CN104727936B - Double-piston rotary internal combustion engine - Google Patents
Double-piston rotary internal combustion engine Download PDFInfo
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- CN104727936B CN104727936B CN201510029762.9A CN201510029762A CN104727936B CN 104727936 B CN104727936 B CN 104727936B CN 201510029762 A CN201510029762 A CN 201510029762A CN 104727936 B CN104727936 B CN 104727936B
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Abstract
The invention discloses a kind of double-piston rotary internal combustion engine, the first rotor is made up of rotating shaft disk, first piston body and the first gyroaxis, and the bottom surface of cover plate is connected with first piston body end face；Second rotor is made up of the second gyroaxis and second piston body；The upper end plate of dish and lower end plate are connected with the ring flange of burning chamber shell and gear-box respectively；The incomplete roller gear of the first roller gear and first gear axle and second gear axle that are arranged on the first gyroaxis axle head alternately engages, the incomplete roller gear of the second roller gear and first gear axle and second gear axle that are arranged on the second gyroaxis axle head alternately engages, and the roller gear of cylindrical gear shaft is engaged respectively with the roller gear of first gear axle and power output gear axle；The oval gear of oval gear axle is engaged respectively with the oval gear of second gear axle and power output gear axle.Oil consumption of the present invention is low, power to weight ratio is high, moment of torsion is big, simple and compact for structure, vibration is light, life-span length, easily design, easily manufacture.
Description
Technical field
The present invention relates to technical field of internal combustion engines, particularly to rotary-piston class double-piston rotary internal combustion engine.
Background technology
Heat engine is to convert heat energy into the device of mechanical energy, and internal combustion engine is an important kind of heat engine, and internal combustion engine is main
Including ignition system, combustion system, drive system, cooling system, oil supply system, lubricating system etc..
Since 1898 about Christian era crankshaft connecting rod type internal combustion engine is invented so far, in surface car, shipping and various dynamic
In power equipment, crankshaft connecting rod type internal combustion engine obtains most commonly used application, and has greatly accelerated the historical progress of the mankind.Bent axle
The basic functional principle of connecting rod type internal-combustion engine, is that the gases at high pressure promotion that piston is burnt in cylinder moves up and down, and leads to
Crossing the rotation of connecting rod band dynamic crankshaft, the straight reciprocating motion of piston being converted into the unidirectional rotary motion of bent axle, thus realizing bent axle
The heat to power output of connecting rod type internal-combustion engine and power output.
The key technical indexes evaluating internal combustion engine has power to weight ratio（Power/weight ratio, is sometimes also adopted by cylinder power per liter and refers to
Mark）, oil consumption rate, anufacturability, working service life-span etc..For crankshaft connecting rod type internal combustion engine, engine power output is logical
Cross what the crankshaft connecting rod type drive system of piston, connecting rod and bent axle triplicity completed.This internal combustion engine mainly has as follows
Structural disadvantage:
1st, in crankshaft connecting rod type biography cylinder of internal-combustion engine, gaseous mixture burning time when pressure maximum, volume are minimum is 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 carry
High engine performance, all reaches the different degrees of advanced ignition of before upper dead canter or oil spout in order to allow gaseous mixture in piston
When combustion chamber volume is minimum, burning faster, more completely, so as to obtain bigger power output, and reduces electromotor
Discharge exhaust gas concentration, but do so also creates certain negative interaction：Because of advanced ignition, in-cylinder pressure drastically raises, and blocks
Piston stroking upward, increased compression negative work, and easily causes combustion knock phenomenon.This contradiction is in existing crankshaft connecting rod type internal combustion
All the time exist in machine.
2nd, during crankshaft connecting rod type internal combustion engine operation, the force direction periodically-varied to piston for the connecting rod, and
When engine power output is maximum, connecting rod also reaches near maximum along cylinder wall surface normal direction to the active force of piston, by
This causes the frictional power loss between piston and cylinder very big, and is easily caused surface between piston and cylinder and draws because of friction
The damage rising.
3rd, in the operation process of crankshaft connecting rod type internal combustion engine, piston is in a kind of reciprocating motion state all the time, during air inlet
Piston enters compression travel in lower dead center moment again quickly, thus not having more time inspirations more when cylinder body volume is maximum
Fresh mixing oil gas, during aerofluxuss, piston enters suction stroke quickly to top dead centre moment again, so that volume of cylinder is minimum
When do not have more times to allow waste gas farthest to discharge, these situations finally all affect more fresh mixing oil gas enter
Entering cylinder, thus leading to engine breathing efficiency low, making the raising of HP, hp/litre be subject to certain affecting.
4th, crankshaft connecting rod system is not axial symmetry part, the vibration being caused by crankshaft connecting rod system during internal combustion engine operation
Greatly, noise is big；Crankshaft connecting rod system has much difficulty in healing weighing apparatus, and its manufacturing process is more complicated, high cost；In use, piston, bent axle connect
Linkage etc. is easy to wear, and maintenance cost is high；Internal combustion engine limit speed using crankshaft-link rod is low, seriously constrains electromotor work(weight
The raising of ratio.
5th, the complex structure such as the air throttle of crankshaft connecting rod type internal combustion engine, crankshaft-link rod, takes up room big, leads to electromotor to be tied
Structure is not compact.
Since entering for 20th century, the manifesting of energy crisis, and problem of environmental pollution is intensification, promotes to bent axle even
The design improvement of rod-type internal combustion engine.At present, the design through multiple stages such as pressurized combustion, EFIization improvement improves, bent
The technical performance index of axle connecting rod type internal-combustion engine substantially reached ultimate attainment, but tied by above-mentioned crankshaft connecting rod type internal combustion engine
The restriction of structure shortcoming, wants to obtain the internal combustion engine of more preferable technical performance index, only adopts new IC Engine Design scheme.
Early in 20 beginnings of the century, occur in that a kind of internal combustion engine being referred to as triangle rotor type electromotor, and obtain later
Relatively broad application.Compared with crankshaft connecting rod type internal combustion engine, triangle rotor type electromotor employs the interior of gear-driven form
Combustion engine Design of Transmission System, preferably, Engine Limit rotating speed is high, the therefore work(weight of electromotor for the axial symmetry of gear drive
Outstanding than more, structure is also more compact.But in place of triangle rotor type electromotor there is also some shortcomings.Such as cylinder internal combustion
Burning is insufficient, oil consumption is excessive, and output shaft torque is too small, cylinder seal difficulty etc..This is because in rotary polygonal piston engine cylinder
The bulbs of pressure that combustion gas acts on rotor side surface are divided into two power, push dynamic output shaft rotation for one, and another power is pointed to
Output shaft center, thus lead to whole machine output torque too small；Make combustion rate too low because its cylinder is long and narrow, excessive oil consumption；
Because using the cylinder of special shape, result in the difficulty that cylinder processing and manufacturing and cylinder seal manufacture and design.Above-mentioned triangle
The some problem that rotor motor exists, leads to it to be difficult to greatly increasingly serious today in energy crisis and problem of environmental pollution
Scope is promoted the use of.
Enter 21 century, on the one hand, from the angle of social need：
1st, energy crisis is more significantly, and environmental problem is on the rise, and the discharge standard of internal combustion engine improves constantly, thus promoting
The mankind find the internal-combustion engine technology of more energy-conserving and environment-protective.
2nd, in car and boat power set field, especially in the family-sized car field that market is huge, by battery durable ability, electricity
The restriction of pond safety, charging public utility construction coverage etc., the domestic sedan-chair of pure motorized motions for a comparatively long period of time
Car market share is still very low, and the internal combustion engine of oil electricity mixed form will become the green of the family-sized car of future city society etc.
Power set are practical to be selected.
3rd, in military technological field, the battlefield surroundings of Future Information, will further facilitate various unmanned vehicle equipments
Innovation Input, relatively other power set such as aero-turbine, internal combustion engine is with its significantly low oil consumption, long-life, low
The technical advantages such as cost, will continue to occupy one seat in unmanned vehicle power set field.
4th, other aspects, such as personal aircraft industry, aviation plant protection industry, aviation patrol and examine industry, model plane motion industry, aviation
Sports industry etc., internal combustion engine will continue its important power set role and status.
On the other hand, from the angle of internal-combustion engine technology development：
1st, crankshaft connecting rod type internal combustion engine improves through some designs, and its technical performance has reached substantially to the limit, its technology
The higher requirement of difficult to reach such as performance indications power to weight ratio, oil consumption rate, anufacturability, working service life-span.
2nd, triangle rotor type electromotor is one of internal-combustion engine technology breakthrough, but its high oil consumption, low output torque, sealing are tired
The technology weakness such as difficulty makes it be difficult to become the main body of internal-combustion engine technology of new generation.
Although the 3, triangle rotor type electromotor has many technology weaknesses, the brand new form that it adopts, open
New design philosophy, opens the beginning of " rotary-piston class internal combustion engine ", is expected to solve many structures of crankshaft connecting rod type internal combustion engine
Property shortcoming, so in today of 21 century, occurring in that the patent of invention of more " rotary-piston class internal combustion engine ".But it is at present just
Only, in such patent of invention, some patents are the mutation of crankshaft connecting rod type internal combustion engine, and its structure still retains crankshaft-link rod shape
Parts, have impact on internal combustion engine performance realize；Some patent structure designs are excessively complicated, have impact on the work(weight of internal combustion engine
Than, anufacturability, working service life-span etc.；Some patents lack necessary Quantitative design and analysis, according to its conceptual design
Manufacture product and do not actually reach the nominal technical performance of patent.
In sum：21 century needs the technology such as a kind of power to weight ratio, oil consumption rate, anufacturability, working service life-span to refer to
Indicate the internal-combustion engine technology of important breakthrough, and " rotary-piston class internal combustion engine " is likely to become and meets these technical requirements
Internal-combustion engine technology of new generation.
Content of the invention
It is an object of the invention to provide double-piston rotary internal combustion engine, use for reference the excellent design theory of " rotary-piston ", lead to
Cross fundamental difference in crankshaft connecting rod type internal combustion engine, be also substantially distinguished from the heating power Transfer Structure Design of triangle rotor type electromotor,
Realize the important breakthrough in the key technical indexes such as power to weight ratio, oil consumption rate, anufacturability, working service life-spans for the internal combustion engine, with
Meet the use demand to internal-combustion engine technology for the mankind.
The present invention takes technical scheme below to realize above-mentioned purpose.Double-piston rotary internal combustion engine, including the first rotor,
Cover plate, the second rotor, dish, burning chamber shell and gear-box, the first rotor is Y-shaped, by rotating shaft disk, first piston body and
Single-revolution axle constitute, rotating shaft disk one side be provided centrally with the first gyroaxis, rotating shaft disk another side is around the first gyroaxis axis pair
Claim to be provided with two first piston bodies, the axle head of the first gyroaxis is provided with keyway, and the axle center of the first gyroaxis is provided with axis hole；
Cover plate is discoid, and the middle setting of cover plate has the boss with central through hole, and the periphery of cover plate is provided with chimb；Lid
The bottom surface of plate is connected with first piston body end face；
Second rotor is T-shaped, is made up of the second gyroaxis and second piston body, one end of the second gyroaxis is symmetrically arranged with
Two second piston bodies, the termination of the other end of the second gyroaxis is provided with keyway, and first piston body and second piston body is outer
All equal diameters；
The dish axle center of dish is provided with axis hole, and the two ends of dish axle are connected with end plate and lower end plate, upper end plate periphery and
Lower end plate periphery is provided with screw；Second gyroaxis is threaded onto in the axis hole of the first gyroaxis, the first gyroaxis and second time
Rotating shaft is all threaded onto in the axis hole at dish axle center, first piston body and second piston extracorporeal set combuster housing；
Burning chamber shell is provided with ring flange in peviform, the periphery at the room bottom of burning chamber shell, and ring flange is provided with spiral shell
Hole, burning chamber shell periphery is provided with porting, and on burning chamber shell, the offside of porting is provided with spark plug/fuel injector
Pilot hole, spark plug/fuel injector is fixedly installed in pilot hole；The upper end plate of dish is adjacent with the rotating shaft disk of the first rotor, disk
The screw of upper end plate of shape part and the screw of burning chamber shell ring flange are bolted；
Gear-box is in peviform, and its bottom middle setting has axis hole, and the periphery of gear-box upper end case mouth is provided with ring flange, method
Blue disk is provided with screw and the lower end valve snail hole with dish is bolted；Gear-box bottom axis hole is provided with power output tooth
Wheel shaft, the both sides of power output gear axle are provided with oval gear axle and cylindrical gear shaft, and power output gear axle is provided with one
Individual oval gear and a roller gear, the oval gear on power output gear axle is nibbled with the oval gear on oval gear axle
Close, the roller gear on power output gear axle is engaged with the roller gear in cylindrical gear shaft；It is provided with first gear axle
One complete roller gear and two incomplete roller gears, second gear axle is provided with an oval gear and two not complete
Wholecircle stud wheel；Roller gear in cylindrical gear shaft is engaged with the complete roller gear on first gear axle；Oval gear axle
On oval gear engage with the oval gear on second gear axle；The shaft with keyway end of the second gyroaxis and the first gyroaxis is all
In gear-box, equipped with the first roller gear, the axle head of the second gyroaxis is equipped with the second Cylinder Gear for the axle head of the first gyroaxis
Wheel, the first roller gear is replaced with the incomplete roller gear of first gear axle and the incomplete roller gear of second gear axle to be nibbled
Close, the second roller gear is replaced with the incomplete roller gear of first gear axle and the incomplete roller gear of second gear axle to be nibbled
Close.
The gear teeth of two incomplete roller gears of described first gear axle are axially complementary.
The gear teeth of two incomplete roller gears of described second gear axle are axially complementary.
Described dish can be monolayer card, and card middle setting has axis hole, and 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 volume
Variable cylinder, during internal combustion engine operation, from power output gear shaft to the first rotor and bitrochanteric drive connection
Observe, respectively through two-way, a road is include into series relationship two to the uniform rotation campaign on power output gear axle
" the power output gear axle-oval gear axle-second gear axle the-the first roller gear/the second roller gear " of oval gear group
The conversion of alternately engaged transmission, another road be constant ratio " power output gear axle-cylindrical gear shaft-first gear axle-
The alternately engaged transmission conversion of the second roller gear/the first roller gear ", is ultimately converted to the first rotor and bitrochanteric tool
The periodicity variable speed having fixed skew moves.So that the volume of four cylinders periodicity increase and decrease successively, and according to
It is in air-breathing, compression, acting, exhaust stroke second periodicity, thus cylinder of internal-combustion engine produces circulation work(, and pass through power output
Gear shaft outwards exports power.
Double-piston rotary internal combustion engine provided by the present invention, has following beneficial effect：
1st, significantly reducing engine consumption, thus improving fuel economy, and improving engine exhaust emission.
2nd, the power to weight ratio of electromotor can be greatly improved.
3rd, engine structure is simple, and anufacturability is good.
4th, engine luggine and noise level are low, smooth running, and moving component is few, thus the electromotor working service life-span
Long.
5th, engine structure is compact.
6th, engine power output torque is big.
7th, the multiple design parameter of electromotor can adjust.
8th, the structure design only needing very little adjusts, and the present invention can change into high performance pump.
Brief description
Fig. 1 is the perspective view of the present invention.
Fig. 2 is the 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 the cover plate of the present invention.
Fig. 5 is the perspective view with cover plate combination for the first rotor of the present invention.
Fig. 6 is the bitrochanteric perspective view of the present invention.
Fig. 7 is the perspective view of the dish of the present invention.
Fig. 8 is the front view of the burning chamber shell of the present invention.
Fig. 9 be in Fig. 8 A-A to cross section structure diagram.
Figure 10 is the perspective view of the first gear axle of the present invention.
Figure 11 is the perspective view of the second gear axle of the present invention.
Figure 12 is rotor motion and the volume of cylinder change schematic diagram of the present invention（When power output gear Shaft angle is 0 °
Carve）.
Figure 13 is rotor motion and the volume of cylinder change schematic diagram of the present invention（When power output gear Shaft angle is 90 °
Carve）.
Figure 14 is rotor motion and the volume of cylinder change schematic diagram of the present invention（When power output gear Shaft angle is 180 °
Carve）.
Figure 15 is rotor motion and the volume of cylinder change schematic diagram of the present invention（When power output gear Shaft angle is 270 °
Carve）.
Figure 16 is rotor motion and the volume of cylinder change schematic diagram of the present invention（When power output gear Shaft angle is 360 °
Carve）.
Figure 17 is rotor motion and the volume of cylinder change schematic diagram of the present invention（When power output gear Shaft angle is 450 °
Carve）.
Figure 18 is rotor motion and the volume of cylinder change schematic diagram of the present invention（When power output gear Shaft angle is 540 °
Carve）.
Figure 19 is rotor motion and the volume of cylinder change schematic diagram of the present invention（When power output gear Shaft angle is 630 °
Carve）.
Figure 20 is rotor motion and the volume of cylinder change schematic diagram of the present invention（When power output gear Shaft angle is 720 °
Carve）.
Figure 21 is cylinder maximum and the minimum volume view of the present invention.
Figure 22 is the instantaneous transmission ratio schematic diagram of an oval gear group engaged transmission.
Figure 23 is two oval gear group resultant gear ratio schematic diagrams of the one-tenth series relationship of the present invention.
Figure 24 is the instantaneous transmission ratio schematic diagram that the first rotor of the present invention and the second rotor are relative to power output gear axle.
Figure 25 is the 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 preferable constant volume cycle（Represented with beading fine line I）, crankshaft connecting rod type internal combustion engine actual cycle（With slightly void
Line III represents）, actual cycle of the present invention（Represented with heavy line II）Indicator card（P-v schemes）.
Specific embodiment
The present invention is described further with reference to the accompanying drawings and examples.
Embodiment 1：The double-piston rotary internal combustion engine of the present invention, including combustion system, drive system etc., referring to Fig. 1 extremely
Figure 11.
The first rotor 1 is Y shape part, and including rotating shaft disk 101, one end of rotating shaft disk 101 is and the first gyroaxis 103 axis
Two symmetrical first piston bodies 102, the other end is provided with the first gyroaxis 103, and the termination of the first gyroaxis 103 is provided with key
Groove, the axle center of the first gyroaxis 103 is provided with axis hole, cover plate 2 be discoid, cover plate 2 also offers with first piston body 102 on
The corresponding some through holes in position, pass through first piston body 102 and cover plate 2 through hole using several between the first rotor 1 and cover plate 2
Bolt connection fix.Second rotor 3 is T-shaped structure, and is provided with the second gyroaxis 31, one end setting of the second gyroaxis 31
Have two second piston bodies 32 with axisymmetrical, the other end of the second gyroaxis 31 offers keyway, first piston body 102 with
The outer circumference diameter of second piston body 32 and fan angleAll equal.Second rotor 3 is co-axially mounted with the first rotor 1 and can phase
To rotation, carrying out the second rotor 3 and when being co-axially mounted of the first rotor 1, first the keyway arrangements end of the second rotor 3 is being passed through
The axis hole in the first gyroaxis 103 axle center, the assembling then carrying out again between the first rotor 1 and cover plate 2 is fixed.The disk of dish 4
Axle 43 center 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 being beneficial to
Radiating, upper end plate 41 periphery and lower end plate 42 periphery are provided with screw.Second gyroaxis 31 is threaded onto the first gyroaxis 103
After in axis hole, then it is threaded onto together in dish axle 43 central shaft hole.It is set with combustion outside first piston body 102 and second piston body 32
Burn room housing 5, burning chamber shell 5 is provided with grid hole and is beneficial to radiating, room bottom in peviform, the ceiling 51 of burning chamber shell 5
52 periphery is provided with ring flange, and ring flange is provided with screw, and burning chamber shell 5 periphery is provided with porting 53, combustion chamber shell
On body 5, the offside of porting 53 is provided with the pilot hole 54 of spark plug/fuel injector 7, and spark plug/fuel injector 7 is fixedly installed in
Pilot hole 54.The upper end plate 41 of dish 4 is adjacent with the rotating shaft disk 101 of the first rotor 1, the screw of the upper end plate 41 of dish 4
It is bolted with the screw of burning chamber shell 5 ring flange.Gear-box 6 is in peviform, and its bottom middle setting has axis hole, internal combustion
The power output gear axle 10 of machine passes with outside output power at this hole, and the periphery of gear-box 6 upper end case mouth is provided with method
Blue disk, ring flange is provided with screw and lower end plate 42 screw with dish 4 is bolted.
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 are provided with an oval gear and a roller gear, and oval gear and the cylindrical gear shaft with oval gear axle 14 respectively
13 roller gear engagement.Be provided with first gear axle 8 a complete roller gear and two incomplete roller gears 81,
82, second gear axle 9 is provided with an oval gear and two incomplete roller gears 91,92, the circle of cylindrical gear shaft 13
Stud wheel is engaged with the complete roller gear of first gear axle 8, the ovum of the oval gear of oval gear axle 14 and second gear axle 9
Shape gear engages, and the shaft with keyway end of the second gyroaxis 31 and the first gyroaxis 103 is all located in gear-box 6, the first gyroaxis
, equipped with the first roller gear 11, the second gyroaxis 31 axle head is equipped with the second roller gear 12, the first roller gear 11 for 103 axle head
Alternately engage with the incomplete roller gear 81 of first gear axle 8 and the incomplete roller gear 91 of second gear axle 9, the second circle
Stud wheel 12 is replaced with the incomplete roller gear 82 of first gear axle 8 and the incomplete roller gear 92 of second gear axle 9 to be nibbled
Close.
The oval gear installed on second gear axle 9, oval gear axle 14, power output gear axle 10, its eccentricity is equal
For 1/3rd, its major semiaxis size is equal to each other；The roller gear of power output gear axle 10 and the circle of cylindrical gear shaft 13
Stud wheel, its pitch circle radius ratio is 1:1；The roller gear of cylindrical gear shaft 13 and the complete Cylinder Gear of first gear axle 8
Wheel, its pitch circle radius ratio is 1:2；Two incomplete roller gears 81,82 and first roller gear of first gear axle 8
11/ second roller gear 12, its pitch circle radius ratio is all 2:5；Two incomplete roller gears 91 of second gear axle 9,
92 and the first roller gear 11/ second roller gear 12, its pitch circle radius ratio is all 4:5；Each of first gear axle 8 is not
Completely roller gear such as has at the number of teeth and two sections of uniform continuous gear teeth of circumference, and every section of continuous corresponding central angle of the gear teeth is 90 °；
Two incomplete roller gears 81,82 of first gear axle 8, its pitch circle radius is equal, and the revolution from first gear axle 8
Axis direction is seen, the continuous gear teeth of two incomplete roller gears 81,82 stagger each other completely；Each of second gear axle 9 is not
Completely roller gear 91,92 has one section of continuous gear teeth, and the corresponding central angle of this continuous gear teeth is 180 °；Second gear axle 9
Two incomplete roller gears 91,92, its pitch circle radius is equal, and in terms of the axis direction of second gear axle 9, two are not
The continuous gear teeth of roller gear 91,92 completely stagger each other completely.
Sometime, when major semiaxis and the oval gear being meshed therewith of the oval gear of power output gear axle 10
When the semi-minor axis of the oval gear of axle 14 is conllinear, the major semiaxis of the oval gear of oval gear axle 14 and be meshed therewith second
The oval gear semi-minor axis of gear shaft 9 is conllinear；Now, the incomplete roller gear 92 of second gear axle 9 and the second roller gear
The 12 continuous engagement time length being continuously engaged to half, the incomplete roller gear 91 of second gear axle 9 and the first Cylinder Gear
Wheel 11 is disengaged from the time span that is disengaged from, the incomplete roller gear 82 of first gear axle 8 and second cylinder of half
Gear 12 is disengaged from the time span that is disengaged from of half, the incomplete roller gear 81 of first gear axle 8 and the first circle
Stud wheel 11 is continuously engaged to the continuous engagement time length of half；Now, the first rotor 1 is in the transient speed minimum period,
Second rotor 3 is in transient speed peak, and the part plane of symmetry of the first rotor 1 and the second rotor 3 is perpendicular to one another, each gas
Cylinder volume is equal.
Because the effect of inertia of each moving component of electromotor and load is it is believed that rotating speed n0 on power output gear axle 10
For permanent rotating speed, respectively through two-way, a road is the " power of two oval gear groups including into series relationship to this permanent rotating speed n0
Alternately the nibbling of output gear shaft 10- oval gear axle 14- second gear axle 9- the first roller gear 11/ second roller gear 12 "
Close transmission conversion, another road is " the power output gear axle 10- cylindrical gear shaft 13- first gear axle 8- the of constant ratio
The alternately engaged transmission conversion of two roller gear 12/ first roller gear 11 ", is ultimately converted to the first rotor 1 and the second rotor 3
Have fixed skew periodicity variable speed motion.So that the volume of 4 cylinders periodicity increase and decrease successively, and
Periodically it is in air-breathing, compression, acting, exhaust stroke successively, thus cylinder of internal-combustion engine produces circulation work(and defeated by power
Go out gear shaft 10 and outwards export power.
According to oval gear design specification, eccentricity is 1/3rd oval gear group, its instantaneous transmission such as Figure 22
Shown, the abscissa in Figure 22 is the rotational angle of drivewheel, and vertical coordinate is the instantaneous transmission ratio that driven pulley is relative to drivewheel, its
The maximum of instantaneous transmission ratio is 2, and minima is 0.5, and this instantaneous transmission ratio consecutive variations more than single order can be led everywhere in theory,
The present invention thus can be calculated becomes two groups of oval gear group resultant gear ratios of series relationship as shown in figure 23, abscissa in Figure 23
For the rotational angle of power output gear axle 10, vertical coordinate is the instantaneous biography of second gear axle 9 power output gear axle 10 relatively
Dynamic ratio, the maximum of its instantaneous transmission ratio is 4, and minima is 0.25, this instantaneous transmission ratio consecutive variations single order everywhere in theory
More than can lead.According to two incomplete roller gear the 91,92 and first roller gears 11/ second on aforesaid second gear axle 9
Cylinder Gear in the pitch circle radius ratio of roller gear 12, and aforesaid power output gear axle 10 and cylindrical gear shaft 13
Two incomplete roller gear 81,82 and first roller gears 11/ on wheel pitch radius ratio, and aforesaid first gear axle 8
The pitch circle radius ratio of the second roller gear 12, can calculate the first roller gear 11（Or the first rotor 1）With second
Roller gear 12（Or the second rotor 3）The instantaneous transmission ratio of power output gear axle 10 relatively is as shown in figure 24, and Figure 24 represents
Instantaneous transmission ratio maximum be 4*4/5=3.2, instantaneous transmission ratio minima be 0.25*4/5=0.2, if with thick dashed line in Figure 24
Represent the instantaneous transmission ratio of the first rotor 1, then heavy line means that the instantaneous transmission ratio of the second rotor 3, the heavy line in Figure 24
Or by a segment table, thick dashed line, all shows that the curve of variable ratio and a segment table show that more than the curve single order of fixed drive ratio continuously may be used
Leading is connected smoothly forms, and the junction point of two sections of curves is that the first roller gear 11 is not exclusively round with first gear axle 8
The alternately meshing point of incomplete roller gear 91 on stud wheel 81 and second gear axle 9, or the second roller gear 12 and the
The alternately meshing point of incomplete roller gear 92 on incomplete roller gear 82 and second gear axle 9 on one gear shaft 8, should be alternately
The rotational angle of the corresponding power output gear axle 10 of meshing point is 0 ° and 180 ° of moment, rotates one for power output gear axle 10
Week（360°）, the instantaneous transmission ratio of the first rotor 1 that represented by thick dashed line and two curves of heavy line respectively and the second rotor 3 becomes
Change a cycle, and the phase contrast of both is 0.5 instantaneous transmission ratio period of change.This shows, in power output gear axle
During 10 uniform rotation, the first rotor 1 and the second rotor 3 do the rotation of alternately acceleration and deceleration, therefore the first rotor 1 and second
The periodic increase and decrease of angle between rotor 3.
Instantaneous transmission ratio can be regarded as the derivative that driven gear rotating speed is relative to driving gear rotating speed, therefore can pass through integrating meter
Some closed area being surrounded by two curves of deficiency and excess in nomogram 24, draws the angle between the first rotor 1 and the second rotor 3
Variable quantity maximum=-=1O8 °, the combustor ideal theoretical compression ratio taking the present invention is 11:1, then can calculate
The fan-shaped angle of each piston bodyIt is 25.2 °, in the running of internal combustion engine, first piston body 102 and second piston
Between body 32, minimum angle is=1O.8 °, maximum angle is=+=118.8 °, and thus can use combustion chamber shell
The fan-shaped square hole angle of the porting 53 on body 5It is 25.2 °, the spacing angle of the fan-shaped square hole of porting 53For
10.8°.During internal combustion engine operation, corresponding power output gear axle 10 rotates two weeks, the phase of the first rotor 1 and the second rotor 3
To change in location as shown in Figure 12-Figure 20, in Figure 12-Figure 20, with the corner change of power output gear axle 10, by combustor
The volume periodicity increase and decrease of four cylinders that housing 5, the first rotor 1, cover plate 2, the second rotor 3 are separated out jointly, power
Output gear shaft 10 rotates two weeks, and the first rotor 1 and the second rotor 3 respectively rotate one week, each volume of cylinder increase and decrease four times,
And it is in air-breathing, compression, acting, exhaust stroke successively, then, it is a thermodynamic cycle that each cylinder completes four strokes, whole
It is four thermodynamic cycles that individual internal combustion engine completes 16 strokes.
The heat to power output principle of the present invention is：Gas in each cylinder is externally exported on piston body by active force
Work(, in any moment, the gas in each cylinder is applied with equal gas pressure effect to the piston body of cylinder both sides, therefore
This cylinder both sides piston body obtain at this cylinder interior gas respectively moment loading equal in magnitude and in opposite direction+（+ number
Represent that this moment direction is identical with piston body angular velocity direction）With-（- number represent this moment direction and piston body angular velocity side
To contrary）, the effect axis of moment is the rotary shaft of piston body, and each piston body is under the moment loading obtaining respectively with angle speed
DegreeWithRotate, therefore each piston body obtain respectively at this cylinder interior gas power+With-, this power
Through meshed transmission gear, the power output gear axle 10 coalgebra superposition being finally all delivered to internal combustion engine obtains gas in this cylinder
The net output work of bodyIt can be seen that, each cylinder interior gas is externally exported by power output gear axle 10
Net work is suffered gas load square on the piston body of cylinder sideDifference with cylinder both sides piston body angular velocity
Product.It can be appreciated that the angular velocity of the fan-shaped volume change of this cylinder interior gas is that is to say, that due to first
There is the angular velocity difference of periodicity alternate, therefore volume of cylinder periodicity increase and decrease, cylinder in rotor 1 and the second rotor 3
Also just can periodically be in air-breathing, compression, acting, in exhaust stroke, thus cylinder of internal-combustion engine produces circulation work(, and by dynamic
Power output gear shaft 10 outwards exports power.
For the volume of cylinder Variation Features of the further comparative illustration present invention, the volume of cylinder change procedure of the present invention is returned
One change is processed, and compared with the volume of cylinder change procedure of the crankshaft connecting rod type internal combustion engine after normalized.Normalized
Method is a kind of method of conventional nondimensionalization in engineering, and the present invention is the chi comparing for unification using normalized purpose
Degree.The normalized method of the present invention is under the conditions of the reasonable assumption of the permanent rotating speed of power output gear axle 10 of the present invention, by meter
Calculate transient change amount (0-1 numerical intervals, volume variable quantity when cylinder is in minimum volume state drawing volume of cylinder of the present invention
For 0, cylinder be in maximum volume state be volume variable quantity be 1) with the corresponding time（0-1 numerical intervals）Corresponding relation.Root
According to the first rotor of the present invention 1 shown in Figure 24 and the instantaneous transmission ratio relation of the relative power output gear axle 10 of the second rotor 3, obtain
Go out the volume of cylinder variable quantity of the present invention after normalized（Volume increment）Change over relation as shown in figure 25, accordingly
Number list is as shown in table 1.
Table 1：Normalized combustion chamber volume variable quantity-time relationship numerical tabular of the present invention
| Time t | Normalization volume variable quantity 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 Biao 1, rise to 1 from 0 in time（The whole volume of correspondence increases the time period）, volume of cylinder instantaneous
Increment increases to 1 from 0（Corresponding volume increment reaches maximum from 0）.
The cylinder that the identical method for normalizing of the crankshaft connecting rod type internal combustion engine shown in contrast Figure 26 with Biao 2 obtains after processing holds
Long-pending increment changes over relation.
Table 2：Crankshaft connecting rod type internal combustion engine normalized combustion chamber volume variable quantity-time relationship numerical tabular
| Time t | Normalization volume variable quantity 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 |
It can be seen that, the volume of cylinder pace of change of the present invention all substantially reduces when cylinder instantaneous volumetric is minimum and maximum, because
And the thermodynamic cycle of the present invention is more prone to the high preferable constant volume cycle of the thermal efficiency.Multiple thermodynamic cycles shown in from Figure 27 are shown
Work(figure（P-v schemes）On see, preferable constant volume cycle（Represented with beading fine line I）The area surrounding on indicator card is maximum, represents
Unit working medium under preferable constant volume cycle, produces circulation work(maximum；Crankshaft connecting rod type internal combustion engine actual cycle（With thick dashed line III table
Show）The area surrounding on indicator card is minimum, represents the unit working medium under crankshaft connecting rod type internal combustion engine actual cycle, produces circulation
Work(is minimum；The actual cycle of the present invention（Represented with heavy line II）Although the area surrounding on indicator card is less than preferable constant volume and follows
Ring surround area, but the actual cycle of the present invention surrounds area than crankshaft connecting rod type internal combustion engine actual cycle on indicator card
Area is substantially much bigger for surrounding on indicator card, thus the thermodynamic cycle of the present invention is more prone to the high ideal of the thermal efficiency and determines
Hold circulation, the Actual cycle work of the present invention substantially increases than crankshaft connecting rod type internal combustion engine Actual cycle work, thus being conducive to starting
The obvious reduction of engine oil 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 opens up of the axis hole of lower end plate 42 middle setting and card periphery is so that dish
4 only have monolayer card.I.e.：Dish 4 can be monolayer card, and middle setting has axis hole, and card periphery all offers screw.Burning
The ring flange of room housing 5, dish 4 pass sequentially through bolt with the ring flange of gear-box 6 and are fixedly connected.Other and embodiment 1 phase
With.
The present invention has following advantageous application effect：
1st, significantly reducing engine consumption, thus improving fuel economy, and improving engine exhaust emission.This
Invention mainly realizes this application effect by following technological approaches：
First, with the crankshaft connecting rod type combustion chambers of internal combustion engines volume change-time relationship characteristic phase shown in Figure 26 and table 2
Than, the combustion chamber volume change-time relationship characteristic of the present invention shown in Figure 25 and table 1, the volume of cylinder showing the present invention is at it
When minimum or maximum, change is very slow.When cylinder interior gas are in the compression stroke later stage, slow volume of cylinder pace of change will
Be conducive to the time required for combustible oil gas mixture fully burns in increase cylinder, so as to allow the electronic spark advance of electromotor
Angle greatly reduces, and substantially reduces the compression negative work of cylinder interior gas, increased the circulation work(of electromotor；And work as in cylinder and be in
When power stroke initiates, also due to volume of cylinder is to start to be slowly increased so that combustible oil gas mix in cylinder from its minima
More abundant with thing burning, just can produce higher inner pressure of air cylinder peak with crankshaft connecting rod type internal combustion engine same fuel oil supply
Value, thus increased the circulation work(of electromotor, and improves the waste gas discharge of electromotor.Thus the present invention can reduce engine oil
Consumption, thus improving fuel economy, and improves engine exhaust emission.
Multiple thermodynamic cycle indicator cards shown in from Figure 27（P-v schemes）On see, preferable constant volume cycle（With beading fine line I
Represent）The area surrounding on indicator card is maximum, represents that the unit working medium generation circulation work(under preferable constant volume cycle is maximum, bent axle
Connecting rod type internal-combustion engine actual cycle（Represented with thick dashed line III）The area surrounding on indicator card is minimum, represents in crankshaft connecting rod type
Unit working medium generation circulation work(under combustion engine actual cycle is minimum, the actual cycle of the present invention（Represented with heavy line II）Showing work(
Although the area surrounding on figure surrounds area, actual cycle the enclosing on indicator card of the present invention less than preferable constant volume cycle
Area is substantially much bigger than crankshaft connecting rod type internal combustion engine actual cycle surrounding on indicator card to become area, thus the heat of the present invention
Power circulation is more prone to the high preferable constant volume cycle of the thermal efficiency, and the Actual cycle work of the present invention is more real than crankshaft connecting rod type internal combustion engine
Border circulation work(substantially increases, thus being conducive to the obvious reduction of engine consumption, improves fuel economy.
Four stroke crankshaft connecting rod type internal combustion engines relatively, this factor can bring about 40% circulation work(incrementss for the present invention.
Secondly, according to relevant information, in crankshaft connecting rod type internal combustion engine inner carrier reciprocatory movement, between piston and cylinder wall
Friction loss, consume the 10%-20% of cycle of engine work(.In the piston body rotation process of the present invention, piston body and combustion
Burn the friction loss very little of body shell body etc., be substantially negligible and disregard.Thus invention increases the net output work of electromotor,
Substantially reduce engine consumption, improve fuel economy.
Four stroke crankshaft connecting rod type internal combustion engines relatively, this factor can reduce by about 15% circulation work(loss amount for the present invention.
Again, compared with triangle rotor type electromotor.Equal during relative motion between all parts of present invention composition cylinder
For face contact.The sealing of therefore cylinder is easily realized, good sealing effect, and cylinder leakage tester loss when electromotor runs is little, thus
Engine consumption can be reduced, improve fuel economy, improve engine exhaust emission.
The oil consumption level of the present invention can be reduced to about four stroke crankshaft connecting rod type internal combustion engines by total above-mentioned items factor
60%.
2nd, the power to weight ratio of electromotor can be greatly improved.The present invention mainly realizes this by following technological approaches should
Use effect：
First, with respect to crankshaft connecting rod type internal combustion engine, the throttle valve structure that the present invention need not be complicated；Drive mechanism is also by body
Amass the gear structure that the big crankshaft rod structure of big weight has changed over compact conformation；Air cylinder structure also obvious densification.?
Under same displacement volume, the present invention can have substantially little many volume and weights, therefore can improve the power to weight ratio of electromotor.
Four stroke crankshaft connecting rod type internal combustion engines relatively, this factor can bring about 20% loss of weight amount for the present invention.
Secondly, the power output gear axle of the present invention rotates two weeks, four cylinders respectively complete once to include air-breathing, compression,
Acting, the thermodynamic cycle of four strokes of aerofluxuss, the thermodynamic cycle quantity of the present invention with rotating speed with number of cylinders four stroke bent axles
Connecting rod type internal-combustion engine is identical, but net in view of the thermal efficiency height of the present invention, cylinder scavenging efficiency height, the little output of mechanical friction loss
The favorable factor such as power is big, the therefore power output of the present invention than same rotating speed with discharge capacity four stroke crankshaft connecting rod type internal combustion engines
Greatly.
With regard to the cylinder scavenging efficiency of the present invention, with the crankshaft connecting rod type combustion chambers of internal combustion engines volume shown in Figure 26 and table 2
Change-time relationship characteristic is compared, the combustion chamber volume change-time relationship characteristic of the present invention shown in Figure 25 and table 1, shows this
The volume of cylinder of invention changes very slow when it is minimum or maximum.That is, when cylinder is in exhaust stroke and ends, now
Air vent diminishes, and the slow volume of cylinder of the present invention reduces speed and is beneficial to aerofluxuss fully, and reduces exhaust process air-flow damage
Lose；When cylinder is in intake stroke and ends, now air inlet diminishes, and the slow volume of cylinder of the present invention gathers way and also will have
Beneficial to suction more fresh oil gas mixture, and reduce breathing process windage loss.This is beneficial to improve engine breathing
Efficiency, the also raising gain to engine thermal cycle efficiency.
Four stroke crankshaft connecting rod type internal combustion engines relatively, this factor can bring about 1.65 times of power gain for the present invention.
Finally, compared with existing crankshaft connecting rod type internal combustion engine, all driving members of the present invention are all axialy symmetric part, thus
Electromotor is allowed to have higher limit speed；From the point of view of the efficiency of combustion of electromotor, Figure 25（Table 1）Shown combustor of the present invention
Volume change-time relationship characteristic also will be helpful to electromotor and is maintained to higher efficiency of combustion at high speed.Cause
This, 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
When other need the application of high power to weight ratio, the power to weight ratio of electromotor can be greatly improved by improving the rotating speed of electromotor.
The power to weight ratio of the present invention can be brought up to the four stroke crankshaft connecting rod types about with rotating speed by total above-mentioned items factor
2.1 times of internal combustion engine.
3rd, engine structure is simple, and anufacturability is good.The present invention mainly realizes this by following technological approaches should
Use effect：
First, the building block of the present invention is few, does not have the complicated throttle valve structure of crankshaft connecting rod type electromotor and bent axle to connect
Bar structure etc..
Secondly, manufacturing and designing of each building block of the present invention all has ripe technological procedure, no special fabrication processes
The transmission of the parts requiring, such as oval gear is widely used in terms of textile machine and agricultural machinery etc., spark plug fuel injector skill
Art and cylinder seal technology all can use for reference the mature technology of crankshaft connecting rod type internal combustion engine, etc..
4th, engine luggine and noise level are low, smooth running, and moving component is few, thus the electromotor working service life-span
Long.The present invention mainly realizes this application effect by following technological approaches：
First, compared with existing crankshaft connecting rod type internal combustion engine, each moving component of the present invention is all axialy symmetric part, can have
Effect avoids various vibrations and the noise that moving component caused due to mass unbalance, and electromotor smoothness of operation is good, working service
Life-span length.
Secondly, as shown in figure 24, each movement transmission members of the present invention, its instantaneous transmission ratio consecutive variations is everywhere in theory
More than single order can lead, no rigid shock therefore between drive disk assembly, also no soft impulse；And the transmission of each movement transmission members
Journey can be good with the pressure change process compatible of cylinder interior gas, causes due to being driven impact so as to be prevented effectively from moving component
Various vibrations and noise.Electromotor smoothness of operation is good, working service life-span length.
Finally, the building block of the present invention is few, and moving component is few, and friction loss is little, does not have crankshaft connecting rod type electromotor
Complicated throttle valve structure and crankshaft rod structure etc., therefore breakdown in the motor rate is low, working service life-span length.
5th, engine structure is compact.The present invention mainly realizes this application effect by following technological approaches：
With respect to crankshaft connecting rod type internal combustion engine, the present invention does not have the throttle valve structure of complexity, and drive mechanism is also big by volume
The big crankshaft rod structure of weight has changed over the gear structure of compact conformation, air cylinder structure also obvious densification.Therefore, exist
Under same displacement volume, the present invention can have substantially much smaller volume and weight, on the whole compact conformation, can be preferably applicable
In electromotor overall size is required strict aircraft power plant and ground racing car, Future population dense city small-sized
Change the application scenarios such as ground traffic toolses.
6th, engine power output torque is big.The present invention mainly realizes this application effect by following technological approaches：
The power output gear axle of the present invention rotates two weeks, four cylinders respectively complete once to include air-breathing, compression, acting,
The thermodynamic cycle of four strokes of aerofluxuss, thermodynamic cycle quantity is identical with the crankshaft connecting rod type internal combustion engine of number of cylinders with rotating speed,
But consider the favorable factors such as the thermal efficiency height of the present invention, cylinder power per liter are high, mechanical friction loss little output net power is big.Cause
The power output torque ratio of this present invention is bigger than normal with the crankshaft connecting rod type internal combustion engine of discharge capacity with rotating speed.
The power output moment of torsion of the present invention can be brought up to the four stroke bent axles about with rotating speed by total above-mentioned items factor
1.65 times of connecting rod type internal-combustion engine.
7th, the multiple design parameter of electromotor can adjust.The present invention mainly realizes this application effect by following technological approaches
Really：
Such as, increase and decrease the fan-shaped angle of inventive piston body, the ideal theoretical compression ratio of changeable electromotor；Change the present invention
The eccentricity of each oval gear, can change the maximum cylinder volume of electromotor, etc..
8th, the structure design only needing very little adjusts, and the present invention can change into high performance pump.The present invention mainly passes through
Following technological approaches realize this application effect：
For embodiments of the invention 1 and embodiment 2 it is only necessary to spark plug/fuel injector 7 on burning chamber shell 5
At installing hole, setting is symmetrical in the another set of porting of existing porting, you can the present invention is changed to pump；For the present invention
Embodiment 1 and embodiment 2, can also by the complete roller gear of the roller gear of cylindrical gear shaft 13 and first gear axle 8,
Its pitch circle radius ratio changes into 1:1, two incomplete roller gears 81,82 of first gear axle 8, its continuous gear teeth all changes
The continuous gear teeth for one section of semi-circumference length；Simultaneously by two incomplete roller gears 91,92 and first circle of second gear axle 9
Stud wheel 11 and the second roller gear 12, its pitch circle radius ratio all changes into 8:5；, you can the present invention is changed to pump.
The pump being changed by embodiments of the invention 1 and embodiment 2, compact conformation；Flow is big；Boosting capability is strong；With
When, because the cylinder body volume change-time relationship characteristic of the present invention shown in Figure 25 and table 1 is so that this pump can be opened in fluid inlet
Close initial stage circulation area little in the case of allow relatively low fluid inlet pressure, this pump can also effectively relax fluid issuing opening and closing
Cylinder interior pressure impact phenomenon under the conditions of initial stage small circulation area.Thus, the pump being changed by the present invention, multiple performance refers to
Mark is all higher.
Claims (4)
1. double-piston rotary internal combustion engine, including the first rotor, cover plate, the second rotor, dish, burning chamber shell and gear
Case it is characterised in that：The first rotor is Y-shaped, is made up of rotating shaft disk, first piston body and the first gyroaxis, rotating shaft disk one side
It is provided centrally with the first gyroaxis, rotating shaft disk another side is provided with two first piston bodies around the first gyroaxis axisymmetrical, the
The axle head of single-revolution axle is provided with keyway, and the axle center of the first gyroaxis is provided with axis hole；
Cover plate is discoid, and the middle setting of cover plate has the boss with central through hole, and the periphery of cover plate is provided with chimb；Cover plate
Bottom surface is connected with first piston body end face；
Second rotor is T-shaped, is made up of the second gyroaxis and second piston body, and one end of the second gyroaxis is symmetrically arranged with two
Second piston body, the termination of the other end of the second gyroaxis is provided with keyway, and first piston body is straight with the periphery of second piston body
Footpath is equal；
The dish axle center of dish is provided with axis hole, and the two ends of dish axle are connected with end plate and lower end plate, upper end plate periphery and lower end
Disk periphery is provided with screw；Second gyroaxis is threaded onto in the axis hole of the first gyroaxis, the first gyroaxis and the second gyroaxis
All it is threaded onto in the axis hole at dish axle center, first piston body and second piston extracorporeal set combuster housing；
Burning chamber shell is provided with ring flange in peviform, the periphery at the room bottom of burning chamber shell, and ring flange is provided with screw, combustion
Burn room housing periphery and be provided with porting, on burning chamber shell, the offside of porting is provided with the assembling of spark plug/fuel injector
Hole, spark plug/fuel injector is fixedly installed in pilot hole；The upper end plate of dish is adjacent with the rotating shaft disk of the first rotor, dish
The screw of upper end plate be bolted with the screw of burning chamber shell ring flange；
Gear-box is in peviform, and its bottom middle setting has axis hole, and the periphery of gear-box upper end case mouth is provided with ring flange, ring flange
It is provided with screw and the lower end valve snail hole with dish is bolted；Gear-box bottom 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, and power output gear axle is provided with one
Oval gear and a roller gear, the oval gear on power output gear axle is nibbled with the oval gear on oval gear axle
Close, the roller gear on power output gear axle is engaged with the roller gear in cylindrical gear shaft；It is provided with first gear axle
One complete roller gear and two incomplete roller gears, second gear axle is provided with an oval gear and two not complete
Wholecircle stud wheel；Roller gear in cylindrical gear shaft is engaged with the complete roller gear on first gear axle；Oval gear axle
On oval gear engage with the oval gear on second gear axle；The shaft with keyway end of the second gyroaxis and the first gyroaxis is all
In gear-box, equipped with the first roller gear, the axle head of the second gyroaxis is equipped with the second Cylinder Gear for the axle head of the first gyroaxis
Wheel, the first roller gear is replaced with the incomplete roller gear of first gear axle and the incomplete roller gear of second gear axle to be nibbled
Close, the second roller gear is replaced with the incomplete roller gear of first gear axle and the incomplete roller gear of second gear axle to be nibbled
Close.
2. double-piston rotary internal combustion engine according to claim 1 it is characterised in that two of described first gear axle not
The gear teeth of roller gear completely are axially complementary.
3. double-piston rotary internal combustion engine according to claim 1 it is characterised in that two of described second gear axle not
The gear teeth of roller gear completely are axially complementary.
4. double-piston rotary internal combustion engine according to claim 1 is it is characterised in that described dish can be single-layered disk
Face, card middle setting has axis hole, and card periphery offers screw.
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| Application Number | Priority Date | Filing Date | Title |
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| CN2313052Y (en) * | 1997-05-08 | 1999-04-07 | 吴素良 | Dual-rotating non-linear drive piston-type internal combustion engine |
| US6994071B2 (en) * | 2002-05-17 | 2006-02-07 | Schwam Paul A | Two-cycle engine for counter-rotation especially for aviation applications |
| US7703433B2 (en) * | 2007-02-28 | 2010-04-27 | Richard Colman Webster | Rotary internal combustion engine and rotary compressor |
| CN101196124B (en) * | 2007-08-08 | 2010-09-08 | 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 |
| CN104153881B (en) * | 2014-08-02 | 2016-06-29 | 熊薇 | The differential drive mechanism of internal combustion engine |
| CN104533608B (en) * | 2014-12-24 | 2016-08-17 | 唐仁杰 | Double-piston rotor internal-combustion engine |
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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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