CN101922347A - Double-rotation four-cycle piston type double-shaft internal combustion engine, pressure flow driver and pump - Google Patents
Double-rotation four-cycle piston type double-shaft internal combustion engine, pressure flow driver and pump Download PDFInfo
- Publication number
- CN101922347A CN101922347A CN2010102462187A CN201010246218A CN101922347A CN 101922347 A CN101922347 A CN 101922347A CN 2010102462187 A CN2010102462187 A CN 2010102462187A CN 201010246218 A CN201010246218 A CN 201010246218A CN 101922347 A CN101922347 A CN 101922347A
- Authority
- CN
- China
- Prior art keywords
- double
- shaft
- combustion engine
- rotation
- piston
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Abstract
The invention discloses a double-rotation four-cycle piston type double-shaft internal combustion engine, a pressure flow driver and a pump. The double-rotation four-cycle piston type double-shaft internal combustion engine comprises barrel-shaped cylinders, cylinder covers, a crankshaft, a sleeve shaft, rotary pistons, a control shaft and elliptical gears, wherein two groups of the rotary pistons perform reciprocal acceleration and deceleration sinusoidal rotation at an average rotation speed value in a regular rule during work under the control of the control shaft and two groups of the elliptical gears of the same type connected in series with the control shaft; and each cylinder finishes the same four-stroke work in every cycle. The problem of inversion or stillness of the rotary piston does not exist, the acceleration and deceleration smooth transition and corresponding equilibrium conversion between impulse and momentum are realized, and an output or input shaft, namely, the control shaft structurally and stably rotates at a uniform speed; a composite integral structure of the rotary piston solves the problem of requirement on the strength under the conditions of higher rotation speed, high compression ratio and high working pressure; and normal work and operation of the rotary piston are ensured by axial oil supply lubricating technology, limiting self-running-in sealing technology and heat insulating technology. The engine has the advantages of simple structure, high strength, high power, high efficiency and capability of replacing the conventional internal combustion engines in all fields.
Description
(1) technical field
The present invention adheres to technical field of internal combustion engines, fluid dynamic machinery and pump field separately, particularly rotary piston type internal combustion engine field, rotary pressure fluid dynamic machinery and rotary-piston type pressure pump field.
(2) background technique
Motor commonly used at present remains the crankshaft-link rod stroke piston combustion engine of one-hundred-year history, owing to its working principle and structure reason have shortcomings such as unsurmountable efficient is low, volume is big, rotating speed is low, weight is big.In decades, in the world wide, people are making great efforts exploitation always the rotary piston type internal combustion engine of great potential and premium properties, and has manufactured experimently two kinds of representational testing machines, but because multiple key technology fails to solve, is not widely used.
A kind of is triangular rotor rotary piston RC engine (wankel formula) and since this type machine actual make to selection, processing very harsh and wearing and tearing greatly and can't overcome structural defect---inlet and outlet are not smooth, do not obtain and apply.
Another kind is from just disclosed double-rotation four-cycle piston type internal-combustion engine of five sixties of last century: second the 324th page-327 pages of the mathematics, physics and chemistry self-study series of publishing referring to front page Shanghai science tech publishing house in 1964 " physics ", experiment shows that this type compares and have good performance, power big (3.6 times), oil consumption low (1/3), (about 0.5kg/kw) in light weight, rotating speed wide (60 rev/mins-4000 rev/mins), but, because the imperfection of control and supporting technology fails to succeed in developing and the extensive stroke piston combustion engine that falls behind that replaces so far.Though constantly the someone makes great efforts research around here, but still far apart from practical application.
The patent No. is that the Chinese patent of ZL200820223472.3 discloses a kind of double-rotation four-cycle piston type internal-combustion engine, has adopted unidirectional swivel bearing and cam, brake pad etc. to solve rotary-piston reversing and speed difference problem aspect control; Application number is that 200610075922.4 application for a patent for invention discloses a kind of double rotating four-circulating rotary piston type engine, has adopted the control gear of expansion bend and two rotors.
More than up-to-date prior art scheme deficiency have: though one be that two pairs of rotary-pistons can not reverse and exist stall, and rotation speed change is that discontinuity changes, and parts bear that torsional shear power is big, vibratility is big.The 2nd, no matter from arbor or the direct outputting power of sleeve, rotating speed all is unsettled, try to achieve the output rotation steadily if utilize the principle of inertia device, must strengthen the discontinuity rotation speed change that another institute's connection rotary-piston and parts double, also caused four cylinders, corresponding working stroke time of piston go up, the difference of the difference on the speed and power, thrust, vibrations strengthen.The 3rd, problems such as how parts intensity guarantees under high rotating speed, high-power, the acceleration and deceleration working state, and relevant supporting technology more systematicness solve! Therefore up to the present, have the outstanding type that premium properties like this and great development future promptly have a replacement potentiality and still exist only in people's the expectation, be present in the research!
The particularly continuation of worldwide energy crisis and promptly want energy-saving and emission-reduction not stop paying out sharp-pointed day by day today of contradiction of exhibition again, eliminate be widely used and the poor efficiency of enormous amount, heavy stroke piston combustion engine more apparent urgent!
(3) summary of the invention
The present invention has many-sided premium properties and is specially adapted to aircraft at the double-rotation four-cycle piston type internal-combustion engine is potential just; and research for many years; breaking out and the energy-conserving and environment-protective urgency of worldwide energy crisis in recent years particularly again; promoted the research of the outstanding type of this worldwide internal-combustion engine replacement task of will bearing the responsibility; under the long-time continuous tackling key problem; at the rotary-piston of most critical rationally, accurately aspect the control and be applicable in higher rotating speed, more high-power aspect and multinomial supporting technology and the multi-field application, obtain breakthrough.
Its technological scheme is as follows:
It comprises tubular machine cylinder 4, end cap 5, arbor 1, sleeve 2, rotary-piston a-b, c-d, its key technology be the two pairs of rotary-piston acceleration and deceleration of control rotation be elliptic gear group and Control Shaft and bearing.Embodiment has adopted two groups of homotype elliptic gears that are connected in series by Control Shaft 6 to 8-11; And by Control Shaft as output or input shaft, export or be input as at the uniform velocity rotation; Piston is an integrated type composite piston 3,17; Piston lubrication is finished by axle center oil supply system 7.12.16 etc.; Seal arrangement is limit-type from break-in diaphragm seal 18; Rotary-piston double face and two end cap inboard are provided with thermal-protective coating 13,14.
The beneficial effect of comparing internal-combustion engine of the present invention with background technique is:
1, under the two rotary-pistons speed difference control gear control that mainly is made of oval tooth axle group and Control Shaft, it is the sinusoidal curve of rounding off that the acceleration and deceleration of rotary-piston change, and rotary gadget inertia shearing stress is little, shakes little.
2, be provided with and be parallel to the Control Shaft 6 of arbor 1, and by two groups of elliptic gear 8-11 of its control two integrated type rotary-pistons that are connected in series across machine cylinder two ends, the one, solved difference control of two rotary-pistons speed and high-power, high pulling torque to the parts strength demand; The 2nd, solved the masty rotary-piston of a pair of elliptic gear to high speed difference and big compression ratio needs, improve effective cylinder and held ratio, reduced rotary-piston dead volume and quality; Three because of compression power be derived from before cylinder outburst adapted to the multiple fluid demanded fuel; The 4th, more solved steady rotating speed difficult problem of output, output shaft promptly is a Control Shaft, is in all the time on the complementary fully mean value of two groups of opposite property of rotary-piston acceleration and deceleration, belongs to Structural Characteristics, power output is steadily at the uniform velocity to rotate output, sees Figure 15.
3, be steady rotating speed pto with Control Shaft, also realized simultaneously four pistons work weekly in the acceleration and deceleration of identical rule change, promptly four cylinder suction, compression, acting, exhaust stroke are under accurate positioning control, it is identical that time, cylinder are held change curve, working thrust is also identical, and output steadily.
4, momentum transformed to momentum and sees Fig. 3-Fig. 4 under rotary-piston and run-in synchronism parts quickened to promote in the cylinder outburst acting stage, kinetic energy increases and stores, but this moment is because elliptic gear group transmission characteristic, externally see Fig. 8-Fig. 9 for opposite reducing property of ratio transmission this moment, and output shaft is subjected to is to continue that at the uniform velocity property is push-jump; Later stage and exhaust phase are seen Fig. 4-Fig. 6 to doing work, the synchronous parts deceleration of rotary-piston and gear spinning momentum becomes momentum, kinetic energy discharges, though rotary-piston is slowing down but owing to be output as opposite ratio this moment and increase the property transmission and see Fig. 9-Figure 11, output shaft is subjected to remains at the uniform velocity property promotion.Be that each piston monomer turns the output shaft duration of work at it, the supply of moment of torsion is relatively stable.
5, as can be known: each push-jump angle of single piston work is 2 alpha+betas by last, see Fig. 8-Figure 11, much larger than 90 ° of the average operating angles of single piston (360 °/4) on every Thursdays, promptly output shaft is stressed in weekly is overlapping, is in free of discontinuities, stablizes rotary work under the Driving force.
6, there be not the anti-reversing and the static problem of rotary-piston under the prior art in the present invention.The one, because cylinder is when the outburst acting, though the just commentaries on classics thrust and the deboost that act on respectively on former and later two rotary-pistons equate, but because the controlled elliptic gear contact points that is located by connecting respectively to an axle centre distance difference is separately seen Fig. 8-Fig. 9, so moment difference-lever principle, under the promotion engagement of forward torque difference, do respectively that forward quickens and the rotation of slowing down, and all be that complementarity is superimposed upon on the mean speed value and carries out, Figure 15 is not seen in reversing or stall.The 2nd, the huge rotating inertia force of rotary gadget has guaranteed to be in the orientation rotation at an only equalising torque point place of compression terminal point, sees Fig. 3,5,7 and corresponding diagram 8,10,12.The 3rd, the regular rotation of rotary-piston forward has also been guaranteed in the overlapping existence at last described push-jump angle.
7, each work of rotary-piston the lubricated of face that trackslip solved by hollow arbor or sleeve and corresponding oil duct 6,12,7 oil supply systems, and simple, reliable, easy row is seen Fig. 1, Fig. 2.
8, the sealing problem of rotary-piston, solved from break-in diaphragm seal assembly 18 by limit-type: the cross section is the inverted T-shaped diaphragm seal, is equipped with below in big, the young slot in the end of axially offering that spring sheet is placed in the piston corresponding site, sees Figure 14.The one, efficiently solve the sealing of new installation; The 2nd, reduced matching gap and surface Machining required precision between machine cylinder and the rotary-piston body; The 3rd, diaphragm seal is limited after certain phase break-in, use no longer ejects, and has realized motive sealing and nothing friction, zero wearing and tearing, low power consuming ideal effect under the lubricating status, and the internal-combustion engine mechanical efficiency is further improved, and operating life greatly prolongs.
9, rotary-piston and two end cap inboard are provided with thermal-protective coating 13,14, see Fig. 1, Fig. 2, Figure 14, have reduced the parts caloric receptivity, have guaranteed the needed low operating temperature of parts high strength; And reduced heat loss, improved whole efficiency.
10, double-rotation four-cycle piston type double-shaft pressure flow driver of the present invention and pump (Figure 16), have that flow is big, efficient is high, pressure is big, volume is little, in light weight, advantages such as fault is few, long lifetime, purposes is wide: as excavator pressure pump, mine, fire-fighting high-pressure water pump etc. and structure extremely the multiple hydraulic pressure of letter pass and drive.
11, in sum, internal-combustion engine of the present invention has higher efficient, higher working strength, higher rotating speed and power, power output more stably, lower rate of fault, longer operating life, and simple in structure, easy manufacturing, with low cost.Be suitable for multiple liquid, gas fuel, and the adaptive different compression ratio fuel of same type machine, easy to adjust.Typing exploitation easily, power range is wide, and I is not enough kilowatt, greatly can up to ten thousand kilowatts.Not only will eliminate the existing multi-field reciprocating internal combustion engine that is widely used in, more be applicable to power-weight ratio requirement height, to tight national defence, the military machinery of less trouble long lifetime requirement, as tank, Hovercraft, warship, helicopter, light airplane, individual lift device etc.
12, the performance characteristic of near-zero wearing and tearing of the present invention, be equipped with existing internal-combustion engine EFI, big compression ratio mature technology, working speed is wideer, be expected to reach 60 rev/mins-10000 rev/mins, add that upper volume is little, the plentiful deposit of power under the big advantage of power, be applied to vehicle " low load with strong power ", can simplify cost height, complex structure, vitals-gearbox that rate of fault is high fully, become only have retreat, neutral gear and advance and only divide unloaded and the heavy duty pure stepless speed-varying vehicle of totally four gears.As use in conjunction of the present invention in vehicle: only be connection with the pipe, each wheel is independent to drive maneuverability according to order; And do not heighten because of there being " back axle " case potential drop low capacity.
13, beneficial effect is comprehensively looked forward to, timely protection exploitation of the present invention and popularization, and its value is immeasurable, has the strategic value on the national interests, will draw the leap sexual revolution progress of having led a plurality of association areas of internal-combustion engine.
(4) description of drawings
Fig. 1 is an integrated type rotary piston structure schematic representation.
Fig. 2 is embodiment's structure section schematic representation.
Fig. 3-Fig. 7 is rotary-piston and cylinder working procedure schematic representation.
Fig. 8-Figure 12 is the oval control gear view of corresponding diagram 3-Fig. 7 cylinder, pistons work.
Figure 13, Figure 14 are elliptic gear, controlled rotary-piston variable quantity schematic representation.
Figure 15 is the two groups of opposite property of piston acceleration and deceleration speed, time response curve synoptic diagram.
Figure 16 is double-rotation four-cycle piston type double-shaft pressure flow driver and (pressure) pump schematic representation.
(5) embodiment
Below in conjunction with accompanying drawing specific embodiments of the invention are described in detail.Among Fig. 1, Fig. 2 the 3, the 17th, integrated type rotary piston structure schematic representation, its monolithic construction has guaranteed requirements of one's work under high rotating speed, the high pulling torque.Arbor 1 is that multidiameter shaft and sleeve 2 are the equal strength structure on transmit machine intensity, has guaranteed the control and the output intensity needs of two pairs of rotary-pistons.The gear shaft of 15 and 6 consubstantialities can be obtained the intensity transmission maximum, does not increase to take up space, and exports supporting effect easily.
Among Fig. 2, arbor 1, sleeve 2 are concentric slip socket configuration, are that output shaft 6 is parallel with Control Shaft.Elliptic gear 9 engagements that are located by connecting on elliptic gear 8 that sleeve 2 is located by connecting and the Control Shaft in pairs; Elliptic gear 11 engagements that are located by connecting on elliptic gear 10 that arbor 1 is located by connecting and the Control Shaft in pairs; And 9 and 10 install for Vertical location on Control Shaft.Promptly two groups of elliptic gear 8-9,10-11 become tandem to connect by Control Shaft.Elliptic gear 8 major axis are connected with rotary-piston c-d major diameter Vertical location; Elliptic gear 11 is connected with rotary-piston a-b Vertical location.The 7th, the axle center is for lube plant.
Fig. 3-Fig. 7 is the single piston Rotate 180 of a present invention ° work schematic representation.O
1, O
2Difference corresponding integrated type rotary-piston a-b, c-d.
Fig. 3 is that cylinder compresses ends between a, the c, sprays into fuel or ignition operation state, outburst acting beginning; Cylinder suction finishes, compresses beginning between b, the c; The depressed bundle of cylinder block, air-breathing beginning between b, the d.Under this state, two rotary-pistons are in the average rate state of value in the middle of the acceleration and deceleration respectively, and corresponding control gear working state is seen schematic representation 8.O
1, O
2The speed value is identical.
Fig. 3-Fig. 4 is between a, the c in the cylinder outburst acting, and rotary-piston a-b is accelerated to the most at a high speed by the average rate value, and rotary-piston c-d is by the average rate value speed that minimizes; Cylinder is in compression between b, the c, and cylinder is air-breathing between b, the d; Cylinder is in exhaust between a, the d.Corresponding control gear working state is seen Fig. 8-Fig. 9.O
1Rotating speed is increased to the highest by average rate, O
2Minimize by average rate.
Fig. 4-Fig. 5, cylinder reaches maximum between a, the c, and the acting of expanding ends, and exhaust begins; Rotary-piston a-b reduces to the average rate value, and rotary-piston c-d speedup is to the average rate value.Cylinder compresses ends between this moment b, the c, and cylinder holds minimum, in spray fuel or the igniting, and outburst acting beginning; Cylinder suction ends between b, the d, the compression beginning; The depressed bundle of cylinder block between a, the d, air-breathing beginning, corresponding state of a control is seen Figure 10.O
1Reduce to average rate, O
2Increase to average rate.
Fig. 5-Fig. 6, in the cylinder exhaust, rotary-piston a-b rotating speed reduces to the slowest between a, the c; Cylinder is in the outburst acting between b, the c, and rotary-piston c-d speedup is to the fastest; In the cylinder compresses, in the cylinder suction, corresponding state of a control is seen signal Figure 11 between a, the d between b, the c.
Fig. 6-Fig. 7, the cylinder exhaust ends air-breathing beginning between a, the c; Rotary-piston a-b increases to average rate, and rotary-piston c-d reduces to average rate; The cylinder acting finishes between b, the c, and exhaust begins; Cylinder compresses ends between b, the d, in spray fuel or the igniting, and outburst acting beginning; Cylinder suction ends between a, the d, the compression beginning, and corresponding state of a control is seen signal Figure 12.
As can be seen from the figure, when each cylinder turns over a week in tubular machine cylinder, it must experience the stroke of twice compression and twice expansion, from four cylinders, they are simultaneously to carry out exhaust, air-breathing, compression, acting quadrinomial job, in the All Time that rotates a circle, expansion stroke is arranged all.And two pairs of rotary-pistons are subjected to the promotion of twice cylinder expansion stroke respectively in weekly, and promptly output shaft is subjected to four pistons promotions weekly.
Figure 13 is that major axis, minor axis ratio are 5: 3 elliptic gear structural representations.Because elliptic gear bears control and output and rotary-piston acceleration and deceleration alternating shear power, for improving intensity, the preferred number of teeth is few, profile of tooth big, tooth depth low technical scheme: 10 teeth and 14 teeth.Long and short axial ratio is preferably 5: 3-2: 1, and applicable pluralities of fuel and designing requirement.The tooth position be 10 flute profile major axis to for teeth, 14 flute profile major axis to being teeth groove, the transition and conversion of corresponding acceleration and deceleration when alternately doing work that this layout helps its two groups of rotary-pistons controlling.
Two pairs of rotary-piston angle situation of change schematic representation that Figure 13, Figure 14 control when being elliptic gear and work relatively, and referring to Fig. 3-Figure 12.(the job requirement design data is referring to following mode).
A pair of elliptic gear control rotary-piston acceleration and deceleration relative variation is two times (alpha-betas), and promptly 2 (alpha-beta) ≈ is 28 °, and the control variable quantity is after two pairs of elliptic gear overlapped in series: 56 ° of 2 * 28 ° of ≈.
Know that the cylinder work compression ratio is 6, but then notice of invitation piston fan ring cross section entad occupies that the angle amount is 50.8 °, at this moment, when air-breathing or acting end of a period cylinder is maximum, entad occupy that the angle amount is 67.2 °, exhaust or compression end of a period value are 11.2 °.
Driving machine of the present invention and pump machine cylinder have two imports and two outlets, referring to Figure 16 and above content.
Claims (9)
1. double-rotation four-cycle piston type double-shaft internal combustion engine, pressure flow driver and pump, comprise tubular machine cylinder (4), end cap (5), arbor (1), sleeve (2), rotary-piston (a-b, c-d), it is characterized in that controlling the periodically variable device of rotary-piston acceleration and deceleration is elliptic gear and Control Shaft; The machine cylinder of pressure flow driver and pump has two fluid inlets and two outlets.
2. double-rotation four-cycle piston type double-shaft internal combustion engine as claimed in claim 1, pressure flow driver and pump, it is characterized in that elliptic gear is the two groups of elliptic gears of same model (8-11) that are connected in series by the Control Shaft that is parallel to arbor (6), Control Shaft is again the power input shaft of combustion engine powered at the uniform velocity rotating output shaft and pump.
3. double-rotation four-cycle piston type double-shaft internal combustion engine, pressure flow driver and pump as claimed in claim 1 or 2 is characterized in that elliptic gear is: preferred 10 teeth of the number of teeth and 14 teeth (Figure 15); Preferred 5: 32: 1 of major axis, minor axis length ratio; The tooth position is minor axis zenith directions one side of the mid point of major axis summit to minor axis summit segmental arc in these place's teeth, and promptly 10 flute profile major axis are to being that teeth, 14 flute profile major axis are to being teeth groove.
4. double-rotation four-cycle piston type double-shaft internal combustion engine, pressure flow driver and pump as claimed in claim 1 or 2 is characterized in that rotary-piston (a-b), (c-d) are respectively integrated type composite piston (3), (17).
5. double-rotation four-cycle piston type double-shaft internal combustion engine as claimed in claim 1 or 2 is characterized in that rotary-piston bilateral working surface and two end cap inboard are provided with thermal-protective coating (13,14).
6. double-rotation four-cycle piston type double-shaft internal combustion engine, pressure flow driver and pump as claimed in claim 1 or 2, it is limit-type from break-in diaphragm seal (18) to it is characterized in that rotary-piston (3), (17) are provided with.
7. double-rotation four-cycle piston type double-shaft internal combustion engine, pressure flow driver and pump as claimed in claim 1 or 2 is characterized in that arbor (1) or sleeve (2) are for having the hollow shaft (12,16) of radial and axial oil leab.
8. double-rotation four-cycle piston type double-shaft internal combustion engine, pressure flow driver and pump as claimed in claim 1 or 2 is characterized in that arbor (1) is one-sided multidiameter shaft.
9. double-rotation four-cycle piston type double-shaft internal combustion engine as claimed in claim 2, pressure flow driver and pump is characterized in that Control Shaft (6) is the gear shaft (15) in intermediate portion transmission output or input.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010102462187A CN101922347A (en) | 2010-03-03 | 2010-08-06 | Double-rotation four-cycle piston type double-shaft internal combustion engine, pressure flow driver and pump |
| PCT/CN2011/000299 WO2011106989A1 (en) | 2010-03-03 | 2011-02-25 | Dual-rotating four-circulating piston-type double-shaft internal combustion engine, pressure fluid driving machine and pump |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010116340.2 | 2010-03-03 | ||
| CN201010116340 | 2010-03-03 | ||
| CN2010102462187A CN101922347A (en) | 2010-03-03 | 2010-08-06 | Double-rotation four-cycle piston type double-shaft internal combustion engine, pressure flow driver and pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101922347A true CN101922347A (en) | 2010-12-22 |
Family
ID=43337509
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010102462187A Pending CN101922347A (en) | 2010-03-03 | 2010-08-06 | Double-rotation four-cycle piston type double-shaft internal combustion engine, pressure flow driver and pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN101922347A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011106989A1 (en) * | 2010-03-03 | 2011-09-09 | Duan Fangquan | Dual-rotating four-circulating piston-type double-shaft internal combustion engine, pressure fluid driving machine and pump |
| WO2013020362A1 (en) * | 2011-08-10 | 2013-02-14 | Duan Fangquan | Internal cooling and circulated lubrication-model, dual rotary piston-type biaxial internal combustion engine |
| CN109058099A (en) * | 2018-09-18 | 2018-12-21 | 江苏钧微动力科技有限公司 | A kind of twayblade vector pump |
| CN114645775A (en) * | 2022-03-18 | 2022-06-21 | 北京理工大学 | Double-shaft supporting device of rotary opposed piston engine |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2244367A6 (en) * | 1973-09-19 | 1975-04-11 | Boes Jean | Rotary vane type two rotor engine - rotors controlled by non-circular gears form variable vol chambers |
| JPS5851224A (en) * | 1981-09-20 | 1983-03-25 | Koshiro Nakabayashi | Wing shaft rotating device utilizing elliptic gear |
| CN2313052Y (en) * | 1997-05-08 | 1999-04-07 | 吴素良 | Dual-rotating non-linear drive piston-type internal combustion engine |
| CN101063421A (en) * | 2006-04-24 | 2007-10-31 | 周金社 | Double rotating four-circulating rotary piston type engine |
| CN201318213Y (en) * | 2008-12-17 | 2009-09-30 | 杜明辉 | Double-rotation four-cycle piston type internal combustion engine |
-
2010
- 2010-08-06 CN CN2010102462187A patent/CN101922347A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2244367A6 (en) * | 1973-09-19 | 1975-04-11 | Boes Jean | Rotary vane type two rotor engine - rotors controlled by non-circular gears form variable vol chambers |
| JPS5851224A (en) * | 1981-09-20 | 1983-03-25 | Koshiro Nakabayashi | Wing shaft rotating device utilizing elliptic gear |
| CN2313052Y (en) * | 1997-05-08 | 1999-04-07 | 吴素良 | Dual-rotating non-linear drive piston-type internal combustion engine |
| CN101063421A (en) * | 2006-04-24 | 2007-10-31 | 周金社 | Double rotating four-circulating rotary piston type engine |
| CN201318213Y (en) * | 2008-12-17 | 2009-09-30 | 杜明辉 | Double-rotation four-cycle piston type internal combustion engine |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011106989A1 (en) * | 2010-03-03 | 2011-09-09 | Duan Fangquan | Dual-rotating four-circulating piston-type double-shaft internal combustion engine, pressure fluid driving machine and pump |
| WO2013020362A1 (en) * | 2011-08-10 | 2013-02-14 | Duan Fangquan | Internal cooling and circulated lubrication-model, dual rotary piston-type biaxial internal combustion engine |
| CN109058099A (en) * | 2018-09-18 | 2018-12-21 | 江苏钧微动力科技有限公司 | A kind of twayblade vector pump |
| CN114645775A (en) * | 2022-03-18 | 2022-06-21 | 北京理工大学 | Double-shaft supporting device of rotary opposed piston engine |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| WO2003083276A1 (en) | Internal combustion engine and method | |
| CN102434279A (en) | Combustion engine without crank shaft connection rod | |
| CN101922347A (en) | Double-rotation four-cycle piston type double-shaft internal combustion engine, pressure flow driver and pump | |
| US20120291572A1 (en) | Baker Torcor motion conversion mechanism | |
| RU2727821C1 (en) | Pneumatic motor | |
| EP2456966B1 (en) | Constant velocity engine/technology | |
| EP1016785A1 (en) | Eccentric sliding vane equilibrium rotor device and its applications | |
| CN201818361U (en) | Dual-rotation four-circulation piston type double-shaft internal combustion engine, pressure flow driving machine and pump | |
| CN102926863A (en) | Internal-combustion engine with two-phase inner cam shock wave shifting for transmission | |
| CN102269048B (en) | Heat insulation intercooling circulating lubrication double-rotation piston type double-shaft internal combustion engine | |
| CN103423150A (en) | Rotor fluid mechanical transfiguration mechanism | |
| CN110043361B (en) | Cylinder body structure of mixed-action opposed piston and mixed-layer rotor stator engine | |
| CN107304710A (en) | Reciprocating-piston rotary engine | |
| CN106285928A (en) | Piston stops the continuous rotary engine of dynamic formula | |
| CN103047003A (en) | Outside-protruding-inside random tooth difference cam moving type transmission combustion engine | |
| CN202348425U (en) | Internal cooling circulating lubrication type double-shaft internal-combustion engine with double rotary pistons | |
| CN103422981B (en) | The motor of star rotary fluid machinery and application thereof and fluid motor | |
| CN105697144A (en) | Internal-bi-phase cam driven roller needle roller block type internal combustion engine | |
| CN113497498A (en) | Interlink rotor variable displacement pump | |
| CN113719350B (en) | Constant volume electric control combustion coupling engagement engine | |
| CN104595022A (en) | Internal combustion rotor engine | |
| CN211351852U (en) | Interlink rotor variable displacement pump | |
| CN211975158U (en) | Two-dimensional piston engine | |
| CN212296610U (en) | Interlink rotor engine | |
| WO2011106989A1 (en) | Dual-rotating four-circulating piston-type double-shaft internal combustion engine, pressure fluid driving machine and pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20101222 |