CN101696653A - Rotary-wing piston engine - Google Patents
Rotary-wing piston engine Download PDFInfo
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- CN101696653A CN101696653A CN 200910209804 CN200910209804A CN101696653A CN 101696653 A CN101696653 A CN 101696653A CN 200910209804 CN200910209804 CN 200910209804 CN 200910209804 A CN200910209804 A CN 200910209804A CN 101696653 A CN101696653 A CN 101696653A
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- piston
- oil
- rotary
- cylinder body
- clutch
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F01C1/063—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them
- F01C1/073—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them having pawl-and-ratchet type drive
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/008—Driving elements, brakes, couplings, transmissions specially adapted for rotary or oscillating-piston machines or engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
The invention relates to a rotary piston-type engine, in particular to a rotary-wing piston engine. The currently used engine has the drawbacks of complex structure, large noise, large mechanical wear, high specific gravity, incompactness, small torque and small compression ratio. To overcome the drawbacks, the rotary-wing piston engine adopts two groups (A and B) of wing-shaped pistons that are arranged in an intercrossing way and alternately rotate and stop in a cylinder body, wherein each piston group is provided with a unidirectional overrunning clutch and can control the separation and connection of the piston group for the unidirectional overrunning clutch and a main shaft. When any group of pistons rotate an angle, air intaking, compressing, working and exhausting strokes are performed at the same time. At the end of the compressing stroke, the A group of pistons stop just behind the B group of pistons which are to participate in next combustion and working, so the rotating inertia force of the pistons is cushioned. In addition, no such mechanism as a crankshaft connecting rod, an air intake valve and an exhaust valve is used, so the structure of the engine is simple and compact. The pistons exert no impact on the cylinder body during circular rotation, so the mechanical wear is small and the sealing performance is desirable. The compression ratio can be set freely so as to manufacture a gasoline engine or diesel engine.
Description
Technical field:
The present invention relates to a kind of explosive motor, particularly relate to a kind of rotary piston engine.
Background technique:
Now both at home and abroad practical explosive motor mainly contains that conventional engine and triangular piston rotary engine (abbreviation rotary engine) conventional engine efficient are low has only about 40% and weight/power ratio G/Ne height, and power per liter Ne/zVh is low, blowdown is many.Rotary engine seals bad than benefits such as conventional engine G/Ne are low, the compression ratio diesel engine of can not high therefore failing till now to make, output torque is little during with discharge capacity, and therefore usability is not popularized and used not as conventional engine.Invented multiple rotary engine and all do not had practicality for overcoming before the above-mentioned shortcoming people, because joint and the separation problem of its inertial force and piston and main shaft and the reduction of consumed energy efficient, complex structure will obtain the variable volume working room time during structure that piston is walked, stops, walked.
Summary of the invention:
Rotary-wing piston engine of the present invention (be called for short rotor motor) is to be basic design with the rotary-wing piston machine, its rotary-wing piston machine structure is that mainly it intersects two groups of pistons laying wing inside by the cylinder body of sealing, main shaft and clutch, break is formed, its piston machine working medium is liquid state or gaseous state, two groups of pistons of its piston machine rotate in turn and stop, its piston shaft is a hollow shaft, therefore and the same line of axis of main shaft also can rotate by independent circumference, not to the cylinder body impact force, good airproof performance, complete machine oscillation is little, the ratio height of total measurement (volume) and discharge capacity, and clutch and break are formed to walk, stop, the structure of walking is when having solved piston and stopping and the main shaft separation problem.Resistance when any piston rotation stops during with the motor of above-mentioned piston machine principle design is the impact that the firing pressure of working stroke has next time been eliminated the piston rotatory inertia, therefore can the better rotary piston engine of manufacturing property.
The working principle of diesel oil rotor motor is described earlier.
Its structure is A1 and the A3 piston that wing is arranged on A group piston 3 its wheel hubs in the cylinder body 1 shown in Figure 1, B2 and its A of B4 piston that wing is arranged on B group piston 4 its wheel hubs, the B piston set in cylinder body, cross one another lay can only be within two pistons the angle rotation can not surmount and also one group of piston when engaging rotation with main shaft another group piston to separate with main shaft be exactly to do intermittently to rotate, mono-directional overrun clutch 10 is that outer shroud initiatively encircles driven (main shaft 2) in (piston side), be installed in the piston wheel hub, other has controlled mono-directional overrun clutch 42 is ring actives (main shaft 2) in the outer shroud driven (piston side), be installed in the piston hollo axle internal diameter, be exactly A, the B piston set is respectively installed a mono-directional overrun clutch and a controlled mono-directional overrun clutch.
Intake stroke a: starter motor rotates its torque with main shaft 2 and rotates A group piston by the controlled mono-directional overrun clutch that A organizes piston side, this moment, A1 piston rear portion produced negative inspiratory pressure, the pusher dog of air controlled mono-directional overrun clutch 42 when suction port 5 advances that its A1 piston front portion rotates to oil sprayer 8 positions in the cylinder body is stirred the clutch inside and outside ring and is broken away from A group piston is separated with main shaft 2, and A group piston side Brake drum braking is simultaneously stopped the rotation piston and can not be reversed and can only just branch to a piston end surface arc length and end apart from intake stroke.
The controlled mono-directional overrun clutch of B group piston side engaged with main shaft 2 and B group piston and rotates the B2 piston when compression stroke b:A group piston stopped, the anterior air compression of its rear portion air inlet when its piston combustion bowl 9 of its pressurized air promotion A1 piston is just in time to the oil sprayer position to A1 piston rear pin block breaker slot the A1 piston stopped, this moment air compression to the firing chamber in 9 simultaneously the controlled mono-directional overrun clutch pusher dog of B group piston side stir the clutch inside and outside ring and break away from and make B organize piston to separate with main shaft, B group piston side Brake drum braking simultaneously, its piston can not reverse, cylinder body compressed air pressure and temperature raise and can light fuel oil this moment, and compression stroke ends.
Working stroke c:B2 piston compression stroke is at the end speeded up A group piston deceleration and is unclamped, oil sprayer 8 sprays fuel oils simultaneously, its work by combustion promotes the rotation of A1 piston, the A3 piston that connects together also rotates, its anterior air compression rear portion air inlet, the mono-directional overrun clutch 10 in the A group piston wheel hub engages rotating spindle 2 outputting powers simultaneously.
Firing chamber, A1 piston rear portion, exhaust stroke d:A3 piston compression stroke end 9 arrive relief opening 6 and has been begun combustion gas, and its firing chamber 9 has during to the front of scavenging port 62 wind that blower send to sweep residual exhaust gases in the firing chamber by scavenging air pipe 7 in addition.
Work by combustion piston B2 rear portion is next time arrived in the A3 piston front portion that it connected together when normal working of engine e:A1 piston had done work just in time air compression, its pressure promotes its firing chamber of B2 piston and forwards oil sprayer 8 positions to, oil sprayer oil spout simultaneously, oil inflame B2 piston rear portion acting anterior exhaust simultaneously, the B4 piston front portion that connects together makes the air inlet of air compression rear portion next time stroke cycle prepare, just run well after the engine start, air inlet, compression, acting, exhaust is carried out simultaneously, therefore do not need flywheel, this moment, the firing pressure at B2 piston rear portion stopped the rotation the piston A3 that is in the compression stroke end of a period, the rotating inertia force that is A group piston has been eliminated, its A group piston is the same with B group piston sense of rotation, and therefore its A group piston rotatory inertia energy is added in the combustion gas of doing work at B2 piston rear portion raises the efficiency.
The cyclic process of rotor engine charge, compression, acting, exhaust, four-journey is rational in sum.
Below in conjunction with Figure of description diesel oil rotor motor is that example further specifies.
Description of drawings
Fig. 1 is the four-journey fundamental diagram of rotor motor
Fig. 2 is the motor sectional view
Fig. 3 is cylinder body and piston sectional view
Fig. 4 is the cylinder cap sectional view
Fig. 5 is the piston sectional view
Fig. 6 is a cylinder head cooling water road sectional view
Fig. 7 is cylinder cap, cylinder body, piston stereogram
Fig. 8 is piston, controlled mono-directional overrun clutch, Brake drum stereogram
1 cylinder body, 2 main shafts, 3A organizes piston, 4B organizes piston, 5 peripheral inlet ports, 6 peripheral exhaust ports, 7 scavenging air pipes, 8 oil sprayers, 9 firing chambers, 10 mono-directional overrun clutchs, the outlet of 11 cylinder block cooling waters, 12 cooling water channels, 13 cooling water channel walls, 14 cylinder block cooling water imports, 15 cylinder caps, 16 cylinder head gaskets, 17 side inlet ports, 18 end face relief openings, 19 cylinder head cooling water imports, the outlet of 20 cylinder head cooling waters, 21 cooling water channels, 22 strengthening rib, 23 bolts hole, 24 cylinder bolts, 25 cylinder head ring gasket grooves, 26 pistons, 27 piston cavities, 28 right-angle type rotary valves, 29 oilholes, 30 cooling-oil inlets, 31 cooling-oil outlets, 32 piston hollo axles, 33 piston wheel hub gas, the oil seal annular groove, 34 piston seal oilholes, 35 piston oil seal grooves, the airtight sealing groove of 36 pistons, 37 piston seal films, 38 springs, 39 tapped holes, 40 sliding bearings, 41 cylinder bolts, 42 controlled mono-directional overrun clutchs, 43 clutch pusher dogs, 44 levers, 45 sliding discs, 46 Brake drums, 47 screw holes, 48 breaker slots, 49 pins, 50 cams, 51 camshafts, 52 camshaft bearing supporting frames, 53 camshaft bearings, 54 driven gears, 55 shaftgears, 56 oil outlets, 57 actuation gears, 58 fans, 59 bearing bracket stands, 60 main bearings, 61 bearing caps, 62 scavenging ports, 63 piston wheel hubs, 64 arcuate sockets, 65 inclined-plane leg pieces.
It is that cylinder body 1 is to be fixedly mounted on the base that diesel oil rotor motor is mainly formed structure, peripheral inlet port 5 more than 1 or 1 is arranged on its cylinder body, its suction port is connected air-strainer, also have 1 or 1 peripheral exhaust port 6 that above combustion gas is used, peripheral scavenging port 62 more than 1 or 1 and peripheral scavenging air pipe 7, its relief opening is connected outlet pipe with scavenging port, the purposes of scavenging port 62 is that the wind that has blower to send in addition blows out the residual exhaust gases in the piston combustion bowl advance scavenging air pipe 7 backs, its gas port is all apneustic to be open in usual, also has the oil sprayer 8 more than 1 or 1, with fuel oil be diesel oil or biodiesel, its fuel oil is to pump high-voltage tube by high pressure oil pump to go into the oil sprayer oil spout, contact with controlled overrunning clutch inside and outside ring when its injection time is a piston combustion bowl 9 to the position of oil sprayer or the separation time is set, when firing chamber 9 is to the position of oil sprayer as with magnetic clutch the time and its magnetic clutch be switched on or switched off the time and set.
Other has peripheral cooling water intake 14, its cooling water is pumped into from cooling water tank through water pump, and the cooling water channel 12 of inner chamber of cylinder block makes the cylinder body cooling after coolant outlet 11 recovery tanks, equally distributed installation cylinder cap is interior by A with bolt 41 its cylinder bodies on its cylinder body both sides end face, two groups of pistons of B cross one another and lay, its piston hollo axle 32 is to rotate in the internal diameter of the sliding bearing 40 installed on the cylinder cap internal diameter, its A, two groups of piston wheel hubs of B are to respectively there being the annular groove 33 of laying airtight seal ring and oil seal ring on the side, the large diameter closure gasket groove of one side is the hermetic seal annular groove, equidistant erietiform protrusion groove more than 4 or 4 is arranged on its annular groove external diameter, the circular airtight seal ring that the erietiform jut is arranged more than 4 or 4 is laid in the outside in its hermetic seal annular groove, lay the circular seal ring on the inboard in its annular groove, the joint of its seal ring will stagger with the joint that the seal ring of jut is arranged and be placed in its closure gasket groove of major diameter gas, the closure gasket groove of opposite side minor diameter is the oil seal annular groove, its groove is followed the cooling-oil outlet intercommunication by oilhole, its oil seal ring is that each is made up of interior ring and outer shroud more than 1 or 1, the joint of ring staggers mutually and is installed in the annular groove, its gas, spring, the effect of its airtight seal ring and oil seal ring are arranged at oil seal ring bottom is to prevent that gas leaks between two groups of piston wheel hubs in the cylinder body.
The rotor engine piston is A, two groups of pistons of B are formed, including two or more pistons 26 on every group of piston wheel hub external diameter is formed by fixedly connecting, its piston set crosses one another in cylinder body and lays, the axis of its piston hollo axis and main shaft 2 is same lines, piston is the center circumferential rotation at its axis, combuster 9 on its each piston, the oil that two or more hermetic seal film traps 36 and oil seal film trap 35 its oil seal film traps more than 1 or 1 are arranged that interconnects on inner chamber 27 and its periphery and the both sides end face is that the oilhole 34 of inner chamber 27 intercommunications is supplied with, lay the airtight mounting and the oil seal sheet 37 of series connection more than 2 or 2 in its hermetic seal film trap and the oil seal film trap respectively, two of the diaphragm seals of another sample or two are placed in the film trap with the upper connection lamination that staggers mutually, and the effect of its airtight mounting and oil seal sheet is to prevent piston and cylinder body, cylinder cap leaks gas in the gap.
A, each installs the initiatively mono-directional overrun clutch 10 of (piston side) interior ring driven (main shaft 2) of outer shroud with key on two groups of piston wheel hubs of B internal diameter, ring is to fixedly mount with key on the main shaft 2 in it, moment of torsion output usefulness when its mono-directional overrun clutch is the piston acting, its two groups of piston wheel hub outsides respectively connect hollow shaft 32, controlled mono-directional overrun clutch 42 is installed respectively on its internal diameter, the symmetrical concave groove more than 2 or 2 is arranged on its clutch external diameter and in hollow shaft 32 internal diameters, flow out cold oil in its groove, clutch 42 is ring actives (main shaft 2) in the outer shroud driven (piston side), interior ring is to install with key on the main shaft, and its clutch 42 is that main shaft 2 drive piston shaft 32 rotation composition pistons are walked, stop, the intermittent movement of walking.Its controlled mono-directional overrun clutch and mono-directional overrun clutch are to substitute with magnetic clutch, this moment 1 piston set each with 1 magnetic clutch, magnetic clutch corresponding wheel hub or hollow shaft when installing in big therefore piston wheel hub of mono-directional overrun clutch volume or the piston hollo axle are done greatly, install in addition with synchronous switching circuit and the power-supply system of piston rotation, the contact of its switching circuit is installed on pin 49 lower ends, also can substitute the contact switch circuit with piston position sensor and electronic switching circuit.
Stirring of the pusher dog 43 of controlled overrunning clutch 42 is that shaftgear 55 rotations are rotated driven gear 54, on cam 50 rotation promotion pins 49 of installing on its connection camshaft 51, following flatface follower motion, its pin is to install on the camshaft bearing supporting frame 52, its supporting frame is to install on the cylinder cap inner diameter wall, its inclined-plane, pin lower end leg piece 65 promotes sliding disc 45 in the arcuate socket 64 of sliding disc 45, ball is filled in its sliding disc internal diameter both sides, therefore can laterally move, rotate in a circumferential direction, its sliding disc promotes lever 44, its lever is that small angle inclination is installed on the clutch limit, the angle of its lever changes makes the rotation of clutch pusher dog 43 angles, the size of pusher dog angle of swing is that the both sides length of lever is adjusted the controlled mono-directional overrun clutch outer shroud of the rotation that makes pusher dog and separated with interior ring, just realize separating and engaging of piston shaft and main shaft, lever 44 is that return spring is arranged, the effect of its spring be sliding disc when not having thrust lever get back on the origin-location.
Pin 49 its heads are inclined-planes, respectively there is flatface follower the upper and lower, there is swing spring at its pin middle part, the effect of its spring is after cam promotion driven member makes the pin head advance breaker slot, or maintain the original state after going out breaker slot, make piston deceleration in the breaker slot 48 of its inclined-plane, pin lower end leg piece 65 promotion sliding discs its head system driving wheels 46 of while, the front portion of its breaker slot is just identical pin head inclined-plane, inclined-plane, its Brake drum is 39 li of tapped holes that are installed in the piston hollo axial end with screw through screw hole 47, but piston can not reverse just changeing and block again after can forwarding a piston end surface distance to during the braking of its Brake drum, this is because the length of breaker slot is just so long, its effect be piston the compression stroke end do not reverse and also its firing chamber 9 can move to the work by combustion travel position wait for after-combustion begin before its pin go out breaker slot and make braking unclamp piston to rotate, the arc length l of its breaker slot is that thickness a closed before and after the piston end surface arc length ι according to the breaker slot correspondence added pin head inclined-plane, be l=ι+a, during the rotation of A group piston B group piston want braking state just the Brake drum on the both sides piston hollo axle do braking respectively and unclamp action, the adjustment at its action interval is that the velocity ratio of shaftgear 55 and driven gear 54 and each circulation of cam are δ
o+ δ
s+ δ
1 o+ δ
1 sMotion angle for actuating travel δ among=2 π.With far angle of repose δ
sSize adjust setting, the movement process timing of cam, pin and the sliding disc piston stroke of coincideing, rotation starting time of piston be after oil sprayer oil spout last time and next oil spout before the length that stops injection time adjusting.
The driven member of cam mechanism be its cam of flat base member 1 driven member contacting structure is respectively arranged when the upper and lower position is that pin follows cam to move simultaneously, this structure does not have retardation phenomenon than the structure that generally adds the return spring with 1 driven member.
Its motor is to engage and separate main shaft and piston shaft with clutch, its clutch comes rotating spindle, general mono-directional overrun clutch engaging time is about 0.4/s, magnetic clutch is≤0.3/s on time, therefore its motor is a low speed, clutch or clutch time will shift to an earlier date just that the time of stirring of clutch pusher dog will shift to an earlier date faster if the rotating speed that improves motor is just with joint and disengaging time, another kind method is on the main shaft 2 rear portion clutch ends gearwheel to be installed, 1 pair of bearing is installed on the base in addition, the high speed output shaft is installed on its bearing bore diameter, its axle is gone up small gear is installed, its gearwheel and pinion are rotated, the size of its velocity ratio is adjusted the rotating speed of high speed shaft, just the output speed of motor.
To be the same two parts have on equally distributed bolt 41 its bolts corresponding bolt hole 23 that cylinder caps 15 backs in both sides are installed at cylinder body both sides end face to cylinder cap 15 use nut screwing clamping, cylinder head gasket 16 is installed between its cylinder cap and the cylinder body is prevented the interior gas leakage of cylinder body.
On the cylinder cap inner side surface by laying 1 or 1 seal ring of forming with upper inner ring and outer shroud in closure gasket groove 25 its grooves, joint installation of staggering mutually of its two ring, spring is arranged at its seal ring bottom, the effect of its seal ring is to prevent that gas leaks between piston wheel hub and cylinder cap in the cylinder body, sliding bearing 40 is installed on the cylinder cap internal diameter, its cylinder cap exterior edge face, both sides and cylinder body suction port 5, corresponding locates with the both sides side inlet port of counting 17, its suction port 5 and 17 connects with air-strainer, also have cylinder body relief opening 6 corresponding parts to have with the both sides cylinder cap end face relief opening of counting 18, its relief opening 6 and 18 connects outlet pipe, its suction port and relief opening are all apneustic, are open in usual.
The cooling water that other has water pump to pump advances cylinder head cooling water import 19, during cooling water process cooling water channel 21 cylinder cap is cooled off after coolant outlet 20 flows out back cooling water tank, its cylinder cap outside lower and eminence have strengthening rib 22 to make enhancing rigidity, installation shaft bolster 59 usefulness nuts are fixed on two cylinder cap outside bolt 24, interference fit installation main shaft 2 on main bearing 60 its bearing bore diameters respectively is installed in its both sides bearing bracket stand, its rear portion is a clutch end, actuation gear 57 is installed with key in its front portion, its effect is to rotate high pressure fuel pump with the Transmitted chains engagement, water pump, oil pump, generator, the needed machine turns of engine runnings such as blower provides power, these machine parts are installed at the anterior suitable position of motor, main shaft 2 the cooling water that there is its water tank of cooling water tank fan 58 its fronts is installed foremost by water pump suction pipeline, advance each water intake, the connection of water outlet and reflow pipe flows to the circulation of water tank formation cooling water and makes the control of engine body temperature behind cooling cylinder body and the cylinder cap.
Oil cooling but and oil lubrication be in the base oil sump machine oil through pump with oil pump behind the filter screen oil pipe to right-angle type rotary valve 28 advance piston hollo shafting oil hole 29 and through cooling-oil inlet 30 in the piston cavity 27 cooling piston and piston oil closure gasket groove and piston wheel hub oil seal annular groove fuel feeding after export 31 and flow out outward simultaneously to clutch to the concave surface gap more than 1 or 1 between clutch 42 and the piston hollo axle 32, sliding disc, cam, gears etc. are lubricated, the oil that other enters oilhole 29 advances sliding bearing 40 through aperture and is lubricated, and machine oil is lubricated the back to piston cooling and each part and gets back to oil sump from oil outlet 56 and finish circulation.
Cylinder body and cylinder cap, piston are the processing of casting back, the degree of finish of cylinder body, piston and cylinder cap surface of contact
More than 10, piston wheel hub and casting of piston consubstantiality and processing, the piston hollo axle is made the back piston wheel hub with steel more than 45 ° and is connected.
Can use supercharging technology if raise the efficiency, this moment, suction port connect on the pressurized machine ajutage again, and this moment, compression ratio ε was smaller.
The fuel oil of fuel oil gasoline, Aalcohols fuel, gaseous fuel or easy vaporization when the rotor motor is made petrol engine, spark plug changes the outfit after above-mentioned diesel injector will be dismantled herein, its spark plug wiring point ignition system, other installs power-supply system and fuel supply systems such as storage battery, generator, suction port is connected to Carburetor or electric-controlled injection device, and its compression ratio ε will adjust the smaller not combustion gas detonation of catching fire naturally.
Rotor motor of the present invention does not in sum have that connecting rod is little with intake valve, exhaust valve and double-action mechanism so mechanical abrasion, energy loss is little, noise reduces and efficiently solve piston when stopping inertial force and piston separate with main shaft and engage and the rotatory inertia energy utilizes and improved efficient, total measurement (volume) can be made gasoline rotor motor or diesel oil rotor motor with ratio height, power per liter height, body compactness, any setting of compression ratio of discharge capacity.
Claims (10)
1. rotary-wing piston engine, it is characterized in that, with the rotary-wing piston machine is basic design, mainly by base, the cylinder cap of installing on cylinder body (1) and its bi-side (15), the A that intersection is laid in sliding bearing on its internal diameter (40) and the cylinder body, two groups of pistons of B and its both sides Brake drum (46) and braking system, each main bearing (60) of installing of its both sides of its braking control system and main shaft (2), each mono-directional overrun clutch (10) of installing on two groups of pistons, the system of stirring of its clutch pusher dog (43) of controlled unidirectional super clutch (42), its clutch is to substitute with 1 magnetic clutch, fuel supply system, air supply system, vent systems, oil cooling but, oil lubrication system, water cooling system and ignition system, power-supply system is formed, its rotary-wing piston engine can be made petrol engine or diesel engine, can use supercharging technology when needing.
2. rotary-wing piston engine according to claim 1, it is characterized in that, peripheral inlet port (5), peripheral exhaust port (6), scavenging port (62), scavenging air pipe (7) and cooling water intake (14) more than 1 or 1, the cooling water channel (12) that its inner chamber of coolant outlet (11) has cooling water channel wall (13) to separate are arranged on the circumferential surface of the cylinder body of installing on the base (1), and equally distributed installation cylinder cap is with the structure that cylinder head gasket (16) are installed on its cylinder body bi-side of bolt (41) on its cylinder body bi-side.
3. rotary-wing piston engine according to claim 1, it is characterized in that, use nut screwing clamping after having bolt hole corresponding on corresponding its bolt of bolt hole (23) of cylinder body bi-side bolts (41) that the both sides cylinder cap is installed on two the same cylinder caps (15), have with the side inlet port of counting (17) with cylinder body suction port and cylinder body relief opening corresponding part on its each exterior edge face of both sides cylinder cap, end face relief opening (18) and cooling water intake (19), coolant outlet (20), strengthening rib (22), cylinder bolt (24), its cylinder cap inner side surface has the annular groove (25) that airtight seal ring is installed, joint in its groove more than 1 or 1 seal ring that the interior ring laid and outer shroud are formed that staggers, its cylinder cap inner chamber has installs sliding bearing (40) on cooling water channel (21) and the internal diameter, cylinder cap exterior edge face bolt (24) is gone up the structure of installation shaft bolster (59).
4. rotary-wing piston engine according to claim 1, it is characterized in that, intersect in the cylinder body and lay A, two groups of pistons of B, its piston is that the two or more pistons (26) that respectively have that connect on wheel hub (63) external diameter are formed, its each piston rear portion combuster (9) and inner chamber (27), the oil seal sheet that its periphery and both sides end face respectively have interior two or more series connection of its groove of oil seal groove (35) more than 1 or 1 of interconnecting staggers joint and two-layerly or two-layer lays with superimposed layer, other has two or more airtight sealing grooves (36), the airtight mounting of laying two or more series connection in its groove staggers joint and two-layerly or two-layer lays with superimposed layer, A, two groups of piston wheel hubs of B are to respectively having the groove of laying airtight seal ring and the groove (33) of oil seal ring on the side, its large diameter hermetic seal annular groove external diameter has the erietiform protrusion groove, the airtight seal ring of laying the erietiform jut on the outside in its annular groove, lay circular airtight seal ring on the inboard in its annular groove, the joint of two airtight seal ring staggers and lays, the interior two or more oil seal ring joints of the oil seal annular groove of the minor diameter on the opposite side wheel hub side stagger and lay, its wheel hub outside connects piston hollo axle (32), its axle is to install on sliding bearing (40) internal diameter, its axle one side has cooling oilhole (29), its piston hollo axial end has tapped hole (39), piston wheel hub inner chamber is installed in its clutch internal diameter of mono-directional overrun clutch (10) and with key main shaft (2) is installed, the structure that main shaft (2) are installed in its destage device internal diameter of controlled mono-directional overrun destage device (42) is installed in the piston hollo axle internal diameter, two free wheel device is to substitute with 1 magnetic clutch, install power supply and switching circuit this moment in addition, and its switching circuit can be used contact switch circuit or electronic switching circuit.
5. rotary-wing piston engine according to claim 1, it is characterized in that, cylinder body peripheral inlet port (5) and its bi-side cylinder cap side inlet ports (17) connect on air-strainer or the pressurized machine ajutage when being diesel engine, its suction port (5), (17) connect Carburetor or electric-controlled injection device during petrol engine, cylinder body peripheral exhaust port (6) and scavenging port (62), cylinder cap end face relief opening (18) is to connect outlet pipe, and scavenging air pipe (7) is the structure that connects blower.
6. rotary-wing piston engine according to claim 1, it is characterized in that, its main bearing of main bearing (60) respectively is installed on main shaft (2) both sides to be mounted on the bearing bracket stand (59), respectively there is shaftgear (55) its main shaft (2) both sides, its anterior actuation gear (57) of installing, select to engage when wanting high engine speeds and disengaging time is installed gearwheel on clutch or main shaft (2) output terminal faster, pair of bearings is installed on the base, on its internal diameter high speed shaft is installed, its axle is gone up small gear, the structure of its gearwheel and pinion is installed.
7. rotary-wing piston engine according to claim 1, it is characterized in that, pusher dog (43) on the controlled mono-directional overrun clutch (42) is lever (44) one end in contact, the other end of lever is sliding disc (45) contact, the angle of swing size of its pusher dog is that lever both sides length is adjusted, Brake drum (46) is mounted on piston hollo axle (32) end face, it is the inclined-plane that its front portion of two or more breaker slots (48) is arranged on its Brake drum internal diameter, it is the same that the arc length of its breaker slot is that the piston end surface arc length adds the length of closing of pin thickness, pin (49) is that camshaft bearing supporting frame (52) is gone up installation, its supporting frame is to install on the cylinder cap inner diameter wall, its pin head is that the inclined-plane follows the inclined-plane of breaker slot to coincide, respectively there is the flatface follower of cam contact its pin upper and lower, there is swing spring at its pin middle part, its inclined-plane, pin lower end leg piece (65) is moved in the arcuate socket (64) of sliding disc (45), cam (50) is that camshaft (51) is gone up installation, its camshaft connects driven gear (54), the structure of its gear engagement shaftgear (55).
8. rotary-wing piston engine according to claim 1, it is characterized in that, diesel engine is that the oil sprayer (8) more than 1 or 1 is installed on the cylinder body, its fuel oil is that high pressure oil pump is supplied with, can use supercharging technology when raising the efficiency, the spark plug that changes the outfit on this oil sprayer (8) position during petrol engine, compression ratio will be adjusted, in addition mounting points ignition system, power-supply system and fuel supply system.
9. rotary-wing piston engine according to claim 1, it is characterized in that, cooling and lubrication oil are to flow out from right-angle type rotary valve (28) oil inlet hole (29) oil outlet (31) concave surface gap through clutch and piston hollo axle after cooling-oil inlet (30) carries out cooling piston to piston cavity (27) simultaneously clutch, sliding disc, cam, gear to be lubricated, and sliding bearing (40) piston oil seal groove and piston wheel hub closure gasket groove fuel feeding are after the circulation of oil outlet (56) withdrawing oil drain pan in addition.
10. rotary-wing piston engine according to claim 1, it is characterized in that, cooling cylinder body and cylinder cap rear-bank rotor housing coolant outlet (11) and cylinder head cooling water outlet (20) were flowed out when the water cooling water advanced behind cylinder body and the cylinder cap through cylinder block cooling water road (12) and cylinder head cooling water road (21) by pipeline by cylinder body water intake (14), cylinder cap water intake (19), formed cooling water through the pipeline reflux tank and circulated.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200910209804 CN101696653A (en) | 2009-10-26 | 2009-10-26 | Rotary-wing piston engine |
| PCT/CN2010/001694 WO2011050571A1 (en) | 2009-10-26 | 2010-10-25 | Rotary piston engine |
| CN201080006143.3A CN102282347B (en) | 2009-10-26 | 2010-10-25 | Rotary piston engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200910209804 CN101696653A (en) | 2009-10-26 | 2009-10-26 | Rotary-wing piston engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101696653A true CN101696653A (en) | 2010-04-21 |
Family
ID=42141774
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200910209804 Pending CN101696653A (en) | 2009-10-26 | 2009-10-26 | Rotary-wing piston engine |
| CN201080006143.3A Expired - Fee Related CN102282347B (en) | 2009-10-26 | 2010-10-25 | Rotary piston engine |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201080006143.3A Expired - Fee Related CN102282347B (en) | 2009-10-26 | 2010-10-25 | Rotary piston engine |
Country Status (2)
| Country | Link |
|---|---|
| CN (2) | CN101696653A (en) |
| WO (1) | WO2011050571A1 (en) |
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| WO2011050571A1 (en) * | 2009-10-26 | 2011-05-05 | Jin Zhegen | Rotary piston engine |
| CN102213139A (en) * | 2011-05-07 | 2011-10-12 | 苗军 | Double-rotating-blade swinging type engine |
| CN102797558A (en) * | 2012-08-20 | 2012-11-28 | 赛兴嘎 | Rotor engine |
| WO2013020362A1 (en) * | 2011-08-10 | 2013-02-14 | Duan Fangquan | Internal cooling and circulated lubrication-model, dual rotary piston-type biaxial internal combustion engine |
| CN105221254A (en) * | 2015-08-19 | 2016-01-06 | 庞乐钧 | Rotary combustion engine |
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| CN108223116A (en) * | 2017-12-02 | 2018-06-29 | 张英华 | Rotary piston engine and control method |
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| WO2016092379A1 (en) * | 2014-12-10 | 2016-06-16 | Joseph Portelli | A rotary four stroke internal combustion engine |
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| CA1170576A (en) * | 1981-10-07 | 1984-07-10 | Rudolf P. Picavet | Global rotary engine |
| JPH084401B2 (en) * | 1988-06-09 | 1996-01-24 | 信義 金子 | Grass root pruning machine |
| CN1049950C (en) * | 1992-10-12 | 2000-03-01 | 郭仁发 | Rotary engine for self-lifting |
| DE19734783C2 (en) * | 1997-08-07 | 2001-09-13 | Hisham Zakeyh | Rotary piston internal combustion engine |
| CN1102199C (en) * | 1998-05-28 | 2003-02-26 | 聂再安 | Differential rotary piston engine |
| CN2906076Y (en) * | 2006-04-12 | 2007-05-30 | 李兆全 | Piston rotating type four-in-one IC engine |
| JP4131290B1 (en) * | 2007-06-21 | 2008-08-13 | 樹伸 大森 | Cat and mouse internal combustion engine |
| CN101696653A (en) * | 2009-10-26 | 2010-04-21 | 金哲根 | Rotary-wing piston engine |
-
2009
- 2009-10-26 CN CN 200910209804 patent/CN101696653A/en active Pending
-
2010
- 2010-10-25 CN CN201080006143.3A patent/CN102282347B/en not_active Expired - Fee Related
- 2010-10-25 WO PCT/CN2010/001694 patent/WO2011050571A1/en active Application Filing
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| WO2011050571A1 (en) * | 2009-10-26 | 2011-05-05 | Jin Zhegen | Rotary piston engine |
| CN102213139A (en) * | 2011-05-07 | 2011-10-12 | 苗军 | Double-rotating-blade swinging type engine |
| WO2013020362A1 (en) * | 2011-08-10 | 2013-02-14 | Duan Fangquan | Internal cooling and circulated lubrication-model, dual rotary piston-type biaxial internal combustion engine |
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| CN105221254A (en) * | 2015-08-19 | 2016-01-06 | 庞乐钧 | Rotary combustion engine |
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| CN105569839B (en) * | 2015-10-25 | 2017-11-07 | 宋跃忠 | A kind of novel efficient engine |
| CN106194430A (en) * | 2016-09-30 | 2016-12-07 | 淄博衡动机械制造有限公司 | Collision explosion motor |
| CN106285993A (en) * | 2016-10-20 | 2017-01-04 | 北京理工大学 | A kind of miniature rotor electromotor cooling system |
| CN106499504A (en) * | 2016-11-03 | 2017-03-15 | 北京理工大学 | A kind of miniature rotor engine water is cold and adjustable electromagnetic sealing device |
| CN108223116A (en) * | 2017-12-02 | 2018-06-29 | 张英华 | Rotary piston engine and control method |
| CN108223791A (en) * | 2018-01-04 | 2018-06-29 | 中国人民解放军国防科技大学 | Self-rotating anti-friction structure of piston ring |
| CN108223791B (en) * | 2018-01-04 | 2020-01-10 | 中国人民解放军国防科技大学 | Self-rotating anti-friction structure of piston ring |
| CN108937812A (en) * | 2018-07-17 | 2018-12-07 | 广州沃安实业有限公司 | A kind of intelligence cleaning equipment |
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| CN114183232A (en) * | 2021-12-15 | 2022-03-15 | 林康团 | Infusion device with anti-blocking function for machining automobile engine |
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| CN115163200B (en) * | 2022-07-26 | 2024-04-16 | 聂再安 | Rotary piston steam engine |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102282347A (en) | 2011-12-14 |
| WO2011050571A1 (en) | 2011-05-05 |
| CN102282347B (en) | 2013-04-17 |
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Application publication date: 20100421 |