CN101709671B - Symmetrical rocker type large-torque output engine - Google Patents
Symmetrical rocker type large-torque output engine Download PDFInfo
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- CN101709671B CN101709671B CN2009102417210A CN200910241721A CN101709671B CN 101709671 B CN101709671 B CN 101709671B CN 2009102417210 A CN2009102417210 A CN 2009102417210A CN 200910241721 A CN200910241721 A CN 200910241721A CN 101709671 B CN101709671 B CN 101709671B
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Abstract
The invention relates to symmetrical rocker type large-torque output engine which is characterized by comprising a first cylinder unit, a second cylinder unit, a first push rod, a second push rod, a fist rocker, a second rocker, an overrunning clutch, a power output shaft, a reverse overrunning clutch, a transmission shaft, a drive gear, a driven gear, an auxiliary rocker, a parallel connecting rod, a connecting rod, a crank, an energy storage fly wheel and a crank shaft, wherein the first cylinder unit and the second cylinder unit comprise cylinders, pistons, fuel supply and ignition systems, inlet systems and exhaust systems; the first cylinder unit and the second cylinder unit are symmetrically arranged at two sides of the power output shaft to respectively transmit piston thrust to the first rocker and the second rocker through the first push rod and the second push rod; and the rocking of the first rocker and the second rocker is utilized to output torque from the power output shaft through the overrunning clutch, thereby transforming the reciprocating motion of the pistons into rotation motion of the power output shaft. The invention solves the problem of dead points existing in the crank connecting motion mechanism, realizes the efficient large-torque output of a piston engine, improves the efficiency of the piston engine, and reduces fuel consumption of the engine.
Description
Technical field
The present invention relates to a kind of motor, particularly a kind of to-and-fro motion with piston changes into the symmetrical rocker type large-torque output engine that rotatablely moves of pto.
Background technique
At present; The motion major part of conventional reciprocating reciprocating engine is a connecting rod; This connecting rod by piston 1 ', connecting rod 2 ' and crank 3 ' form (as shown in Figure 1); Its effect be with piston 1 ' to-and-fro motion, through connecting rod change into crankshaft 4 ' rotatablely move.Its working principle is, fuel produces heat energy in cylinder 5 ' internal combustion during engine operation, and when gases are heated, they expand promotes piston 1 ' move, through connecting rod 2 ' be delivered to crankshaft 4 ' and make its rotation acting.In the course of the work; Heat energy will be realized continuous transformation many times to mechanical energy through associating; A work cycle is all experienced in each transformation; Piston 1 ' moving from top to bottom or from top to bottom once is called a stroke, and general conventional engine is accomplished a work cycle needs 4 strokes, i.e. suction stroke, compression stroke, acting (outburst) stroke and exhaust stroke.A work cycle, piston 1 ' up and down reciprocatingly 4 times, crankshaft 4 ' revolve takes two turns.In a work cycle; Having only working stroke is the active stroke by piston 1 ' throw crank linkage mechanism; The power of its excess-three stroke, for single-cylinder engine, be by accumulated energy flywheel 6 ' inertial force drive crank and connecting rod movement; For multicylinder engine, then be by the cylinder 5 ' work of the piston that carries out working stroke 1 ' other non-working stroke of drive.
At working stroke, when piston 1 ' at top dead center position, fuel is sprayed into by in piston 1 ' air compressed, the fuel combustion blast, gas expands and promotes piston 1 ' move downward acting, this moment piston 1 ' stressed maximum.Characteristic by connecting rod has determined; This moment crank 3 ' with connecting rod 2 ' be in line; Piston 1 ' active force is very little with respect to the moment radius at crankshaft 4 ' center, and the moment of torsion of crankshaft 4 ' generation is equaled the long-pending of power and moment radius, therefore by crankshaft 4 ' outwards the moment of torsion of output is less.And, with piston 1 ' move downward, crank 3 ' also rotates simultaneously; The moment radius that acts on crankshaft 4 ' center increases thereupon; But because cylinder 5 ' volume enlarge simultaneously, gas to piston 1 ' pressure reduce rapidly, therefore; Crankshaft 4 ' moment of torsion output do not reach best condition yet, fail to give full play to the best efficiency that the fuel combustion blast is produced.Piston 1 ' movement process in; The variation of active force and moment radius is also bigger; Caused the unstability of crankshaft 4 ' moment of torsion output, can not give full play to piston 1 ' when top dead center, the effect that fuel combustion produces piston 1 ' maximum thrust; Directly influence the performance of engine efficiency level, cause the huge waste of the energy.
To the problems referred to above; A large amount of experts and scholars are devoted to solve the problem of this respect always both at home and abroad; (of following technical documentation) appears in existing many patents like new work engine principle aspects such as rotary engines; But because its complex structure, control system is difficult to technical problems such as realization, and fails on producing, to widely apply.And its motions of internal-combustion engine such as the diesel engine of using now, petrol engine remain brace and connecting rod framework.
Technical paper 1: novel rotary piston type engine, number of patent application 200810030021.
Technical paper 2: rotary engine, number of patent application 200510103234.
Technical paper 3: deflecting type reciprocating movement engine, number of patent application 200710163913.
Technical paper 4: combustion engine with rotary engine body, number of patent application 200710133585.
Technical paper 5: Slidine-vane rotor engine, number of patent application 200710148485.
Technical paper 6: multi-link engine, number of patent application 200810173230.
Summary of the invention
To above problem, the purpose of this invention is to provide the symmetrical rocker type large-torque output engine that rotatablely moves that a kind of to-and-fro motion with piston changes into pto.
For realizing above-mentioned purpose, the present invention takes following technological scheme: a kind of symmetrical rocker type large-torque output engine is characterized in that: it comprises first cylinder block and second cylinder block of being made up of cylinder, piston, fuel delivery and ignition system, gas handling system, vent systems, first, second push rod; First, second fork, free wheel device, pto; Reverse free wheel device, transmission shaft, driving gear; Driven gear, secondary fork, parallel rod; Connecting rod, crank, accumulated energy flywheel and crankshaft; Said first cylinder group is arranged at a side of said pto; One end of said first push rod is articulated on the piston of said first cylinder block; One end of the other end of said first push rod and said first fork is hinged; The other end of said first fork is fixed on the said free wheel device; Said free wheel device is sleeved on the said pto, and said free wheel device and pto have common revolution axle center, and said piston, first push rod, first fork, free wheel device and pto are formed the moment of torsion output mechanism of said first cylinder block; Said second cylinder block is symmetricly set in the opposite side of said pto with respect to said first cylinder block; One end of said second push rod is articulated on the piston of said second cylinder block; One end of the other end of said second push rod and said second fork is hinged; The other end of said second fork is fixed on the said free wheel device; And be symmetrical in said pto with said first fork, said piston, second push rod, second fork, free wheel device and pto are formed the moment of torsion output mechanism of said second cylinder block; Said driving gear is fixed on the said pto, itself and the driven gear engagement of being fixed on the said transmission shaft; Said reverse free wheel device be sleeved on the said transmission shaft and with said free wheel device reverse configuration, said reverse free wheel device and transmission shaft have common revolution axle center; One end of said secondary fork is fixed on the outer rim of said reverse free wheel device, and an end of the other end of said secondary fork and said parallel rod is hinged, and the other end of said parallel rod and said first fork are hinged; Said accumulated energy flywheel is fixedly connected on the said crankshaft, the hinged composition connecting rod of an end of said connecting rod and said crank, the other end of said connecting rod be articulated on said first fork or second fork more arbitrarily.
The articulating point of said first, second push rod and said piston is configured on the axis of said piston; The articulating point of said first, second push rod and said first, second fork is configured in the near axis of said piston; The axis normal configuration of the neutral position of said first, second fork swing and said piston, the length of said first, second fork is greater than the radius of said crank.
The length of said connecting rod is greater than the radius of 2 times said crank, the articulating point of the length of said connecting rod, the length of said crank, said connecting rod and said second fork to said second pendulum swinging center apart from sum greater than the distance of said crank shaft core to said second pendulum swinging center.
The articulating point of said parallel rod and said second fork equals the distance of the articulating point of said secondary fork and said parallel rod to said transmission shaft axle center to the distance in said pto axle center, and the length of said parallel rod equals the centre distance of said pto and said transmission shaft.
The diameter of said driving gear and driven gear and the number of teeth equate.
The equal in length of said first push rod and second push rod, the equal in length of said first fork and second fork.
On the basis of said first cylinder block and second cylinder block, increase 2N cylinder block, wherein N is the natural number except that zero; The cylinder block that increases is symmetricly set on the both sides of said pto, and the cylinder block that increases all has the moment of torsion output mechanism with said first cylinder block and the second cylinder block same structure; The fork of adjacent two cylinder block of all and said pto homonymy all is fixed into one through connecting rod.
The present invention is owing to take above technological scheme, and it has the following advantages:
1, the present invention with two cylinder block balanced configurations in the both sides of pto; Piston thrust is delivered to fork respectively through push rod, utilizes the swing of fork moment of torsion to be exported by pto, thereby the to-and-fro motion of piston is changed into rotatablely moving of pto through free wheel device; Solve the technical barrier that there is the dead point in crank rod movement mechanism; Realize the efficient high pulling torque output of reciprocating engine, improve the efficient of reciprocating engine, reduce the fuel consume of motor.2, the articulating point of push rod of the present invention and piston is configured on the axis of piston; The articulating point of push rod and fork is configured in the near axis of piston; The axis normal configuration of the neutral position of fork swing and piston; The length of fork can be given full play to the thrust of piston like this greater than the radius of crank, increases the moment of torsion output of pto.
Description of drawings
Fig. 1 is the structural representation of conventional piston formula motor
Fig. 2 is the structural representation of the embodiment of the invention 1
Fig. 3 is the structural representation of the embodiment of the invention 2
Embodiment
Below in conjunction with accompanying drawing and embodiment the present invention is carried out detailed description.
Embodiment 1:
As shown in Figure 2, present embodiment comprises cylinder block I and the cylinder block II that is made up of cylinder 1, piston 2, fuel delivery and ignition system 3, gas handling system 4, vent systems 5, push rod 6,8, fork 7,9; Free wheel device 10, pto 11, reverse free wheel device 12, transmission shaft 13; Gear 14,15, secondary fork 16, parallel rod 17; Connecting rod 18, crank 19, accumulated energy flywheel 20 and crankshaft 21.
Cylinder group I is arranged at a side of pto 11; One end of push rod 6 is articulated on the piston 2 of cylinder block I; One end of the other end of push rod 6 and fork 7 is hinged, and the other end of fork 7 is fixed on the free wheel device 10, and free wheel device 10 is sleeved on the pto 11; And free wheel device 10 has common revolution axle center A with pto 11, thereby has formed the moment of torsion output mechanism of cylinder block I by piston 2, push rod 6, fork 7, free wheel device 10 and pto 11.
Cylinder block II is symmetricly set in the opposite side of pto 11 with respect to cylinder block I; One end of push rod 8 is articulated on the piston 2 of cylinder block II; One end of the other end of push rod 8 and fork 9 is hinged; The other end of fork 9 is fixed on the free wheel device 10, and is symmetrical in pto 11 with fork 7, thereby has formed the moment of torsion output mechanism of cylinder block II by piston 2, push rod 8, fork 9, free wheel device 10 and pto 11.
In the foregoing description; The articulating point of push rod 6,8 and piston 2 is configured on the axis of piston 2; The articulating point of push rod 6,8 and fork 7,9 is configured in the near axis of piston 2, the axis normal configuration of the neutral position of fork 7,9 swings and piston 2, and the length of fork 7,9 is greater than the radius of crank 19; Can give full play to the thrust of piston 2 like this, increase the moment of torsion output of pto 11.
In the foregoing description; The length of connecting rod 18 is greater than the radius of 2 times crank 19; The articulating point of the length of the length of connecting rod 18, crank 19, connecting rod 18 and fork 9 arrives the distance of fork 9 swinging centers apart from sum greater than crank 19 axle center to fork 9 swinging centers, to satisfy the motion requirement of each member
In the foregoing description; The distance that parallel rod 17 and the articulating point D point of fork 9 orders to pto 11 axle center A equals the distance that secondary fork 16 and the articulating point C point of parallel rod 17 are ordered to transmission shaft 13 axle center B, and the length of parallel rod 17 equals the centre distance of pto 11 and transmission shaft 13.
In the foregoing description, the equal in length of push rod 6 and push rod 8, the equal in length of fork 7 and fork 9.
In the foregoing description, the diameter and the number of teeth of gear 14 and gear 15 equate.
Embodiment 2:
As shown in Figure 3; Present embodiment and embodiment's 1 difference is; It has increased cylinder block III and cylinder block IV on the basis of cylinder block I and cylinder block II; And cylinder block III is arranged on the same side of cylinder block I, and it is connected with the moment of torsion output mechanism of being made up of piston 2, push rod 22, fork 23, free wheel device 26 and pto 11.Cylinder block IV is symmetricly set on the opposite side of pto 11 with respect to cylinder block III, and it is connected with the moment of torsion output mechanism of being made up of piston 2, push rod 24, fork 25, free wheel device 26 and pto 11.The fork 7 of cylinder block I is fixed into one with the fork 23 of cylinder block III by connecting rod 27, and the fork 9 of cylinder block II is fixed into one with the fork 25 of cylinder block IV by connecting rod 27.
Working principle of the present invention is that the order of the working stroke of each cylinder block is followed successively by cylinder block I → cylinder block II → cylinder block III → cylinder block IV.
Working stroke at cylinder block I; Explosive power when utilizing fuel combustion promotes piston 2 and moves downward from top dead center, the power of piston 2 is delivered to an end of fork 7 through push rod 6; Drive the axis swing of fork 7 around pto 11; Transfer torque to pto 11 through free wheel device 10, outputed power by pto 11, the power that the moment of torsion that pto 11 obtains equals push rod 6 and its power are amassed with respect to the arm of force in pto 11 axle center.In the movement process of piston 2 from the top dead center to the lower dead center, the arm of force of push rod 6 active forces changes the excursion that is far smaller than the connecting rod arm of force, so pto 11 can obtain bigger and more uniform moment of torsion output.At this moment, fork 7 drives secondary fork 16 around transmission shaft 13 swings through parallel rod 17, and pto 11 drives transmission shaft 13 by gear 14 and gear 15 and rotates, and reverse free wheel device 12 separates with transmission shaft 13.When cylinder block I accomplished working stroke, cylinder block II accomplished compression stroke, and cylinder block III accomplishes suction stroke, and cylinder block IV accomplishes exhaust stroke.
In the working stroke of cylinder block I, fork 9 moves upward through the piston 2 that push rod 8 promotes cylinder block II, accomplishes the compression stroke of cylinder block II.When piston 2 is lighted a fire during to top dead center; Explosive power when utilizing fuel combustion; Promote piston 2 and move downward, the power of piston 2 is delivered to an end of fork 9 through push rod 8 from top dead center, drive fork 9 and with the fork 7 of its balanced configuration axis swing around pto 11.At this moment; Free wheel device 10 separates with pto 11, and power is through the articulating point of fork 7 with parallel rod 17, through parallel rod 17; Drive secondary fork 16 around transmission shaft 13 swings; Through transferring torque to transmission shaft 13,, output power by pto 11 by being fixed in the gear 15 on the transmission shaft 13 and giving pto 11 with transmission of power with its meshed gears 14 with secondary fork 16 fixing reverse free wheel devicees 12.When cylinder block II accomplished working stroke, cylinder block III accomplished compression stroke, and cylinder block IV accomplishes suction stroke, and cylinder block I accomplishes exhaust stroke.
In cylinder block II working stroke; The cylinder block III that is disposed at opposite side accomplishes compression stroke, and when the piston 2 of cylinder block III during at top dead center, the piston 2 that fuel combustion promotes cylinder block III moves downward; The power of piston 2 is delivered to an end of fork 23 through push rod 22; Drive the axis swing of fork 23, transfer torque to pto 11, output power by pto 11 through free wheel device 26 around pto 11.Simultaneously, cylinder block IV accomplishes compression stroke, and cylinder block I accomplishes suction stroke, and cylinder block II accomplishes exhaust stroke.
In cylinder block III working stroke; Cylinder block IV accomplishes compression stroke; When the piston 2 of cylinder block IV during at top dead center; The piston 2 that fuel combustion promotes cylinder block IV moves downward, and through push rod 24 power of piston 2 is delivered to an end of fork 25, drive fork 25 and with the fork 23 of its balanced configuration axis swing around pto 11.At this moment; Free wheel device 10 separates with pto 11 with free wheel device 26, and power is through the articulating point of fork 23 with parallel rod 17, through parallel rod 17; Drive secondary fork 16 around transmission shaft 13 swings; Through transferring torque to transmission shaft 13,, output power by pto 11 by being fixed in the gear 15 on the transmission shaft 13 and giving pto 11 with transmission of power with its meshed gears 14 with secondary fork 16 fixing reverse free wheel devicees 12.Simultaneously, cylinder block I accomplishes compression stroke, and cylinder block II accomplishes suction stroke, and cylinder block III accomplishes exhaust stroke.
At the working stroke of cylinder block I and cylinder block III, free wheel device 10 engages with pto 11, and reverse free wheel device 12 separates, and power is directly exported by pto 11; At the working stroke of cylinder block II and IV, reverse free wheel device 12 engages with transmission shaft 13, gives pto 11 through gear 14 and gear 15 with transmission of power, and free wheel device 10 separates, so the motion of pto 11 output has only a direction.
Each cylinder block working stroke has sub-fraction thrust to pass to connecting rod 18 through push rod 6 simultaneously, promotes connecting rod 18 motions, drives crank 19 by connecting rod 18 and rotates, and makes accumulated energy flywheel 20 rotations that are fixedly connected with crankshaft 21.The main function of the connecting rod of this moment is the opening and closing according to firing time, intake valve and the exhaust valve of each cylinder block of angle position control of crank 19, and the startup of motor can be driven by connecting rod.
In sum; For 4 two-stroke engines, adopt 4 cylinder block configurations, circulation is acting successively; Make motor the cylinder block acting all arranged at each stroke; Pto 11 all can gain impetus in each stroke like this, can realize the uninterrupted continuously rotation of pto 11, realizes power output.
The present invention only describes with the foregoing description; The structure of each parts, the position is set and connects and all can change to some extent; On the basis of technological scheme of the present invention; All improvement and equivalents of individual component being carried out according to the principle of the invention all should not got rid of outside protection scope of the present invention.
Claims (14)
1. symmetrical rocker type large-torque output engine, it is characterized in that: it comprises first cylinder block and second cylinder block of being made up of cylinder, piston, fuel delivery and ignition system, gas handling system, vent systems, first, second push rod, first, second fork; Free wheel device, pto, reverse free wheel device, transmission shaft; Driving gear, driven gear, secondary fork, parallel rod; Connecting rod, crank, accumulated energy flywheel and crankshaft;
Said first cylinder group is arranged at a side of said pto; One end of said first push rod is articulated on the piston of said first cylinder block; One end of the other end of said first push rod and said first fork is hinged; The other end of said first fork is fixed on the said free wheel device; Said free wheel device is sleeved on the said pto, and said free wheel device and pto have common revolution axle center, and said piston, first push rod, first fork, free wheel device and pto are formed the moment of torsion output mechanism of said first cylinder block;
Said second cylinder block is symmetricly set in the opposite side of said pto with respect to said first cylinder block; One end of said second push rod is articulated on the piston of said second cylinder block; One end of the other end of said second push rod and said second fork is hinged; The other end of said second fork is fixed on the said free wheel device; And be symmetrical in said pto with said first fork, said piston, second push rod, second fork, free wheel device and pto are formed the moment of torsion output mechanism of said second cylinder block;
Said driving gear is fixed on the said pto, itself and the driven gear engagement of being fixed on the said transmission shaft; Said reverse free wheel device be sleeved on the said transmission shaft and with said free wheel device reverse configuration, said reverse free wheel device and transmission shaft have common revolution axle center; One end of said secondary fork is fixed on the outer rim of said reverse free wheel device, and an end of the other end of said secondary fork and said parallel rod is hinged, and the other end of said parallel rod and said first fork are hinged;
Said accumulated energy flywheel is fixedly connected on the said crankshaft, the hinged composition connecting rod of an end of said connecting rod and said crank, the other end of said connecting rod be articulated on said first fork or second fork more arbitrarily.
2. a kind of symmetrical rocker type large-torque output engine as claimed in claim 1; It is characterized in that: the articulating point of said first, second push rod and said piston is configured on the axis of said piston; The articulating point of said first, second push rod and said first, second fork is configured in the near axis of said piston; The axis normal configuration of the neutral position of said first, second fork swing and said piston, the length of said first, second fork is greater than the radius of said crank.
3. a kind of symmetrical rocker type large-torque output engine as claimed in claim 1; It is characterized in that: the length of said connecting rod is greater than the radius of 2 times said crank, the articulating point of the length of said connecting rod, the length of said crank, said connecting rod and said second fork to said second pendulum swinging center apart from sum greater than the distance of said crank shaft core to said second pendulum swinging center.
4. a kind of symmetrical rocker type large-torque output engine as claimed in claim 2; It is characterized in that: the length of said connecting rod is greater than the radius of 2 times said crank, the articulating point of the length of said connecting rod, the length of said crank, said connecting rod and said second fork to said second pendulum swinging center apart from sum greater than the distance of said crank shaft core to said second pendulum swinging center.
5. like claim 1 or 2 or 3 or 4 described a kind of symmetrical rocker type large-torque output engines; It is characterized in that: the articulating point of said parallel rod and said second fork equals the distance of the articulating point of said secondary fork and said parallel rod to said transmission shaft axle center to the distance in said pto axle center, and the length of said parallel rod equals the centre distance of said pto and said transmission shaft.
6. like claim 1 or 2 or 3 or 4 described a kind of symmetrical rocker type large-torque output engines, it is characterized in that: the diameter of said driving gear and driven gear and the number of teeth equate.
7. a kind of symmetrical rocker type large-torque output engine as claimed in claim 5 is characterized in that: the diameter of said driving gear and driven gear and the number of teeth equate.
8. like claim 1 or 2 or 3 or 4 or 7 described a kind of symmetrical rocker type large-torque output engines, it is characterized in that: the equal in length of said first push rod and second push rod, the equal in length of said first fork and second fork.
9. a kind of symmetrical rocker type large-torque output engine as claimed in claim 5 is characterized in that: the equal in length of said first push rod and second push rod, the equal in length of said first fork and second fork.
10. a kind of symmetrical rocker type large-torque output engine as claimed in claim 6 is characterized in that: the equal in length of said first push rod and second push rod, the equal in length of said first fork and second fork.
11. like claim 1 or 2 or 3 or 4 or 7 or 9 or 10 described a kind of symmetrical rocker type large-torque output engines, it is characterized in that: on the basis of said first cylinder block and second cylinder block, increase 2N cylinder block, wherein N is the natural number except that zero; The cylinder block that increases is symmetricly set on the both sides of said pto, and the cylinder block that increases all has the moment of torsion output mechanism with said first cylinder block and the second cylinder block same structure; The fork of adjacent two cylinder block of all and said pto homonymy all is fixed into one through connecting rod.
12. a kind of symmetrical rocker type large-torque output engine as claimed in claim 5 is characterized in that: on the basis of said first cylinder block and second cylinder block, increase 2N cylinder block, wherein N is the natural number except that zero; The cylinder block that increases is symmetricly set on the both sides of said pto, and the cylinder block that increases all has the moment of torsion output mechanism with said first cylinder block and the second cylinder block same structure; The fork of adjacent two cylinder block of all and said pto homonymy all is fixed into one through connecting rod.
13. a kind of symmetrical rocker type large-torque output engine as claimed in claim 6 is characterized in that: on the basis of said first cylinder block and second cylinder block, increase 2N cylinder block, wherein N is the natural number except that zero; The cylinder block that increases is symmetricly set on the both sides of said pto, and the cylinder block that increases all has the moment of torsion output mechanism with said first cylinder block and the second cylinder block same structure; The fork of adjacent two cylinder block of all and said pto homonymy all is fixed into one through connecting rod.
14. a kind of symmetrical rocker type large-torque output engine as claimed in claim 8 is characterized in that: on the basis of said first cylinder block and second cylinder block, increase 2N cylinder block, wherein N is the natural number except that zero; The cylinder block that increases is symmetricly set on the both sides of said pto, and the cylinder block that increases all has the moment of torsion output mechanism with said first cylinder block and the second cylinder block same structure; The fork of adjacent two cylinder block of all and said pto homonymy all is fixed into one through connecting rod.
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| CN2009102417210A CN101709671B (en) | 2009-12-02 | 2009-12-02 | Symmetrical rocker type large-torque output engine |
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| CN2009102417210A CN101709671B (en) | 2009-12-02 | 2009-12-02 | Symmetrical rocker type large-torque output engine |
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| CN101709671B true CN101709671B (en) | 2012-05-02 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102926866A (en) * | 2012-11-09 | 2013-02-13 | 沈阳建筑大学 | Gasoline engine of swinging rod power output mechanism |
| CN205154396U (en) * | 2014-12-20 | 2016-04-13 | 赵景杰 | Novel internal -combustion engine transmission device |
| CN104832279B (en) * | 2015-01-08 | 2018-01-02 | 武汉富国发动机科技有限公司 | New energy-saving IC engine |
| CN104832280B (en) * | 2015-01-08 | 2017-08-08 | 武汉富国发动机科技有限公司 | Improve the internal combustion engine of practicality and high efficiency output |
| CN104832281B (en) * | 2015-01-08 | 2017-08-08 | 武汉富国发动机科技有限公司 | The energy-saving IC engine of optimization |
| CN107939520A (en) * | 2017-10-23 | 2018-04-20 | 闫传东 | To cylinder two-stroke internal combustion engine |
| CN109653975A (en) * | 2019-02-19 | 2019-04-19 | 尹建 | A kind of reciprocating engine lever Variable plunger pump power take-off mechanism |
| CN109812333A (en) * | 2019-03-18 | 2019-05-28 | 张家港川梭车业有限公司 | A kind of twin-tub rack pinion internal combustion engine |
| CN109958533B (en) * | 2019-03-28 | 2020-10-09 | 浙江大学 | Hydraulic engine |
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