figure 15 is rotor motion of the present invention and volume of cylinder change schematic diagram (power output gear Shaft angle is 270 ° of moment).
Figure 16 is rotor motion of the present invention and volume of cylinder change schematic diagram (power output gear Shaft angle is 360 ° of moment).
Figure 17 is rotor motion of the present invention and volume of cylinder change schematic diagram (power output gear Shaft angle is 450 ° of moment).
Figure 18 is rotor motion of the present invention and volume of cylinder change schematic diagram (power output gear Shaft angle is 540 ° of moment).
Figure 19 is rotor motion of the present invention and volume of cylinder change schematic diagram (power output gear Shaft angle is 630 ° of moment).
Figure 20 is rotor motion of the present invention and volume of cylinder change schematic diagram (power output gear Shaft angle is 720 ° of moment).
Figure 21 is that cylinder of the present invention is maximum with minimum volume view.
Figure 22 is the instantaneous transmission ratio schematic diagram of an oval gear group engagement driving.
Figure 23 is two oval gear group resultant gear ratio schematic diagram of one-tenth series relationship of the present invention.
Figure 24 is the first rotor of the present invention and the instantaneous transmission ratio schematic diagram of the relative power output gear axle of the second rotor.
Figure 25 is normalized combustion chamber volume variable quantity-time curve of the present invention.
Figure 26 is the normalized combustion chamber volume variable quantity-time curve of crankshaft connecting rod type internal-combustion engine.
Figure 27 is the indicator diagram (p-v figure) of desirable constant volume cycle (representing by beading fine line I), crankshaft connecting rod type internal-combustion engine actual cycle (representing with thick dashed line III), actual cycle of the present invention (representing with heavy line II).
Embodiment
Below in conjunction with drawings and Examples, the present invention is described further.
embodiment 1:double-piston rotary internal combustion engine of the present invention, comprises combustion system, transmission system etc., see Fig. 1 to Figure 11.
The first rotor 1 is Y shape part, comprise rotating shaft dish 101, one end of rotating shaft dish 101 is two first piston bodies 102 with the first turning axle 103 axisymmetrical, the other end is provided with the first turning axle 103, the termination of the first turning axle 103 is provided with keyway, the axle center of the first turning axle 103 is provided with axis hole, cover plate 2 is garden plate-like, cover plate 2 also offers the some through holes corresponding with position on first piston body 102, between the first rotor 1 and cover plate 2, use several bolts passing first piston body 102 and cover plate 2 through hole to be connected and fixed.Second rotor 3 is T-shaped structure, and be provided with the second turning axle 31, one end of second turning axle 31 is provided with and offers keyway, the outer circumference diameter of first piston body 102 and the second piston body 32 and fan angle with the other end of two of axisymmetrical the second piston body 32, second turning axlees 31
all equal.Second rotor 3 is installed with the first rotor 1 is coaxial and can relatively rotates, carry out the second rotor 3 and the first rotor 1 coaxial install time, first by the axis hole of the keyway arrangements end of the second rotor 3 through the first turning axle 103 axle center, and then being mounted with between the first rotor 1 and cover plate 2 is carried out.Pan Zhou 43 center of dish 4 is provided with axis hole, and the two ends of dish axle 43 are connected with end plate 41 and lower end plate 42, and upper end plate 41 is beneficial to heat radiation in latticed, and upper end plate 41 periphery and lower end plate 42 periphery are provided with screw.After in the axis hole that second turning axle 31 is threaded onto the first turning axle 103, then be threaded onto together in dish axle 43 central shaft hole.Burning chamber shell 5 is set with outside first piston body 102 and the second piston body 32, burning chamber shell 5 is in falling peviform, the top, room 51 of burning chamber shell 5 is provided with grid hole and is beneficial to heat radiation, at the bottom of room, the periphery of 52 is provided with flange plate, flange plate is provided with screw, burning chamber shell 5 periphery is provided with porting 53, and on burning chamber shell 5, the offside of porting 53 is provided with the pilot hole 54 of spark plug/oil sprayer 7, and spark plug/oil sprayer 7 is fixedly installed in pilot hole 54.The upper end plate 41 of dish 4 is adjacent with the rotating shaft dish 101 of the first rotor 1, and the screw of the upper end plate 41 of dish 4 and the screw of burning chamber shell 5 flange plate are bolted.Gear-box 6 is in peviform, axis hole is provided with in the middle of bottom it, the power output gear axle 10 of internal-combustion engine passes with outside outputting power from this hole, and the periphery of gear-box 6 upper end case mouth is provided with flange plate, and flange plate is provided with screw and is bolted with lower end plate 42 screw of dish 4.
The both sides of power output gear axle 10 are provided with oval gear axle 14 and cylindrical gear shaft 13, power output gear axle 10 is provided with an oval gear and a cylindrical gears, and engages with the oval gear of oval gear axle 14 and the cylindrical gears of cylindrical gear shaft 13 respectively.First gear shaft 8 is provided with a complete cylindrical gears and two incomplete cylindrical gearss 81, 82, second gear shaft 9 is provided with an oval gear and two incomplete cylindrical gearss 91, 92, the cylindrical gears of cylindrical gear shaft 13 engages with the complete cylindrical gears of the first gear shaft 8, the oval gear of oval gear axle 14 engages with the oval gear of the second gear shaft 9, the shaft with keyway end of the second turning axle 31 and the first turning axle 103 is all positioned at gear-box 6, the axle head of the first turning axle 103 is equipped with the first cylindrical gears 11, second turning axle 31 axle head is equipped with the second cylindrical gears 12, first cylindrical gears 11 alternately engages with the incomplete cylindrical gears 81 of the first gear shaft 8 and the incomplete cylindrical gears 91 of the second gear shaft 9, second cylindrical gears 12 alternately engages with the incomplete cylindrical gears 82 of the first gear shaft 8 and the incomplete cylindrical gears 92 of the second gear shaft 9.
The oval gear that second gear shaft 9, oval gear axle 14, power output gear axle 10 are installed, its eccentricity is 1/3rd, and its major semi axis size is equal to each other; The cylindrical gears of power output gear axle 10 and the cylindrical gears of cylindrical gear shaft 13, its gear joint garden radius ratio is 1:1; The cylindrical gears of cylindrical gear shaft 13 and the complete cylindrical gears of the first gear shaft 8, its gear joint garden radius ratio is 1:2; Two incomplete cylindrical gears 81,82 and first cylindrical gears 11/ second cylindrical gearss 12 of the first gear shaft 8, its gear joint garden radius ratio is all 2:5; Two incomplete cylindrical gears 91,92 and first cylindrical gears 11/ second cylindrical gearss 12 of the second gear shaft 9, its gear joint garden radius ratio is all 4:5; The numbers of teeth such as each incomplete cylindrical gears of the first gear shaft 8 has and the uniform two sections of continuous gear teeth of circumference, the central angle that every section of continuous gear teeth are corresponding is 90 °; Two incomplete cylindrical gearss 81,82 of the first gear shaft 8, its gear joint garden radius is equal, and from the rotational axis direction of the first gear shaft 8, the continuous gear teeth of two incomplete cylindrical gearss 81,82 stagger each other completely; The each incomplete cylindrical gears 91,92 of the second gear shaft 9 has one section of continuous gear teeth, and the central angle that these continuous gear teeth are corresponding is 180 °; Two incomplete cylindrical gearss 91,92 of the second gear shaft 9, its gear joint garden radius is equal, and from the axial direction of the second gear shaft 9, the continuous gear teeth of two incomplete cylindrical gearss 91,92 stagger each other completely.
Sometime, when the semi-minor axis conllinear of the major semi axis of the oval gear of power output gear axle 10 and the oval gear of oval gear axle 14 that is meshed with it, the major semi axis of the oval gear of oval gear axle 14 and the oval gear semi-minor axis conllinear of the second gear shaft 9 be meshed with it; Now, the incomplete cylindrical gears 92 of the second gear shaft 9 and the second cylindrical gears 12 are engaged to the length continuous engagement time of half continuously, the incomplete cylindrical gears 91 of the second gear shaft 9 and the first cylindrical gears 11 depart from disengaging length engagement time being engaged to half, the incomplete cylindrical gears 82 of the first gear shaft 8 and the second cylindrical gears 12 depart from disengaging length engagement time being engaged to half, and the incomplete cylindrical gears 81 of the first gear shaft 8 and the first cylindrical gears 11 are engaged to the length continuous engagement time of half continuously; Now, the first rotor 1 is in the transient speed minimum period, and the second rotor 3 is in transient speed peak, and the part symmetry plane of the first rotor 1 and the second rotor 3 is perpendicular to one another, and each volume of cylinder is equal.
Due to the effect of inertia of each moving element of motor and load, can think that the rotating speed n0 on power output gear axle 10 is permanent rotating speed, this permanent rotating speed n0 is respectively through two-way, one tunnel is the alternately engagement driving conversion of " power output gear axle 10-oval gear axle 14-second gear shaft 9-first cylindrical gears 11/ second cylindrical gears 12 " of two the oval gear groups including into series relationship, another road is the alternately engagement driving conversion of " power output gear axle 10-cylindrical gear shaft 13-first gear shaft 8-second cylindrical gears 12/ first cylindrical gears 11 " of constant ratio, finally convert the periodicity variable speed motion with fixed skew of the first rotor 1 and the second rotor 3 to.Make the volume periodicity increase and decrease successively of 4 cylinders thus, and be periodically in air-breathing, compression, acting, exhaust stroke successively, thus cylinder of internal-combustion engine produces circulation merit, and by power output gear axle 10 outwards outputting power.
According to oval gear design code, eccentricity is the oval gear group of 1/3rd, its instantaneous transmission ratio as shown in figure 22, abscissa in Figure 22 is the rotation angle of driving wheel, y coordinate is the instantaneous transmission ratio of the relative driving wheel of follower, the maximum value of its instantaneous transmission ratio is 2, minimum value is 0.5, this instantaneous transmission ratio consecutive variations more than single order can be led everywhere in theory, the present invention can be calculated thus and become two groups of oval gear group resultant gear ratios of series relationship as shown in figure 23, in Figure 23, abscissa is the rotation angle of power output gear axle 10, y coordinate is the instantaneous transmission ratio of the relative power output gear axle 10 of the second gear shaft 9, the maximum value of its instantaneous transmission ratio is 4, minimum value is 0.25, this instantaneous transmission ratio consecutive variations more than single order can be led everywhere in theory.According to two incomplete cylindrical gearss 91 on aforesaid second gear shaft 9,92 and the first gear joint garden radius ratio of cylindrical gears 11/ second cylindrical gears 12, and the cylindrical gears joint garden radius ratio in aforesaid power output gear axle 10 and cylindrical gear shaft 13, and two incomplete cylindrical gearss 81 on aforesaid first gear shaft 8,82 and the first gear joint garden radius ratio of cylindrical gears 11/ second cylindrical gears 12, the first cylindrical gears 11(or the first rotor 1 can be calculated) with the second cylindrical gears 12(or the second rotor 3) relative power output gear axle 10 instantaneous transmission ratio as shown in figure 24, the instantaneous transmission ratio maximum value that Figure 24 represents is 4*4/5=3.2, instantaneous transmission ratio minimum value is 0.25*4/5=0.2, if represent the instantaneous transmission ratio of the first rotor 1 in Figure 24 with thick dashed line, then heavy line just represents the instantaneous transmission ratio of the second rotor 3, heavy line in Figure 24 or thick dashed line, all show that the curve of variable ratio and a segment table show that more than the curve single order of fixed drive ratio can lead to be connected smoothly continuously and form by a segment table, namely the tie point of two sections of curves is the incomplete alternately contact points of incomplete cylindrical gears 91 on cylindrical gears 81 and the second gear shaft 9 on the first cylindrical gears 11 and the first gear shaft 8, or the second incomplete alternately contact points of incomplete cylindrical gears 92 on cylindrical gears 82 and the second gear shaft 9 on cylindrical gears 12 and the first gear shaft 8, the rotation angle that should replace the corresponding power output gear axle 10 of contact points is 0 ° and 180 ° of moment, power output gear axle 10 is rotated one week (360 °), the instantaneous transmission ratio change one-period of the first rotor 1 represented by thick dashed line and heavy line two curves respectively and the second rotor 3, and the phase difference both it is 0.5 instantaneous transmission ratio period of change.This shows, in the uniform rotation process of power output gear axle 10, the first rotor 1 and the second rotor 3 do the rotation of alternately acceleration and deceleration, the periodic increase and decrease of angle therefore between the first rotor 1 and the second rotor 3.
Instantaneous transmission ratio can be regarded as the derivative of the relative driving gear rotating speed of driven gear rotating speed, the some closed areas therefore by being surrounded by actual situation two curves in integral and calculating Figure 24, draws the variable angle amount maximum value between the first rotor 1 and the second rotor 3
=
-
=1O8 °, getting firing chamber of the present invention ideal theoretical compression ratio is 11:1, then can calculate the fan-shaped angle of each piston body
be 25.2 °, in the running of internal-combustion engine, between first piston body 102 and the second piston body 32, minimum angle is
=1O.8 °, maximum angle is
=
+
=118.8 °, and the fan-shaped square hole angle of porting 53 thus on desirable burning chamber shell 5
be 25.2 °, the spacing angle of the fan-shaped square hole of porting 53
it is 10.8 °.In internal combustion engine operation process, corresponding power output gear axle 10 rotates two weeks, the relative position change of the first rotor 1 and the second rotor 3 is as shown in Figure 12-Figure 20, in Figure 12-Figure 20, along with the corner of power output gear axle 10 changes, by burning chamber shell 5, the first rotor 1, cover plate 2, the volume periodically increase and decrease of four cylinders that the second rotor 3 is separated out jointly, power output gear axle 10 rotates two weeks, the first rotor 1 and the second rotor 3 respectively rotate one week, each volume of cylinder increase and decrease four times, and be in air-breathing successively, compression, acting, exhaust stroke, so, each cylinder completes a four strokes i.e. thermodynamic cycle, whole internal-combustion engine completes 16 strokes i.e. four thermodynamic cycles.
Heat to power output principle of the present invention is: the gas in each cylinder is by active force external output work on piston body, any moment, the piston body of gas in each cylinder to cylinder both sides is applied with equal gas pressure effect, therefore this cylinder both sides piston body respectively from this cylinder interior gas obtain equal and opposite in direction and the contrary moment loading in direction+
(+number this moment direction of expression is identical with piston body angular velocity direction) and-
(-number represent this moment direction contrary with piston body angular velocity direction), the effect axis of moment is the running shaft of piston body, each piston body under the moment loading obtained respectively with angular velocity
with
rotate, therefore each piston body from this cylinder interior gas obtain respectively power+
with-
, this power is through meshed transmission gear, and the power output gear axle 10 coalgebra superposition being finally all delivered to internal-combustion engine obtains the clean output work of this cylinder interior gas
, as can be seen here, each cylinder interior gas is gas load square suffered on the piston body of cylinder side by the net work that power output gear axle 10 externally exports
with the difference of cylinder both sides piston body angular velocity
product.
also can be understood as the angular velocity of the fan-shaped volume-variation of this cylinder interior gas, that is, because the first rotor 1 and the second rotor 3 exist the angular velocity difference of periodically alternately change, therefore volume of cylinder periodically increase and decrease, cylinder also just can periodically be in air-breathing, compression, acting, exhaust stroke, thus cylinder of internal-combustion engine produces circulation merit, and by power output gear axle 10 outwards outputting power.
For further comparative illustration volume of cylinder Variation Features of the present invention, by volume of cylinder change procedure normalized of the present invention, and compared with the volume of cylinder change procedure of the crankshaft connecting rod type internal-combustion engine after normalized.Normalized method is the method for a kind of nondimensionalization conventional in engineering, and the present invention adopts normalized object to be in order to the unified yardstick compared.The normalized method of the present invention is under the reasonable assumption condition of the permanent rotating speed of power output gear axle 10 of the present invention, by calculating transient change amount (the 0-1 numerical intervals of volume of cylinder of the present invention, when cylinder is in minimum volume state, volume-variation amount is 0, and it be volume-variation amount is 1 that cylinder is in maximum volume state) with the corresponding relation of corresponding time (0-1 numerical intervals).The instantaneous transmission ratio relation of the first rotor of the present invention 1 according to Figure 24 and the relative power output gear axle 10 of the second rotor 3, draw the volume of cylinder variable quantity (volume increment) of the present invention after normalized in time variation relation as shown in figure 25, corresponding number list is as shown in table 1.
Table 1: normalized combustion chamber volume variable quantity-time relationship numerical tables of the present invention
| Time t | Normalization volume-variation amount V |
| 0 | 0.00000 |
| 0.05 | 0.00013 |
| 0.1 | 0.00106 |
| 0.15 | 0.00376 |
| 0.2 | 0.00957 |
| 0.25 | 0.02060 |
| 0.3 | 0.04058 |
| 0.35 | 0.07681 |
| 0.4 | 0.14483 |
| 0.45 | 0.27677 |
| 0.5 | 0.49976 |
| 0.55 | 0.72278 |
| 0.6 | 0.85482 |
| 0.65 | 0.92296 |
| 0.7 | 0.95927 |
| 0.75 | 0.97932 |
| 0.8 | 0.99038 |
| 0.85 | 0.99621 |
| 0.9 | 0.99893 |
| 0.95 | 0.99987 |
| 1 | 1.00000 |
In Figure 25 and table 1, rising to the corresponding whole volume of 1(from 0 in time increases the time period), the instantaneous delta of volume of cylinder is increased to the corresponding volume increment of 1(from 0 and arrives from 0 maximum).
Contrast Figure 26 and the volume of cylinder increment variation relation in time obtained after the identical method for normalizing process of the crankshaft connecting rod type internal-combustion engine shown in table 2.
Table 2: the normalized combustion chamber volume variable quantity-time relationship numerical tables of crankshaft connecting rod type internal-combustion engine
| Time t | Normalization volume-variation amount V |
| 0 | 0.00000 |
| 0.05 | 0.00820 |
| 0.1 | 0.03245 |
| 0.15 | 0.07177 |
| 0.2 | 0.12456 |
| 0.25 | 0.18871 |
| 0.3 | 0.26168 |
| 0.35 | 0.34069 |
| 0.4 | 0.42286 |
| 0.45 | 0.50541 |
| 0.5 | 0.58579 |
| 0.55 | 0.66184 |
| 0.6 | 0.73188 |
| 0.65 | 0.79468 |
| 0.7 | 0.84946 |
| 0.75 | 0.89582 |
| 0.8 | 0.93358 |
| 0.85 | 0.96278 |
| 0.9 | 0.98351 |
| 0.95 | 0.99588 |
| 1 | 1.00000 |
Visible, volume of cylinder pace of change of the present invention all obviously reduces when cylinder instantaneous volumetric is minimum and maximum, and thus the high desirable constant volume cycle of the thermal efficiency is tended in thermodynamic cycle of the present invention more.From the multiple thermodynamic cycle indicator diagram (p-v figure) shown in Figure 27, the area that desirable constant volume cycle (representing by beading fine line I) surrounds on indicator diagram is maximum, represents the unit working medium under desirable constant volume cycle, produces circulation merit maximum; The area that crankshaft connecting rod type internal-combustion engine actual cycle (representing with thick dashed line III) surrounds on indicator diagram is minimum, represents the unit working medium under crankshaft connecting rod type internal-combustion engine actual cycle, produces circulation merit minimum; Actual cycle of the present invention (representing with heavy line II) although the area that surrounds on indicator diagram be less than desirable constant volume cycle surround area, but actual cycle of the present invention on indicator diagram surround area ratio crankshaft connecting rod type internal-combustion engine actual cycle on indicator diagram to surround area obviously much bigger, thus the high desirable constant volume cycle of the thermal efficiency is tended in thermodynamic cycle of the present invention more, Actual cycle work of the present invention obviously increases than crankshaft connecting rod type internal-combustion engine Actual cycle work, thus is conducive to the obvious reduction of engine consumption.
embodiment 2:in the embodiment of the present invention 1, described dish 4 can cancel the upper end plate 41 of network-like structure, retains the lower end plate 42 of dish 4, and the screw that the axis hole arranged in the middle of lower end plate 42 and card periphery are offered, and makes dish 4 only have individual layer card.That is: dish 4 can be individual layer card, and centre is provided with axis hole, and card periphery all offers screw.Flange plate, the dish 4 of burning chamber shell 5 are bolted to connection successively with the flange plate of gear-box 6.Other is identical with embodiment 1.
the present invention has following advantageous application effect:
1, significantly can reduce engine consumption, thus improve fuel economy, and improve engine exhaust emission.The present invention mainly realizes this effect by following technological approaches:
First, compared with the crankshaft connecting rod type combustion chambers of internal combustion engines volume-variation-time relationship characteristic shown in Figure 26 and table 2, Figure 25 and the combustion chamber volume change-time relationship characteristic of the present invention shown in table 1, show that volume of cylinder of the present invention changes when it is minimum or maximum very slow.When cylinder interior gas is in the compression stroke later stage, volume of cylinder pace of change increases the time in cylinder required for combustible oil gas mixture Thorough combustion by being conducive to slowly, thus the ignition advance angle of motor can be allowed greatly to reduce, substantially reduce the compression negative work of cylinder interior gas, add the circulation merit of motor; And when being in power stroke in cylinder and being initial, equally because volume of cylinder is slow increase from its minimum value, make combustible oil gas mixture burning in cylinder more abundant, fuel oil supply same with crankshaft connecting rod type internal-combustion engine just can produce higher inner pressure of air cylinder peak value, thus add the circulation merit of motor, and improve the toxic emission of motor.Thus the present invention can reduce engine consumption, thus improves fuel economy, and improves engine exhaust emission.
From the multiple thermodynamic cycle indicator diagram (p-v figure) shown in Figure 27, the area that desirable constant volume cycle (representing by beading fine line I) surrounds on indicator diagram is maximum, represent that the unit working medium generation circulation merit under desirable constant volume cycle is maximum, the area that crankshaft connecting rod type internal-combustion engine actual cycle (representing with thick dashed line III) surrounds on indicator diagram is minimum, represent that the unit working medium generation circulation merit under crankshaft connecting rod type internal-combustion engine actual cycle is minimum, actual cycle of the present invention (representing with heavy line II) although the area that surrounds on indicator diagram be less than desirable constant volume cycle surround area, but actual cycle of the present invention on indicator diagram surround area ratio crankshaft connecting rod type internal-combustion engine actual cycle on indicator diagram to surround area obviously much bigger, thus the high desirable constant volume cycle of the thermal efficiency is tended in thermodynamic cycle of the present invention more, Actual cycle work of the present invention obviously increases than crankshaft connecting rod type internal-combustion engine Actual cycle work, thus be conducive to the obvious reduction of engine consumption, improve fuel economy.
Relative four-stroke crankshaft connecting rod type internal-combustion engine, this factor can for the present invention bring about 40% circulation merit increasing amount.
Secondly, according to interrelated data, in crankshaft connecting rod type internal-combustion engine inner carrier reciprocatory movement, the frictional loss between piston and cylinder wall, consumes the 10%-20% of cycle of engine merit.In piston body rotation process of the present invention, the frictional loss of piston body and blazer housing etc. is very little, substantially negligible.Thus invention increases the clean output work of motor, obviously reduce engine consumption, improve fuel economy.
Relative four-stroke crankshaft connecting rod type internal-combustion engine, this factor can be the circulation merit loss amount of the present invention's minimizing about 15%.
Again, compared with triangle rotor type motor.Face contact is during relative movement between all parts that the present invention forms cylinder.Therefore the sealing of cylinder easily realizes, good sealing effect, and cylinder leakage tester loss when motor runs is little, thus can reduce engine consumption, improves fuel economy, improves engine exhaust emission.
Add up to above-mentioned every factor, oil consumption level of the present invention can be reduced to and be about 60% of four-stroke crankshaft connecting rod type internal-combustion engine.
2, the power to weight ratio of motor can significantly be improved.The present invention mainly realizes this effect by following technological approaches:
First, relative to crankshaft connecting rod type internal-combustion engine, the present invention is without the need to the throttle valve structure of complexity; Driving mechanism has also changed over the gear structure of compact structure by the crankshaft rod structure that the large weight of volume is large; Air cylinder structure is obvious compactness also.Under same displacement volume, the present invention can have obviously little many volume and weights, therefore can improve the power to weight ratio of motor.
Relative four-stroke crankshaft connecting rod type internal-combustion engine, this factor can for the present invention bring about 20% loss of weight amount.
Secondly, power output gear axle of the present invention rotates two weeks, four cylinders respectively complete the thermodynamic cycle once comprising air-breathing, compression, acting, exhaust four strokes, thermodynamic cycle quantity of the present invention is identical with the four-stroke crankshaft connecting rod type internal-combustion engine of cylinder number with same rotating speed, but consider the favorable factors such as the thermal efficiency of the present invention is high, cylinder scavenging efficiency is high, mechanical friction loss little output net power is large, therefore power stage of the present invention is than large with the four-stroke crankshaft connecting rod type internal-combustion engine of discharge capacity with rotating speed.
About cylinder scavenging efficiency of the present invention, compared with the crankshaft connecting rod type combustion chambers of internal combustion engines volume-variation-time relationship characteristic shown in Figure 26 and table 2, Figure 25 and the combustion chamber volume change-time relationship characteristic of the present invention shown in table 1, show that volume of cylinder of the present invention changes when it is minimum or maximum very slow.That is, when cylinder is in exhaust stroke at the end, now relief opening diminishes, and the present invention slowly volume of cylinder minimizing speed will be conducive to exhaust fully, and reduce exhaust process windage loss; When cylinder is in suction stroke at the end, now suction port diminishes, and the present invention slowly volume of cylinder gathers way and also will be conducive to sucking more fresh oil gas mixture, and reduces breathing process windage loss.This will be conducive to improving engine breathing efficiency, also to the raising gain to some extent of engine thermal cycle efficiency.
Relative four-stroke crankshaft connecting rod type internal-combustion engine, this factor can bring the power gain of about 1.65 times for the present invention.
Finally, compared with existing crankshaft connecting rod type internal-combustion engine, all driving components of the present invention are all axialy symmetric part, thus allow motor to have higher limit speed; From the combustion efficiency of motor, the combustion chamber volume change-time relationship characteristic of the present invention shown in Figure 25 (table 1) also still can keep higher combustion efficiency at high speed by contributing to motor.Therefore, the present invention has the good potentiality of high-power output under high rotating speed.When the present invention as aircraft power plant, ground racing car or other need the application of high power to weight ratio time, by improving the rotating speed of motor, significantly improve the power to weight ratio of motor.
Add up to above-mentioned every factor, 2.1 times that power to weight ratio of the present invention can be brought up to the four-stroke crankshaft connecting rod type internal-combustion engine being about same rotating speed.
3, engine structure is simple, and anufacturability is good.The present invention mainly realizes this effect by following technological approaches:
First, constituent elements of the present invention is few, does not have the complicated throttle valve structure and crankshaft rod structure etc. of crankshaft connecting rod type motor.
Secondly, manufacturing and designing of each constituent elements of the present invention all has ripe technical process, without the component that special fabrication processes requires, as oval gear transmission is widely used in textile manufacturing machine and farm machinery etc., spark plug oil sprayer technology and cylinder seal technology all can use for reference the mature technology of crankshaft connecting rod type internal-combustion engine, etc.
4, engine luggine and noise level low, smooth running, moving element is few, thus the motor working service life-span is long.The present invention mainly realizes this effect by following technological approaches:
First, compared with existing crankshaft connecting rod type internal-combustion engine, each moving element of the present invention is all axialy symmetric part, and the various vibration effectively avoiding moving element to cause due to mass unbalance and noise, engine running stationarity is good, and the working service life-span is long.
Secondly, as shown in figure 24, each movement transmission members of the present invention, its instantaneous transmission ratio consecutive variations more than single order can be led everywhere in theory, therefore between transmission part without rigid impulse, also without soft impulse; And the transmission process of each movement transmission members can mate well with the pressure change procedure of cylinder interior gas, thus moving element can be effectively avoided to impact the various vibration and noise caused due to transmission.Engine running stationarity is good, and the working service life-span is long.
Finally, constituent elements of the present invention is few, and moving element is few, and frictional loss is little, and do not have the complicated throttle valve structure and crankshaft rod structure etc. of crankshaft connecting rod type motor, therefore breakdown in the motor rate is low, and the working service life-span is long.
5, engine structure is compact.The present invention mainly realizes this effect by following technological approaches:
Relative to crankshaft connecting rod type internal-combustion engine, the present invention does not have complicated throttle valve structure, and driving mechanism has also changed over the gear structure of compact structure by the crankshaft rod structure that the large weight of volume is large, and air cylinder structure is obvious compactness also.Therefore, under same displacement volume, the present invention can have obviously much smaller volume and weight, compact structure on the whole, can be applicable to the application such as miniaturization ground traffic tools motor overall size being required to strict aircraft power plant and ground racing car, Future population dense city better.
6, engine power output torque is large.The present invention mainly realizes this effect by following technological approaches:
Power output gear axle of the present invention rotates two weeks, four cylinders respectively complete the thermodynamic cycle once comprising air-breathing, compression, acting, exhaust four strokes, thermodynamic cycle quantity is identical with the crankshaft connecting rod type internal-combustion engine of number of cylinders with same rotating speed, but considers the favorable factors such as the thermal efficiency of the present invention is high, cylinder power per liter is high, mechanical friction loss little output net power is large.Therefore Power output torque ratio of the present invention is bigger than normal with the crankshaft connecting rod type internal-combustion engine of discharge capacity with rotating speed.
Add up to above-mentioned every factor, 1.65 times that Power output moment of torsion of the present invention can be brought up to the four-stroke crankshaft connecting rod type internal-combustion engine being about same rotating speed.
7, the multiple design parameter adjustable of motor.The present invention mainly realizes this effect by following technological approaches:
Such as, the fan-shaped angle of inventive piston body is increased and decreased
, the ideal theoretical compression ratio of changeable motor; Change the eccentricity of each oval gear of the present invention, the maximum cylinder volume of motor can be changed, etc.
8, only need very little structural design adjustment, the present invention can change into high performance pump.The present invention mainly realizes this effect by following technological approaches:
For embodiments of the invention 1 and embodiment 2, only need the mounting hole place of the spark plug/oil sprayer 7 on burning chamber shell 5 that the another set of porting being symmetrical in existing porting is set, can the present invention be changed into pump; For embodiments of the invention 1 and embodiment 2, can also by the complete cylindrical gears of the cylindrical gears of cylindrical gear shaft 13 and the first gear shaft 8, its gear joint garden radius ratio changes into 1:1, two incomplete cylindrical gearss 81,82 of the first gear shaft 8, its continuous gear teeth all change the continuous gear teeth of one section of semi-circumference length into; Simultaneously by two of the second gear shaft 9 incomplete cylindrical gears 91,92 and first cylindrical gearss 11 and the second cylindrical gears 12, its gear joint garden radius ratio all changes into 8:5; , can the present invention be changed into pump.
The pump changed by embodiments of the invention 1 and embodiment 2, compact structure; Flow is large; Boosting capability is strong; Simultaneously, due to the cylinder body volume-variation-time relationship characteristic of the present invention shown in Figure 25 and table 1, make this pump can allow lower fluid inlet pressure when the fluid inlet opening and closing initial stage, circulation area was little, this pump effectively can also relax the cylinder interior pressure impact phenomenon under fluid output opening and closing initial stage small circulation area condition.Thus, the pump changed by the present invention, multiple performance index are all higher.
Claims (4)
1. double-piston rotary internal combustion engine, comprise the first rotor, cover plate, the second rotor, dish, burning chamber shell and gear-box, it is characterized in that: the first rotor is Y-shaped, be made up of rotating shaft dish, first piston body and the first turning axle, the center of rotating shaft dish one side is provided with the first turning axle, rotating shaft dish another side is provided with two first piston bodies around the first turning axle axisymmetrical, and the axle head of the first turning axle is provided with keyway, and the axle center of the first turning axle is provided with axis hole;
Cover plate is garden plate-like, and the centre of cover plate is provided with the boss of band central through bore, and the periphery of cover plate is provided with chimb; The bottom surface of cover plate is connected with first piston body end face;
Second rotor is T-shaped, is made up of the second turning axle and the second piston body, and one end of the second turning axle is symmetrically arranged with two the second piston bodies, and the termination of the other end of the second turning axle is provided with keyway, and first piston body is equal with the outer circumference diameter of the second piston body;
The Pan Zhou center of dish is provided with axis hole, and the two ends of dish axle are connected with end plate and lower end plate, and upper end plate periphery and lower end plate periphery are provided with screw; Second turning axle is threaded onto in the axis hole of the first turning axle, and the first turning axle and the second turning axle are all threaded onto in the axis hole at Pan Zhou center, is set with burning chamber shell outside first piston body and the second piston body;
Burning chamber shell is in falling peviform, periphery at the bottom of the room of burning chamber shell is provided with flange plate, flange plate is provided with screw, burning chamber shell periphery is provided with porting, on burning chamber shell, the offside of porting is provided with the pilot hole of spark plug/oil sprayer, and spark plug/oil sprayer is fixedly installed in pilot hole; The upper end plate of dish is adjacent with the rotating shaft dish of the first rotor, and the screw of the upper end plate of dish and the screw of burning chamber shell flange plate are bolted;
Gear-box is peviform, and be provided with axis hole in the middle of bottom it, the periphery of gear-box upper end case mouth is provided with flange plate, and flange plate is provided with screw and is bolted with the valve snail hole, lower end of dish; Bottom gear-box, axis hole is provided with power output gear axle, the both sides of power output gear axle are provided with oval gear axle and cylindrical gear shaft, power output gear axle is provided with an oval gear and a cylindrical gears, oval gear on power output gear axle engages with the oval gear on oval gear axle, and the cylindrical gears on power output gear axle engages with the cylindrical gears in cylindrical gear shaft; First gear shaft is provided with a complete cylindrical gears and two incomplete cylindrical gearss, the second gear shaft is provided with an oval gear and two incomplete cylindrical gearss; Cylindrical gears in cylindrical gear shaft engages with the complete cylindrical gears on the first gear shaft; Oval gear on oval gear axle engages with the oval gear on the second gear shaft; The shaft with keyway end of the second turning axle and the first turning axle is all positioned at gear-box, the axle head of the first turning axle is equipped with the first cylindrical gears, the axle head of the second turning axle is equipped with the second cylindrical gears, first cylindrical gears alternately engages with the incomplete cylindrical gears of the first gear shaft and the incomplete cylindrical gears of the second gear shaft, and the second cylindrical gears alternately engages with the incomplete cylindrical gears of the first gear shaft and the incomplete cylindrical gears of the second gear shaft.
2. double-piston rotary internal combustion engine according to claim 1, is characterized in that, the gear teeth of two incomplete cylindrical gearss of described first gear shaft are axially complementary.
3. double-piston rotary internal combustion engine according to claim 1, is characterized in that, the gear teeth of two incomplete cylindrical gearss of described second gear shaft are axially complementary.
4. double-piston rotary internal combustion engine according to claim 1, is characterized in that, described dish can be individual layer card, and be provided with axis hole in the middle of card, card periphery offers screw.
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2313052Y (en) * | 1997-05-08 | 1999-04-07 | 吴素良 | Dual-rotating non-linear drive piston-type internal combustion engine |
| US20050098143A1 (en) * | 2002-05-17 | 2005-05-12 | Schwam Paul A. | Two-cycle engine for counter-rotation especially for aviation applications |
| CN101196124A (en) * | 2007-08-08 | 2008-06-11 | 邵文英 | Vane type cavity capability changing device, vane type gas engine and vane compressor |
| US20080202466A1 (en) * | 2007-02-28 | 2008-08-28 | Richard Colman Webster | Rotary internal combustion engine and rotary compressor |
| CN101592072A (en) * | 2008-05-26 | 2009-12-02 | 张振明 | Double-rotor controlled alternate-running engine |
| CN104153881A (en) * | 2014-08-02 | 2014-11-19 | 熊薇 | Differential drive mechanism of internal combustion engine |
| CN104533608A (en) * | 2014-12-24 | 2015-04-22 | 唐仁杰 | Double-piston-rotor internal combustion engine |
-
2015
- 2015-01-22 CN CN201510029762.9A patent/CN104727936B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2313052Y (en) * | 1997-05-08 | 1999-04-07 | 吴素良 | Dual-rotating non-linear drive piston-type internal combustion engine |
| US20050098143A1 (en) * | 2002-05-17 | 2005-05-12 | Schwam Paul A. | Two-cycle engine for counter-rotation especially for aviation applications |
| US20080202466A1 (en) * | 2007-02-28 | 2008-08-28 | Richard Colman Webster | Rotary internal combustion engine and rotary compressor |
| CN101196124A (en) * | 2007-08-08 | 2008-06-11 | 邵文英 | Vane type cavity capability changing device, vane type gas engine and vane compressor |
| CN101592072A (en) * | 2008-05-26 | 2009-12-02 | 张振明 | Double-rotor controlled alternate-running engine |
| CN104153881A (en) * | 2014-08-02 | 2014-11-19 | 熊薇 | Differential drive mechanism of internal combustion engine |
| CN104533608A (en) * | 2014-12-24 | 2015-04-22 | 唐仁杰 | Double-piston-rotor internal combustion engine |
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Effective date of registration: 20191209 Address after: 314409 Xucun township government, Haining City, Jiaxing City, Zhejiang Province Patentee after: Haining Home Textile Industrial Base Investment Development Co.,Ltd. Address before: 330024 Jiangxi province Qingyunpu District of Nanchang City Road Bridge Hongdu a District 38 building 902 room Patentee before: Tang Renjie |
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Application publication date: 20150624 Assignee: Zhejiang Rifu Technology Co.,Ltd. Assignor: Haining Home Textile Industrial Base Investment Development Co.,Ltd. Contract record no.: X2022330000248 Denomination of invention: Double piston rotor internal combustion engine Granted publication date: 20170308 License type: Common License Record date: 20220629 |
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Denomination of invention: Double piston rotary internal combustion engine Effective date of registration: 20231227 Granted publication date: 20170308 Pledgee: Bank of Huzhou Co.,Ltd. Pledgor: Haining Home Textile Industrial Base Investment Development Co.,Ltd. Registration number: Y2023980073645 |
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