CN101709671A - Symmetrical rocker type large-torque output engine - Google Patents
Symmetrical rocker type large-torque output engine Download PDFInfo
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- CN101709671A CN101709671A CN200910241721A CN200910241721A CN101709671A CN 101709671 A CN101709671 A CN 101709671A CN 200910241721 A CN200910241721 A CN 200910241721A CN 200910241721 A CN200910241721 A CN 200910241721A CN 101709671 A CN101709671 A CN 101709671A
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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, by 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 many times continuous transformation 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, general conventional engine is finished 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 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 1 that carries out working stroke ' other non-working stroke of drive.
At working stroke, when piston 1 ' at top dead center position, fuel is sprayed into by in the air of piston 1 ' compression, 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 rotate 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 to piston 1 ' maximum thrust, directly influence the performance of engine efficiency level, cause the huge waste of the energy.
At 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, (as described in following technical documentation) appears in existing many patents as 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 to widely apply on producing.And its motions of internal-combustion engine such as the diesel engine of using, petrol engine remain brace and connecting rod framework now.
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
At 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 achieving the above object, the present invention takes following technological scheme: a kind of 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, oppositely free wheel device, transmission shaft, driving gear, driven gear, secondary fork, parallel rod, connecting rod, crank, accumulated energy flywheel and crankshaft; Described first cylinder group is arranged at a side of described pto, one end of described first push rod is articulated on the piston of described first cylinder block, one end of the other end of described first push rod and described first fork is hinged, the other end of described first fork is fixed on the described free wheel device, described free wheel device is sleeved on the described pto, and described free wheel device and pto have common revolution axle center, described piston, first push rod, first fork, free wheel device and pto are formed the moment of torsion output mechanism of described first cylinder block; Described second cylinder block is symmetricly set in the opposite side of described pto with respect to described first cylinder block, one end of described second push rod is articulated on the piston of described second cylinder block, one end of the other end of described second push rod and described second fork is hinged, the other end of described second fork is fixed on the described free wheel device, and be symmetrical in described pto with described first fork, described piston, second push rod, second fork, free wheel device and pto are formed the moment of torsion output mechanism of described second cylinder block; Described driving gear is fixed on the described pto, itself and the driven gear engagement of being fixed on the described transmission shaft; Described reverse free wheel device be sleeved on the described transmission shaft and with described free wheel device reverse configuration, described reverse free wheel device and transmission shaft have common revolution axle center; One end of described secondary fork is fixed on the outer rim of described reverse free wheel device, and an end of the other end of described secondary fork and described parallel rod is hinged, and the other end of described parallel rod and described first fork are hinged; Described accumulated energy flywheel is fixedly connected on the described crankshaft, the hinged composition connecting rod of an end of described connecting rod and described crank, the other end of described connecting rod be articulated on described first fork or second fork more arbitrarily.
The articulating point of described first, second push rod and described piston is configured on the axis of described piston, the articulating point of described first, second push rod and described first, second fork is configured in the near axis of described piston, the axis normal configuration of the neutral position of described first, second fork swing and described piston, the length of described first, second fork is greater than the radius of described crank.
The length of described connecting rod is greater than the radius of 2 times described crank, the articulating point of the length of described connecting rod, the length of described crank, described connecting rod and described second fork to described second pendulum swinging center apart from sum greater than the distance of described crank shaft core to described second pendulum swinging center.
The articulating point of described parallel rod and described second fork equals the distance of the articulating point of described secondary fork and described parallel rod to described transmission shaft axle center to the distance in described pto axle center, and the length of described parallel rod equals the centre distance of described pto and described transmission shaft.
The diameter of described driving gear and driven gear and the number of teeth equate.
The equal in length of described first push rod and second push rod, the equal in length of described first fork and second fork.
Increase 2N cylinder block on the basis of described first cylinder block and second cylinder block, wherein N is the natural number except that zero; The cylinder block that increases is symmetricly set on the both sides of described pto, and the cylinder block that increases all has the moment of torsion output mechanism with described first cylinder block and the second cylinder block same structure; The fork of adjacent two cylinder block of all and described pto homonymy all is fixed into one by 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, utilize the swing of fork moment of torsion to be exported by pto by free wheel device, thereby the to-and-fro motion of piston is changed into rotatablely moving of pto, 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 is greater than the radius of crank, can give full play to the thrust of piston like this, increase 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 drawings and Examples the present invention is described in detail.
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, the other end of fork 7 is fixed on the free wheel device 10, free wheel device 10 is sleeved on the pto 11, and free wheel device 10 and pto 11 have common revolution axle center A, thereby have been made of the moment of torsion output mechanism of cylinder block I 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 be symmetrical in pto 11 with fork 7, thereby 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, 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 of gear 14 and gear 15 and the number of teeth 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, promoting piston 2 moves downward from top dead center, the power of piston 2 is delivered to an end of fork 7 by push rod 6, drive the axis swing of fork 7 moving power output shafts 11, transfer torque to pto 11 by 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 oppositely free wheel device 12 separates with transmission shaft 13.When cylinder block I finished working stroke, cylinder block II finished compression stroke, and cylinder block III finishes suction stroke, and cylinder block IV finishes exhaust stroke.
In the working stroke of cylinder block I, fork 9 moves upward by the piston 2 that push rod 8 promotes cylinder block II, finishes 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 by push rod 8 from top dead center, drive fork 9 and with the axis swing of the fork 7 moving power output shafts 11 of its balanced configuration.At this moment, free wheel device 10 separates with pto 11, power is by the articulating point of fork 7 with parallel rod 17, through parallel rod 17, drive secondary fork 16 around transmission shaft 13 swings, by 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 the fixing reverse free wheel device 12 of secondary fork 16.When cylinder block II finished working stroke, cylinder block III finished compression stroke, and cylinder block IV finishes suction stroke, and cylinder block I finishes exhaust stroke.
In cylinder block II working stroke, the cylinder block III that is disposed at opposite side finishes compression stroke, 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 by push rod 22, drive the axis swing of fork 23 moving power output shafts 11, transfer torque to pto 11, output power by pto 11 by free wheel device 26.Simultaneously, cylinder block IV finishes compression stroke, and cylinder block I finishes suction stroke, and cylinder block II finishes exhaust stroke.
In cylinder block III working stroke, cylinder block IV finishes 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, by push rod 24 power of piston 2 is delivered to an end of fork 25, drive fork 25 and with the axis swing of the fork 23 moving power output shafts 11 of its balanced configuration.At this moment, free wheel device 10 separates with pto 11 with free wheel device 26, power is by the articulating point of fork 23 with parallel rod 17, through parallel rod 17, drive secondary fork 16 around transmission shaft 13 swings, by 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 the fixing reverse free wheel device 12 of secondary fork 16.Simultaneously, cylinder block I finishes compression stroke, and cylinder block II finishes suction stroke, and cylinder block III finishes exhaust stroke.
At the working stroke of cylinder block I and cylinder block III, free wheel device 10 engages with pto 11, and oppositely free wheel device 12 separates, and power is directly exported by pto 11; At the working stroke of cylinder block II and IV, oppositely 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 of fixedlying connected with crankshaft 21.The main function of the connecting rod of this moment is to control the opening and closing of firing time, intake valve and the exhaust valve of each cylinder block according to the angle position 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 be arranged at each stroke, pto 11 all can obtain power 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 technical solution 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 (9)
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;
Described first cylinder group is arranged at a side of described pto, one end of described first push rod is articulated on the piston of described first cylinder block, one end of the other end of described first push rod and described first fork is hinged, the other end of described first fork is fixed on the described free wheel device, described free wheel device is sleeved on the described pto, and described free wheel device and pto have common revolution axle center, described piston, first push rod, first fork, free wheel device and pto are formed the moment of torsion output mechanism of described first cylinder block;
Described second cylinder block is symmetricly set in the opposite side of described pto with respect to described first cylinder block, one end of described second push rod is articulated on the piston of described second cylinder block, one end of the other end of described second push rod and described second fork is hinged, the other end of described second fork is fixed on the described free wheel device, and be symmetrical in described pto with described first fork, described piston, second push rod, second fork, free wheel device and pto are formed the moment of torsion output mechanism of described second cylinder block;
Described driving gear is fixed on the described pto, itself and the driven gear engagement of being fixed on the described transmission shaft; Described reverse free wheel device be sleeved on the described transmission shaft and with described free wheel device reverse configuration, described reverse free wheel device and transmission shaft have common revolution axle center; One end of described secondary fork is fixed on the outer rim of described reverse free wheel device, and an end of the other end of described secondary fork and described parallel rod is hinged, and the other end of described parallel rod and described first fork are hinged;
Described accumulated energy flywheel is fixedly connected on the described crankshaft, the hinged composition connecting rod of an end of described connecting rod and described crank, the other end of described connecting rod be articulated on described 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 described first, second push rod and described piston is configured on the axis of described piston, the articulating point of described first, second push rod and described first, second fork is configured in the near axis of described piston, the axis normal configuration of the neutral position of described first, second fork swing and described piston, the length of described first, second fork is greater than the radius of described 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 described connecting rod is greater than the radius of 2 times described crank, the articulating point of the length of described connecting rod, the length of described crank, described connecting rod and described second fork to described second pendulum swinging center apart from sum greater than the distance of described crank shaft core to described 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 described connecting rod is greater than the radius of 2 times described crank, the articulating point of the length of described connecting rod, the length of described crank, described connecting rod and described second fork to described second pendulum swinging center apart from sum greater than the distance of described crank shaft core to described second pendulum swinging center.
5. as 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 described parallel rod and described second fork equals the distance of the articulating point of described secondary fork and described parallel rod to described transmission shaft axle center to the distance in described pto axle center, and the length of described parallel rod equals the centre distance of described pto and described transmission shaft.
6. as 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 described 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 described driving gear and driven gear and the number of teeth equate.
8. as the described a kind of symmetrical rocker type large-torque output engine of claim 1～7, it is characterized in that: the equal in length of described first push rod and second push rod, the equal in length of described first fork and second fork.
9. as the described a kind of symmetrical rocker type large-torque output engine of claim 1～8, it is characterized in that: increase 2N cylinder block on the basis of described first cylinder block and second cylinder block, wherein N is the natural number except that zero; The cylinder block that increases is symmetricly set on the both sides of described pto, and the cylinder block that increases all has the moment of torsion output mechanism with described first cylinder block and the second cylinder block same structure; The fork of adjacent two cylinder block of all and described pto homonymy all is fixed into one by connecting rod.
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| Application Number | Priority Date | Filing Date | Title |
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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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| CN101709671A true CN101709671A (en) | 2010-05-19 |
| CN101709671B CN101709671B (en) | 2012-05-02 |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102926866A (en) * | 2012-11-09 | 2013-02-13 | 沈阳建筑大学 | Gasoline engine of swinging rod power output mechanism |
| CN104832279A (en) * | 2015-01-08 | 2015-08-12 | 武汉富国发动机科技有限公司 | Novel energy-saving internal combustion engine |
| CN104832281A (en) * | 2015-01-08 | 2015-08-12 | 武汉富国发动机科技有限公司 | Optimized energy-saving internal combustion engine |
| CN104832280A (en) * | 2015-01-08 | 2015-08-12 | 武汉富国发动机科技有限公司 | Perfect, practical and efficient output internal combustion engine |
| CN106194428A (en) * | 2014-12-20 | 2016-12-07 | 赵景杰 | A kind of internal combustion engine actuating device |
| CN109695502A (en) * | 2017-10-23 | 2019-04-30 | 闫传东 | Novel light fuel combustion engine |
| 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 |
| CN109958533A (en) * | 2019-03-28 | 2019-07-02 | 浙江大学 | Fluid power motor |
| WO2020168644A1 (en) * | 2019-02-19 | 2020-08-27 | 尹建 | Reciprocating engine lever-type variable plunder pump power output mechanism |
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2009
- 2009-12-02 CN CN2009102417210A patent/CN101709671B/en not_active Expired - Fee Related
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102926866A (en) * | 2012-11-09 | 2013-02-13 | 沈阳建筑大学 | Gasoline engine of swinging rod power output mechanism |
| CN106194428A (en) * | 2014-12-20 | 2016-12-07 | 赵景杰 | A kind of internal combustion engine actuating device |
| CN104832279A (en) * | 2015-01-08 | 2015-08-12 | 武汉富国发动机科技有限公司 | Novel energy-saving internal combustion engine |
| CN104832281A (en) * | 2015-01-08 | 2015-08-12 | 武汉富国发动机科技有限公司 | Optimized energy-saving internal combustion engine |
| CN104832280A (en) * | 2015-01-08 | 2015-08-12 | 武汉富国发动机科技有限公司 | Perfect, practical and efficient output internal combustion 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 |
| 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 |
| CN109695502A (en) * | 2017-10-23 | 2019-04-30 | 闫传东 | Novel light fuel combustion engine |
| WO2020168644A1 (en) * | 2019-02-19 | 2020-08-27 | 尹建 | Reciprocating engine lever-type variable plunder pump power output 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 |
| CN109958533A (en) * | 2019-03-28 | 2019-07-02 | 浙江大学 | Fluid power motor |
| CN109958533B (en) * | 2019-03-28 | 2020-10-09 | 浙江大学 | Hydraulic engine |
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