CN104533608A

CN104533608A - Double-piston-rotor internal combustion engine

Info

Publication number: CN104533608A
Application number: CN201410813152.3A
Authority: CN
Inventors: 唐仁杰; 熊薇
Original assignee: 唐仁杰
Current assignee: CHUANGLI ELECTRIC (CHUZHOU) Co.,Ltd.
Priority date: 2014-12-24
Filing date: 2014-12-24
Publication date: 2015-04-22
Anticipated expiration: 2034-12-24
Also published as: CN104533608B

Abstract

The invention discloses a double-piston-rotor internal combustion engine. A first rotor comprises a rotating shaft disc, two first piston bodies are arranged at one end of the rotating shaft disc, a first rotating shaft provided with a first egg-shaped gear is installed at the other end of the rotating shaft disc, and the bottom face of a cover plate is connected with the end faces of the first piston bodies. A second rotor comprises a second rotating shaft, two second piston bodies are arranged at one end of the second rotating shaft, a second egg-shaped gear is installed at the other end of the second rotating shaft, the second rotating shaft is installed in a shaft hole of the first rotating shaft in a penetrating mode, and the second rotating shaft and the first rotating shaft are jointly installed in a shaft hole of a disc-shaped piece in a penetrating mode. An upper end disc and a lower end disc of the disc-shaped piece are connected with a combustor shell and a flange of a gearbox through bolts respectively. A power output gear shaft is installed in a shaft hole in the bottom of the gearbox. Upper egg-shaped gears of two double-egg-shaped gear shafts are meshed with the first egg-shaped gear and the second egg-shaped gear respectively, and lower egg-shaped gears of the two double-egg-shaped gear shafts are meshed with two egg-shaped gears on the power output gear shaft respectively. The double-piston-rotor internal combustion engine is low in oil consumption, high in power-to-weight ratio, large in output torque, low in vibration, simple and compact in structure, easy to design and good in manufacturability.

Description

Double-piston rotor internal-combustion engine

Technical field

The present invention relates to technical field of internal combustion engines, particularly rotary piston type 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, by the gearing of crankshaft-and-connecting-rod, the straight reciprocating motion of piston is converted to the unidirectional rotary motion of internal combustion engine moving power output shaft.

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 adopts the power take-off mechanism of gear-driven form, and driving mechanism axial symmetry is better, and Engine Limit rotating speed is high, and therefore power to weight ratio 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 the family-sized car field that market is huge, by the restriction of battery durable and 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, needs internal-combustion engine to contribute share with the green environment construction that the form of oil electricity mixing is future city;

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 in emerging General Aviation market segment and model plane industries etc. such as personal aircrafts, internal-combustion engine will 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 type 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 type internal combustion engine " class.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 type 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 rotor internal-combustion engine, the excellent design theory of " rotary-piston " has been used for reference in this invention, 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.

First technological scheme of the present invention: double-piston rotor internal-combustion engine, it is characterized in that: the first rotor is Y-shaped structure, comprise rotating shaft dish, one end of rotating shaft dish is two first piston bodies with the first turning axle axisymmetrical, the other end is provided with the first turning axle, the termination of the first turning axle is provided with keyway, and the first turning axle axle center 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 end face;

Second rotor is T-shaped structure, and is provided with the second turning axle, and one end of the second turning axle is provided with and two of axisymmetrical the second piston bodies, and the other end of the second turning axle offers 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 is latticed, 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 room is provided with flange plate, and flange plate is provided with screw, and burning chamber shell periphery is provided with porting, the offside of burning chamber shell 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; The axis hole axis both sides of gear-box are provided with two oval gear axle, and two oval gear axle is equipped with oval gear and lower oval gear; Second turning axle and the first turning axle are threaded onto dish axis hole, and axle head is positioned at gear-box, first turning axle axle head is equipped with the first oval gear, second turning axle axle head is equipped with the second oval gear, first oval gear and the second oval gear engage with the upper end oval gear of two oval gear axles of both sides in gear-box respectively, bottom gear-box, axis hole is provided with power output gear axle, power output gear axle is provided with two staggered oval gears side by side up and down, and engages with the lower oval gear of two oval gear axles of both sides in gear-box respectively.

Described dish can be individual layer card, and be provided with axis hole in the middle of card, card periphery offers screw.

In the present invention, burning chamber shell, the first rotor, cover plate, the second rotor are jointly separated out four and are isolated from each other and the cylinder of variable volume, in internal combustion engine operation process, corresponding to the uniform rotation of power output gear axle, the first rotor and bitrochanteric rotating speed and relative angular position cyclically-varying, these four cylinders also periodically increase and decrease volume successively, 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.

Second technological scheme of the present invention: double-piston rotor internal-combustion engine, is characterized in that: burning chamber shell a is in falling peviform, and basin mouth periphery is provided with flange plate, is provided with the first rotor a and the second rotor a in burning chamber shell a; The first rotor a is Y shape part, and its one end is two first piston body a of the first turning axle a axisymmetrical, and the other end is provided with keyway, and the first turning axle a axle center of the first rotor a is provided with manhole; Second rotor a is T-piece, and its one end is two the second piston body a of the second turning axle a axisymmetrical, and the other end is provided with keyway; Second turning axle a is set in the manhole of the first rotor a;

Dish a comprises upper disk surface and lower card, described upper disk surface is provided with through hole with the center of lower card and is connected by axle sleeve, the upper and lower card of dish a peripherally all offers screw, the keyway end of the first rotor a and the second rotor a is threaded onto in the axle sleeve of dish a, the upper disk surface of dish a is adjacent with the first rotor a, and the upper disk surface screw of dish a is fixedly connected with burning chamber shell a flange plate screw hole by bolt; The lower card screw of dish a is fixedly connected with gear-box a flange plate screw hole by bolt;

Gear-box a is peviform, and be provided with axis hole in the middle of bottom it, the periphery of gear-box a upper end case mouth is provided with flange plate, and flange plate is provided with screw and is connected with the lower card screw of dish a by bolt, axis hole in the middle of bottom gear-box a is provided with power output gear axle a, first, second gear shaft symmetry is installed on the axis both sides of power output gear axle a, the upper end of the first gear shaft is provided with cylindrical gears, the upper end of the second gear shaft is provided with cylindrical gears, the lower end of the first gear shaft is provided with oval gear, the lower end of the second gear shaft is provided with oval gear, two oval gear axles are separately installed with oval gear, power output gear axle a is provided with oval gear, the keyway end of the first turning axle a and the second turning axle a is separately installed with cylindrical gears and correspondence and first, the cylindrical gears of the upper end of the second gear shaft engages respectively, first, the oval gear of the lower end of the second gear shaft engages with the oval gear on two oval gear axles respectively, oval gear on two oval gear axles engages with the oval gear on power output gear axle a simultaneously.

Described dish a can be individual layer card, and be provided with axis hole in the middle of card, card periphery offers screw.

In the present invention, burning chamber shell a, the first rotor a, the second rotor a, dish a are jointly separated out four and are isolated from each other and the cylinder of variable volume, in internal combustion engine operation process, corresponding to the uniform rotation of power output gear axle a, the rotating speed of the first rotor a and the second rotor a and relative angular position cyclically-varying, these four cylinders also periodically increase and decrease volume successively, and be periodically in air-breathing, compression, acting, exhaust stroke successively, thus cylinder of internal-combustion engine produces circulation merit, and by the outside outputting power of power output gear axle a.

Comprehensively above-mentioned two technological schemes, observe from power output gear shaft to the drive connection of rotor, uniform rotation campaign on power output gear axle is respectively through two-way, every road includes into the transmission conversion of two oval gear groups of series relationship, converts 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 be jointly separated out by the multiple engine components comprising the first rotor and the second rotor thus, and be periodically in air-breathing, compression, acting, exhaust stroke successively, thus realize heat to power output and the Power output of internal-combustion engine.

Double-piston rotor internal-combustion engine provided by the present invention, has following beneficial effect: significantly can reduce engine consumption, improves fuel economy, improves engine exhaust emission; Significantly can improve the power to weight ratio of motor; Structure is simple, and anufacturability is good; Vibration and noise level low, smooth running, moving element is few, and the working service life-span is long; Compact structure, Power output moment of torsion is large; The multiple design parameter of motor is adjustable, and only need very little structural design adjustment, the present invention can change into high performance pump.

Accompanying drawing explanation

Fig. 1 is the perspective view of the present invention first technological scheme.

Fig. 2 is the perspective view of the first rotor in the present invention first technological scheme.

Fig. 3 is the perspective view of the present invention first technological scheme cover plate.

Fig. 4 is the perspective view of the first rotor and cover plate combination in the present invention first technological scheme.

Fig. 5 is bitrochanteric perspective view in the present invention first technological scheme.

Fig. 6 is the perspective view of dish in the present invention first technological scheme.

Fig. 7 is the plan view of burning chamber shell in the present invention first technological scheme.

Fig. 8 be in Fig. 7 A-A to sectional structure schematic diagram.

Fig. 9 is the perspective view of burning chamber shell in the present invention first technological scheme.

Figure 10 is the perspective view of oval gear in the present invention first technological scheme.

Figure 11 is the perspective view of two oval gear axle in the present invention first technological scheme.

Figure 12 is A direction view in Figure 11.

Figure 13 is the perspective view of the present invention first technological scheme medium power output gear shaft.

Figure 14 is the perspective view of the present invention first technological scheme middle gear tank shell.

Figure 15 is the perspective view of the present invention second technological scheme.

Figure 16 is the perspective view of the first rotor a in the present invention second technological scheme.

Figure 17 is the perspective view of the second rotor a in the present invention second technological scheme.

Figure 18 is the perspective view of dish a in the present invention second technological scheme.

Figure 19 is the perspective view of burning chamber shell a in the present invention second technological scheme.

Figure 20 is rotor motion and volume of cylinder change schematic diagram (0 ° of moment of power output gear Shaft angle) of the present invention first technological scheme.

Figure 21 is rotor motion and volume of cylinder change schematic diagram (45 ° of moment of power output gear Shaft angle) of the present invention first technological scheme.

Figure 22 is rotor motion and volume of cylinder change schematic diagram (90 ° of moment of power output gear Shaft angle) of the present invention first technological scheme.

Figure 23 is rotor motion and volume of cylinder change schematic diagram (135 ° of moment of power output gear Shaft angle) of the present invention first technological scheme.

Figure 24 is rotor motion and volume of cylinder change schematic diagram (180 ° of moment of power output gear Shaft angle) of the present invention first technological scheme.

Figure 25 is rotor motion and volume of cylinder change schematic diagram (225 ° of moment of power output gear Shaft angle) of the present invention first technological scheme.

Figure 26 is rotor motion and volume of cylinder change schematic diagram (270 ° of moment of power output gear Shaft angle) of the present invention first technological scheme.

Figure 27 is rotor motion and volume of cylinder change schematic diagram (315 ° of moment of power output gear Shaft angle) of the present invention first technological scheme.

Figure 28 is rotor motion and volume of cylinder change schematic diagram (360 ° of moment of power output gear Shaft angle) of the present invention first technological scheme.

Figure 29 is that the cylinder of the present invention first technological scheme is maximum with minimum volume view.

Figure 30 is the instantaneous transmission ratio schematic diagram of an oval gear group engagement driving.

Figure 31 is two oval gear group resultant gear ratio schematic diagram that the present invention becomes series relationship.

Figure 32 is the first rotor of the present invention and the second rotor relative power output gear axle fixed skew instantaneous transmission ratio schematic diagram.

Figure 33 is the normalized combustion chamber volume variable quantity-time curve of the present invention.

Figure 34 is the normalized combustion chamber volume variable quantity-time curve of crankshaft connecting rod type internal-combustion engine.

Figure 35 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).

In figure: 1, the first rotor, 11, rotating shaft dish, 12, first piston body, 13, first turning axle, 2, cover plate, 21, boss, 22, chimb, 3, second rotor, 31, second turning axle, 32, second piston body, 4, dish, 41, upper end plate, 42, lower end plate, 5, burning chamber shell, 51, room is pushed up, 52, at the bottom of room, 53, porting, 54, pilot hole, 6, gear box casing, 7, first oval gear, 8, second oval gear, 9, two oval gear axle, 91, upper oval gear, 92, lower oval gear, 10, power output gear axle, 100, spark plug/oil sprayer,

1 ', the first rotor a, 12 ', first piston body a, 13 ', first turning axle a, the 2 ', second rotor a, the 21 ', second turning axle a, 22 ', second piston body a, 4 ', dish a, 5 ', burning chamber shell a, 53 ', porting a, 6 ', gear box casing a, 10 ', power output gear axle a;

101,102,103,104, cylindrical gears;

201,202,203,204, oval gear;

301, the first gear shaft, the 302, second gear shaft, 303, oval gear axle.

Embodiment

Below in conjunction with drawings and Examples, the present invention is further illustrated.

First technological scheme of the present invention: see Fig. 1 to Figure 14, and Figure 20 to Figure 29, double-piston rotor internal-combustion engine, it is characterized in that: the first rotor 1 is Y-shaped structure, comprise rotating shaft dish 11, one end of rotating shaft dish 11 is two first piston bodies 12 with the first turning axle 13 axisymmetrical, and the other end is provided with the first turning axle 13, the termination of the first turning axle 13 is provided with keyway, and the first turning axle 13 axle center is provided with axis hole;

Cover plate 2 is garden plate-like, and the centre of cover plate 2 is provided with the boss 21 of band central through bore, and the periphery of cover plate 2 is provided with chimb 22; The bottom surface of cover plate 2 is connected with first piston 12 end face;

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 with the other end of two of axisymmetrical the second piston body 32, second turning axlees 31, and first piston body 12 is equal with the outer circumference diameter of the second piston body 32;

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 in latticed, and upper end plate 41 periphery and lower end plate 42 periphery are provided with screw; Second turning axle 31 is threaded onto in the axis hole of the first turning axle 13, and the first turning axle 13 and the second turning axle 31 are all threaded onto in the axis hole at Pan Zhou 43 center, are set with burning chamber shell 5 outside first piston body 12 and the second piston body 32;

Burning chamber shell 5 is in falling peviform, 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, the offside of burning chamber shell 5 porting 53 is provided with the pilot hole 54 of spark plug/oil sprayer 100, and spark plug/oil sprayer 100 is fixedly installed in pilot hole 54; The upper end plate 41 of dish 4 is adjacent with the rotating shaft dish 11 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, and be provided with axis hole in the middle of bottom it, 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 axis hole axis both sides of gear-box 6 are provided with two oval gear axle 9, and two oval gear axle 9 is equipped with oval gear 91 and lower oval gear 92, second turning axle 31 and the first turning axle 13 are threaded onto dish 4 axis hole, and axle head is positioned at gear-box 6, first turning axle 13 axle head is equipped with the first oval gear 7, second turning axle 31 axle head is equipped with the second oval gear 8, first oval gear 7 and the second oval gear 8 engage with the upper end oval gear 91 of two oval gear axles 9 of both sides in gear-box 6 respectively, bottom gear-box 6, axis hole is provided with power output gear axle 10, power output gear axle 10 is provided with two staggered oval gears side by side up and down, and engage with the lower oval gear 92 of two oval gear axles 9 of both sides in gear-box 6 respectively.

Described dish 4 can be individual layer card, and be provided with axis hole in the middle of card, card periphery offers screw.

Burning chamber shell 5, the first rotor 1, cover plate 2, second rotor 3 are jointly separated out four and are isolated from each other and the cylinder of variable volume, in internal combustion engine operation process, corresponding to the uniform rotation of power output gear axle 10, the rotating speed of the first rotor 1 and the second rotor 3 and relative angular position cyclically-varying, these four cylinders also periodically increase and decrease volume successively, 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.

Second technological scheme of the present invention: see Figure 15 to Figure 19, double-piston rotor internal-combustion engine, it is characterized in that: burning chamber shell a5 ' is in falling peviform, and basin mouth periphery is provided with flange plate, is provided with the first rotor a1 ' and the second rotor a2 ' in burning chamber shell a5 '; The first rotor a1 ' is Y shape part, and its one end is two first piston body a12 ' of the first turning axle a13 ' axisymmetrical, and the other end is provided with keyway, and the first turning axle a13 ' axle center of the first rotor a1 ' is provided with manhole; Second rotor a2 ' is T-piece, and its one end is two the second piston body a22 ' of the second turning axle a21 ' axisymmetrical, and the other end is provided with keyway; Second turning axle a21 ' is set in the manhole of the first rotor a1 ';

The center of dish a4 ' offers manhole, the keyway end of the first rotor a1 ' and the second rotor a2 ' is threaded onto in the manhole of dish a4 ', the upper and lower card of dish a4 ' peripherally all offers screw, the upper disk surface of dish a4 ' is adjacent with the first rotor a1 ', and the upper disk surface screw of dish a4 ' is fixedly connected with by the flange plate screw hole of bolt with burning chamber shell a5 '; The lower card screw of dish a4 ' is fixedly connected with gear-box a6 ' flange plate screw hole by bolt;

Gear-box a6 ' is in peviform, and be provided with axis hole in the middle of bottom it, the periphery of gear-box a6 ' upper end case mouth is provided with flange plate, and flange plate is provided with screw and is connected with the lower card screw of dish a4 ' by bolt, axis hole in the middle of gear-box a6 ' bottom is provided with power output gear axle a10 ', first gear shaft 301, second gear shaft 302 symmetry is installed on the axis both sides of power output gear axle a10 ', the upper end of the first gear shaft 301 is provided with cylindrical gears 102, the upper end of the second gear shaft 302 is provided with cylindrical gears 104, the lower end of the first gear shaft 301 is provided with oval gear 201, the lower end of the second gear shaft 302 is provided with oval gear 204, two oval gear axles 303 are separately installed with oval gear 202, power output gear axle a10 ' is provided with oval gear 203, the keyway end of the first turning axle a13 ' and the second turning axle a21 ' is separately installed with cylindrical gears 101, 103 and respectively corresponding to first, second gear shaft 301, the cylindrical gears 102 of the upper end of 302, 104 engagements, first, second gear shaft 301, the oval gear 201 of the lower end of 302, 204 engage respectively with the oval gear 202 on two oval gear axles 303, oval gear 202 on two oval gear axles 303 engages with the oval gear 203 on power output gear axle a10 ' simultaneously.

Described dish a4 ' can be individual layer card, and be provided with axis hole in the middle of card, card periphery all offers screw.

Burning chamber shell a5 ', the first rotor a1 ', second rotor a2 ', dish a4 ' is jointly separated out four and is isolated from each other and the cylinder of variable volume, in internal combustion engine operation process, corresponding to the uniform rotation of power output gear axle a10 ', the rotating speed of the first rotor a1 ' and the second rotor a2 ' and relative angular position cyclically-varying, these four cylinders also periodically increase and decrease volume successively, and be periodically in air-breathing successively, compression, acting, exhaust stroke, thus cylinder of internal-combustion engine produces circulation merit, and by power output gear axle a10 ' outwards outputting power.

embodiment 1:first technological scheme of the present invention, double-piston rotor internal-combustion engine, comprises combustion system, transmission system etc., see Fig. 1 to Figure 14, and Figure 20 to Figure 29.

The first rotor 1 is Y shape part, comprise rotating shaft dish 11, one end of rotating shaft dish 11 is two first piston bodies 12 with the first turning axle 13 axisymmetrical, the other end is provided with the first turning axle 13, the termination of the first turning axle 13 is provided with keyway, first turning axle 13 axle center 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 12, between the first rotor 1 and cover plate 2, use several bolts passing first piston body 12 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 12 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 13 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 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 13, then be threaded onto together in dish axle 43 central shaft hole.Burning chamber shell 5 is set with outside first piston body 12 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, 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 the offside of burning chamber shell 5 porting 53 is provided with the pilot hole 54 of spark plug/oil sprayer 100, and spark plug/oil sprayer 100 is fixedly installed in pilot hole 54.The upper end plate 41 of dish 4 is adjacent with the rotating shaft dish 11 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, be provided with axis hole in the middle of bottom it, the power output gear axle 10 of internal-combustion engine passes from this hole, with outside outputting power, 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.Power output gear axle 10 is provided with two staggered oval gears side by side up and down, and engages with the lower oval gear 92 of two oval gear axles 9 of both sides in gear-box 6 respectively.In the space surrounded by gear-box 6 and dish 4, first oval gear 7 is fixed on the keyway arrangements end of the first rotor 1 by key Placement, second oval gear 8 is fixed on the keyway arrangements end of the second rotor 3 by key Placement, two oval gear axle 9 is equipped with oval gear 91 and lower oval gear 92, two oval gear axle has 2, the upper oval gear 91 of one of them two oval gear axle 9 and the first oval gear 7 engagement driving, an oval gear engagement driving of lower oval gear 92 and power output gear axle 10, the upper oval gear 91 of another pair of oval gear axle 9 and the second oval gear 8 engagement driving, the lower oval gear 92 of two two oval gear axles 9 respectively with the oval gear engagement driving of two on power output gear axle 10.

Two oval gears on first oval gear 7, second oval gear 8, upper oval gear 91 and lower oval gear 92 and power output gear axle 10, its eccentricity is , its major semi axis size is equal to each other, the upper oval gear 91 of two oval gear axle 9 and lower oval gear 92, its major semi axis direction spatial vertical each other, two oval gears on power output gear axle 10, its major semi axis direction also spatial vertical each other, sometime, when the first oval gear 7 major semi axis and be meshed with it upper oval gear 91 semi-minor axis conllinear time, lower oval gear 92 major semi axis of this pair of oval gear axle 9 and the oval gear semi-minor axis conllinear of power output gear axle 10 be meshed with it, now, the semi-minor axis of the second oval gear 8 and the upper oval gear 91 major semi axis conllinear of two oval gear axles 9 be meshed with it, now, the first rotor 1 is in transient speed minimum point, 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, 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 by a road " two oval gear axle 9-first oval gear 7 of power output gear axle 10-" and another road " two oval gear axle 9-second oval gear 8 of power output gear axle 10-", every road all includes into two groups of oval gear drive connections of series relationship, and the speed change of corresponding first oval gear 7 that is the first rotor 1 and the second oval gear 8 that is the second rotor 3 is rotated respectively.According to oval gear design code, eccentricity is oval gear group, its instantaneous transmission ratio as shown in figure 30, abscissa in Figure 30 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, instantaneous transmission ratio consecutive variations more than single order can be led everywhere in theory, then can calculate the technical program and become two groups of oval gear group resultant gear ratios of series relationship as shown in figure 31, in Figure 31, 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 first rotor 1 or the second rotor 3, the maximum value of its instantaneous transmission ratio is 4, minimum value is 0.25, instantaneous transmission ratio consecutive variations more than single order can be led everywhere in theory.According to aforesaid first oval gear 7, second oval gear 8, two oval gear axle 9, and each oval gear relative position relation of power output gear axle 10, rotating speed n0 on known corresponding power output gear axle 10, the instantaneous transmission ratio of the first rotor 1 and the second rotor 3 is transient speed all cyclically-varying and fixing phase differences of difference one in other words, as shown in figure 32, if represent the instantaneous transmission ratio of the first rotor 1 in Figure 32 with heavy line, then thick dashed line just represents the instantaneous transmission ratio of the second rotor 3, power output gear axle 10 is rotated one week (360 degree), the first rotor 1 represented by two curves respectively and the instantaneous transmission ratio of the second rotor 3 change two cycles, 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, therefore the periodic increase and decrease of angle 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, therefore the some closed areas by being surrounded by actual situation two curves in integral and calculating Figure 32, draw the variable angle amount maximum value between the first rotor 1 and the second rotor 3 = - =124 degree (about round numbers), 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 15.6 degree, in the running of internal-combustion engine, between first piston body 12 and the second piston body 32, minimum angle is =12.4 degree, maximum angle is = + =136.4 degree, and the fan-shaped square hole angle of porting 53 thus on desirable burning chamber shell 5 be 15.6 degree, the spacing angle of the fan-shaped square hole of porting 53 it is 12.4 degree.In internal combustion engine operation process, corresponding power output gear axle 10 rotates 1 week, the relative position change of the first rotor 1 and the second rotor 3 is as shown in Figure 20-Figure 28, in Figure 20-Figure 28, 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 1 week, the first rotor 1 and the second rotor 3 also rotate one week, each volume of cylinder increase and decrease secondary, 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.

The heat to power output principle of the present invention first technological scheme 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 angular velocity difference, therefore cylinder interior gas externally exports net work by piston body and power output gear axle 10, because the angular velocity difference of the first rotor 1 and the second rotor 3 periodically alternately changes, therefore volume of cylinder periodically increase and decrease, cylinder also just can periodically be in air-breathing, compression, acting, exhaust stroke.

For further illustrating the volume of cylinder Variation Features of the present invention first technological scheme, by the volume of cylinder change procedure normalized of this technological scheme, 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 at combustion engine powered output gear shaft 10(or I. C. engine crankshaft) under the reasonable assumption condition of permanent rotating speed, by calculating transient change amount (the 0-1 numerical intervals of two kinds of cylinder of internal-combustion engine volumes, 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 first rotor 1 according to Figure 32 and the second rotor 3 relative power output gear axle 10 instantaneous transmission ratio relation, draw the present invention first technological scheme volume of cylinder variable quantity (volume increment) after normalization reprocessing in time variation relation as shown in figure 33, corresponding number list is as shown in table 1.

Table 1: normalized combustion chamber volume variable quantity-time relationship numerical tables

Time t	Normalization volume-variation amount V
		0	0.00000
0.05	0.00248
		0.1	0.00997
0.15	0.02317
		0.2	0.04344
0.25	0.07296
		0.3	0.11519
0.35	0.17517
		0.4	0.25904
0.45	0.37057
		0.5	0.50282
0.55	0.63453
		0.6	0.74489
0.65	0.82762
		0.7	0.88675
0.75	0.92839
		0.8	0.95750
0.85	0.97746
		0.9	0.99042
0.95	0.99771
		1	1.00000

In Figure 33 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).

The normalization reprocessing volume of cylinder increment variation relation in time of the crankshaft connecting rod type internal-combustion engine of contrast shown in Figure 34 and 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, the volume of cylinder pace of change of the present invention first technological scheme 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 35, 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.

embodiment 3:second technological scheme of the present invention, double-piston rotor internal-combustion engine, comprises combustion system, transmission system etc., see Figure 15 to Figure 19.

The first rotor a1 ' is Y shape part, and its one end is for being symmetrical in two first piston body a12 ' of the first turning axle a13 ' axis, and the other end is provided with keyway, and the first turning axle a13 ' axle center of the first rotor a1 ' is provided with manhole.Second rotor a2 ' is T-piece, and its one end is two the second piston body a22 ' of the second turning axle a21 ' axisymmetrical, and the other end is provided with keyway; Second turning axle a21 ' is set in the manhole of the first rotor a1 '.The fan angle of first piston body a12 ' and the second piston body a22 ' all equal with outer circumference diameter.The center of dish a4 ' offers manhole, the keyway end of the first rotor a1 ' and the second rotor a2 ' is threaded onto in the manhole of dish a4 ', the upper and lower card of dish a4 ' peripherally all offers screw, the upper disk surface of dish a4 ' is adjacent with the first rotor a1 ', and the upper disk surface screw of dish a4 ' is fixedly connected with by the flange plate screw hole of bolt with burning chamber shell a5 '; The lower card screw of dish a4 ' is fixedly connected with gear-box a6 ' flange plate screw hole by bolt.Burning chamber shell a5 ' is in falling peviform, and basin mouth periphery is provided with flange plate, and side opening is provided with porting a53 ', and side offers pilot hole relative to porting a53 ' place, and spark plug/oil sprayer is mounted with at this pilot hole place.Burning chamber shell a5 ', the first rotor a1 ', the second rotor a2 ', dish a4 ' are jointly separated out four and are isolated from each other and four of variable volume cylinders, in internal combustion engine operation process, along with rotating speed and the relative angular position change of the first rotor a1 ' and the second rotor a2 ', these four cylinders periodically increase and decrease volume successively, and be periodically in air-breathing, compression, acting, exhaust stroke successively.Gear-box a6 ' is in peviform, axis hole is provided with in the middle of bottom it, power output gear axle a10 ' passes with external outputting power from this axis hole, and the periphery of gear-box a6 ' upper end case mouth is provided with flange plate, and flange plate is provided with screw and is connected with the lower card screw of dish a4 ' by bolt; .In the space surrounded by gear-box a6 ' and dish a4 ', first, second gear shaft 301, 302 symmetries are installed on the both sides of the axis hole axis in the middle of gear-box a6 ' bottom, axis hole in the middle of gear-box a6 ' bottom is provided with power output gear axle a10 ', the upper end of the first gear shaft 301 is provided with cylindrical gears 102, the upper end of the second gear shaft 302 is provided with cylindrical gears 104, the lower end of the first gear shaft 301 is provided with oval gear 201, the lower end of the second gear shaft 302 is provided with oval gear 204, two oval gear axles 303 are provided with oval gear 202, power output gear axle a10 ' is provided with oval gear 203, the keyway end of the first turning axle a13 ' and the second turning axle a21 ' is separately installed with cylindrical gears 101, 103 and corresponding to first, second gear shaft 301, the cylindrical gears 102 of the upper end of 302, 104 engage respectively, first, second gear shaft 301, the oval gear 201 of the lower end of 302, 204 engage respectively with the oval gear 202 on two oval gear axles 303, oval gear 202 on two oval gear axles 303 engages with the oval gear 203 on power output gear axle a10 ' simultaneously.

Oval gear 201, oval gear 202, oval gear 203, oval gear 204, its eccentricity is all , its major semi axis size is equal to each other, the gear parameters such as the joint garden radius of cylindrical gears 101, cylindrical gears 102, cylindrical gears 103, cylindrical gears 104 are equal, at a time, the semi-minor axis of oval gear 201 and the major semi axis conllinear of oval gear 202 be meshed with it, now, the semi-minor axis of this oval gear 202 and the major semi axis conllinear of oval gear 203 be meshed with it, now, the major semi axis of oval gear 204 and the semi-minor axis conllinear of oval gear 202 be meshed with it, now, the major semi axis of this oval gear 202 and the semi-minor axis conllinear of oval gear 203 be meshed with it, now, the first rotor a1 ' is in transient speed peak, second rotor a2 ' is in transient speed minimum point, and the part symmetry plane of the first rotor a1 ' and the second rotor a2 ' is perpendicular to one another, each volume of cylinder is equal.

Due to the effect of the inertia of each moving element of motor and load, can think that the rotating speed n0 on power output gear axle a10 ' is permanent rotating speed, this permanent rotating speed n0 is respectively by " power output gear axle a10 '-oval gear axle 303-first gear shaft 301-cylindrical gears 101 " the two groups of oval gear drive connections becoming series relationship with " power output gear axle a10 '-oval gear axle 303-second gear shaft 302-cylindrical gears 103 ", and the periodicity speed change of Correspondent cy linder gear 101 that is the first rotor a1 ' and cylindrical gears 103 that is the second rotor a2 ' is rotated respectively.According to oval gear design code, eccentricity is oval gear group, its instantaneous transmission ratio as shown in figure 30, abscissa in Figure 30 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, instantaneous transmission ratio consecutive variations more than single order can be led everywhere in theory, then can calculate the technical program and become two groups of oval gear group resultant gear ratios of series relationship as shown in figure 31, in Figure 31, abscissa is the rotation angle of power output gear axle a10 ', y coordinate is the instantaneous transmission ratio of the relative power output gear axle a10 ' of the first rotor a1 ' or the second rotor a2 ', the maximum value of its instantaneous transmission ratio is 4, minimum value is 0.25, instantaneous transmission ratio consecutive variations more than single order can be led everywhere in theory.According to aforesaid oval gear 201, oval gear 202, oval gear 203, the relative position relation of oval gear 204, rotating speed n0 on known corresponding power output gear axle a10 ', the instantaneous transmission ratio of the first rotor a1 ' and the second rotor a2 ' is transient speed all cyclically-varying and fixing phase differences of difference one in other words, as shown in figure 32, if represent the instantaneous transmission ratio of the first rotor a1 ' in Figure 32 with thick dashed line, then heavy line just represents the instantaneous transmission ratio of the second rotor a2 ', rotate one week (360 degree) corresponding to power output gear axle a10 ', the instantaneous transmission ratio of the first rotor a1 ' represented by two curves respectively and the second rotor a2 ' changes 2 cycles, 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 a10 ', the first rotor a1 ' and the second rotor a2 ' does the rotation of alternately acceleration and deceleration, therefore the periodic increase and decrease of angle between the first rotor a1 ' and the second rotor a2 ', instantaneous transmission ratio can be regarded as the derivative of the relative driving gear rotating speed of driven gear rotating speed, therefore the some closed areas by being surrounded by actual situation two curves in integral and calculating Figure 32, draw the variable angle amount maximum value between the first rotor a1 ' and the second rotor a2 ' = - =124 degree (about round numbers), 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 15.6 degree, in the running of internal-combustion engine, between first piston body a12 ' and the second piston body a22 ', minimum angle is =12.4 degree, maximum angle is = + =136.4 degree, and the fan-shaped square hole angle of porting 53 ' thus on desirable burning chamber shell 5 (angle definition with embodiment 1) be 15.6 degree, the spacing angle of the fan-shaped square hole of porting 53 (angle definition with embodiment 1) be 12.4 degree.In internal combustion engine operation process, corresponding power output gear axle 10 rotates 1 week, the relative position change of the first rotor a1 ' and the second rotor a2 ', can referring to figures 20 through situation shown in the embodiment 1 shown in Figure 28, by burning chamber shell, the first rotor, second rotor, the volume periodically increase and decrease of four cylinders that dish is separated out jointly, power output gear axle 10 rotates 1 week, the first rotor and the second rotor also rotate one week, each volume of cylinder increase and decrease secondary, 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.

The heat to power output principle of second embodiment of the invention, and volume of cylinder Variation Features, identical with the first embodiment, see Figure 33 (table 1) and Figure 35, this is repeated no more.

embodiment 4:in the embodiment of the present invention 3, dish a4 ' can be individual layer card, and centre is provided with axis hole, and card periphery all offers screw.Flange plate, the dish a4 ' of burning chamber shell a5 ' are bolted to connection successively with the flange plate of gear-box a6 '.Other is identical with embodiment 3.

the present invention has following advantageous application effect:

1, significantly can reduce engine consumption, improve fuel economy, 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 34 and table 2, Tu33Ji table 1shown combustion chamber volume change-time relationship characteristic of the present invention, shows 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 will be conducive to the abundant mixing of combustible oil gas mixture in cylinder slowly, and the time provided in cylinder required for combustible oil gas mixture Thorough combustion, 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 can reduce engine consumption, improve fuel economy, improve engine exhaust emission.

From the multiple thermodynamic cycle indicator diagram (p-v figure) shown in Figure 35, 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, improve engine exhaust emission.

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 is very little, substantially negligible.Thus add the clean output work of motor, obviously reduce engine consumption, improve fuel economy.

Again, compared with triangle rotor type motor.Face contact is during relative movement between each component 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, can reduce engine consumption, improve fuel economy, improve engine exhaust emission.

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 volume weight 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.

Secondly, compared with the crankshaft connecting rod type combustion chambers of internal combustion engines volume-variation-time relationship characteristic shown in Figure 34 and table 2, Tu33Ji table 1shown combustion chamber volume change-time relationship characteristic of the present invention, shows 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, improve the power per liter of motor, thus can improve the power to weight ratio of motor.

Again, the raising of the efficiency of cycle of the present invention and the increase of clean output work, also contribute to the raising of motor power to weight ratio.

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 33 (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 needs the application of higher power to weight ratio as aircraft power plant or other, by improving the rotating speed of motor, significantly improve the power to weight ratio of motor.

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., cylinder seal piston ring packing mode can using for reference crankshaft connecting rod type internal-combustion engine etc.

4, engine luggine and noise level low, smooth running, moving element is few, and 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 30, 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 can effectively avoid moving element 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 volume weight is large, and air cylinder structure is obvious compactness also.Therefore, under same displacement volume, the present invention can have obviously little many volume and weights, compact structure on the whole, can be applicable to better require the applications such as strict aircraft power plant to motor overall size.

6, engine power output torque is large.The present invention mainly realizes this effect by following technological approaches:

Power output gear axle 10 of the present invention rotates one week, four cylinders respectively complete the thermodynamic cycle once comprising air-breathing, compression, acting, exhaust four strokes, and with four cylinder crankshaft connecting rod type internal-combustion engines of discharge capacity, be then crankshaft rotating two weeks, four cylinders respectively complete the thermodynamic cycle once comprising air-breathing, compression, acting, exhaust four strokes.Acting speed of the present invention is same discharge capacity with two times of the crankshaft connecting rod type internal-combustion engine of rotating speed; Consider 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 again.Therefore Power output moment of torsion of the present invention is same discharge capacity with more than two times of crankshaft connecting rod type internal-combustion engine of rotating speed.

7, the multiple design parameter of motor is adjustable.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; Change the first rotor of the present invention and bitrochanteric angular velocity cycle fixed skew by angle between the major axis that changes power output gear axle two oval gears, the volume of cylinder-time behavior 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 spark plug/oil sprayer 100 mounting hole place on internal-combustion engine housing that the another set of porting being symmetrical in existing porting is set, can the present invention be changed into pump; For the second technological scheme of the present invention, can also by the joint garden radius of cylindrical gears 101 and cylindrical gears 103, all change 0.5 times that the cylindrical gears 102 that is meshed with it respectively and cylindrical gears 104 save garden radius into, can the present invention be changed into pump.

The pump developed 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 33 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

1. double-piston rotor internal-combustion engine, it is characterized in that: the first rotor is Y-shaped structure, comprise rotating shaft dish, one end of rotating shaft dish is two first piston bodies with the first turning axle axisymmetrical, the other end is provided with the first turning axle, the termination of the first turning axle is provided with keyway, and the first turning axle axle center is provided with axis hole;

2. double-piston rotor internal-combustion engine, is characterized in that: burning chamber shell a is in falling peviform, and basin mouth periphery is provided with flange plate, is provided with the first rotor a and the second rotor a in burning chamber shell a; The first rotor a is Y shape part, and its one end is two first piston body a of the first turning axle a axisymmetrical, and the other end is provided with keyway, and the first turning axle a axle center of the first rotor a is provided with manhole; Second rotor a is T-piece, and its one end is two the second piston body a of the second turning axle a axisymmetrical, and the other end is provided with keyway; Second turning axle a is set in the manhole of the first rotor a;

3. double-piston rotor internal-combustion engine according to claim 1 and 2, is characterized in that: described dish or described dish a all can be individual layer card, and be provided with axis hole in the middle of card, card periphery offers screw.