CN104879212A - Double-piton four-stroke internal combustion engine - Google Patents
Double-piton four-stroke internal combustion engine Download PDFInfo
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- CN104879212A CN104879212A CN201510215323.7A CN201510215323A CN104879212A CN 104879212 A CN104879212 A CN 104879212A CN 201510215323 A CN201510215323 A CN 201510215323A CN 104879212 A CN104879212 A CN 104879212A
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Abstract
The invention belongs to the field of internal combustion engines and discloses a double-piston four-stroke internal combustion engine. The double-piston four-stroke internal combustion engine comprises a cylinder block, an air cylinder is arranged on the cylinder block, and two opposite pistons are arranged in the air cylinder and connected with crankshafts through connecting rods respectively. When the air cylinder reaches a compression extreme value, the secondary acting piston is positioned at the farthest end of a stroke, the primary acting piston and the corresponding crankshaft already pass through an upper dead center, and the primary acting piston starts to descend but does not reach the farthest end of the stroke, so that a force arm is generated by the connecting rod of the primary acting piston and the corresponding crankshaft, namely when the air cylinder reaches the compression extreme value at the moment of fuel combustion, the favorable force arm is generated by one of the connecting rod and the corresponding crankshaft to enable effectiveness in action at the moment of ignition. The double-piston four-stroke internal combustion engine has the advantages that the ideal force arm for action already exists when the fuel of the internal combustion engine burns for action, energy generated in fuel explosion can be utilized for action, and accordingly fuel energy conversion rate is increased.
Description
technical field:
The invention belongs to field of internal combustion engine, particularly relate to a kind of double-piston quartastroke engine.
background technique:
At present, internal-combustion engine is a motor in the form of piston in single cylinder substantially, wherein crankshaft-link rod, piston runs the serious principle running counter to lever principle and mechanics three elements of attitude, it is different from motor, the rotor radius of motor equals moment of torsion, so the moment of torsion of motor is invariable, and the large phase of reciprocating engine front yard unexpectedly, crank throw is not the arm of force, and it is pulled by connecting rod and circles, and will carry out resolution of forces be calculated to be the arm of force through trigonometric function, the place arm of force is a variable, and bent axle and connecting rod exist angle forever.In work, crankshaft operation to top dead center and lower this time angle be 0, the value of the arm of force is 0, and top dead center is fuel explosive combustion starts work done, maximum heat energy is converted to the perfect time point of mechanical energy, and at this moment arm of force value is 0, moment of torsion is also 0, and be equal to nothing acting, when bent axle to be dragged to turn 90 degrees, arm of force value is only maximum value, and the stroke cylinder pressure that at this moment piston has also slided half has dropped to remaining about 25%.
Summary of the invention:
Technical problem to be solved by this invention is: made internal-combustion engine just have the desirable arm of force to exist when fuel explosive combustion starts work done, and when making outburst, maximum energy can be utilized acting, carries high-octane conversion ratio.
In order to reach above-mentioned technical purpose, technological scheme of the present invention is: a kind of double-piston quartastroke engine, comprise cylinder body, intake valve and exhaust valve, this cylinder body comprises at least one cylinder, in single cylinder, include two pistons be oppositely arranged, be respectively main work doing pistons and time work doing pistons, wherein main work doing pistons connects main work done bent axle by first connecting rod and promotes its rotation, secondary work doing pistons connects time work done by second connecting rod and swings bent axle and promote its motion, and main work done bent axle and time work done are swung bent axle and be connected by transmission device and do identical periodic motion, in the process of acting, when in cylinder, compression ratio reaches extreme value, the position of secondary work doing pistons is positioned at the distalmost end of its stroke, and now the position of main work doing pistons has turned over top dead center and defined the arm of force not in the distalmost end of its stroke, and in order to ensure time work doing pistons its distalmost end time, compression ratio in its cylinder is extreme value, the stroke of this main work doing pistons is less than the stroke of time work doing pistons, like this because the stroke of main work doing pistons is less than the stroke of time work doing pistons, under the identical cycle of motion, the movement velocity of main work doing pistons must be less than the movement velocity of time work doing pistons, so when time work doing pistons leaves its distalmost end, no matter main work doing pistons is identical or reverse with time work doing pistons moving direction, distance between them must be in minimizing, so the compression ratio between two-piston is large in change, be suitable for the needs breaking out acting.In this programme, because secondary work doing pistons is positioned at its distalmost end in that time that fuel breaks out, therefore its second connecting rod is zero relative to the arm of force of secondary work done bent axle, now be not positioned at the distalmost end of its stroke because main work doing pistons starts to decline, that is first connecting rod and main work done bent axle create the desirable arm of force, the size of the arm of force is determined from the distance of the distalmost end of its stroke by the length of connecting rod and main piston, owing to there being the existence of the desirable arm of force, in the starting stage of fuel outburst, make bent axle obtain comparatively high pulling torque, improve the transformation efficiency of fuel.Again because the stroke of main work doing pistons is less than the stroke of time work doing pistons, so under the identical cycle of motion, the motion speed of main work doing pistons is less than the motion speed of time work doing pistons, in running, two-piston has the relative movement stage, move toward one another stage and in the same way motion stage, in these stages, owing to breaking out the stage at fuel, in its compression ratio extreme value, when namely secondary work doing pistons is on the position of distalmost end, because the speed of two pistons is different, so due to secondary work doing pistons be to leave its distalmost end, no matter main work doing pistons is in opposite directions or reverse motions, distance between two-piston is all reducing, in proper order work doing pistons can reach the extreme value of cylinder compression ratio when its distalmost end, now because the first connecting rod on main work doing pistons and main work done bent axle have had larger torque, the just acting when fuel is broken out can be ensured, guarantee the efficiency improving fuel reburning energy.
Further, as the preferred kind of drive, employing drive link is transmission device, and secondary work done is swung bent axle and is connected with main work done bent axle by drive link, and realizes promoting the motion that main work done bent axle does same period.Wherein main work done bent axle is pto＝power take-off.
Further, when the moving radius of the first connecting rod neck on main work done bent axle be less than time work done swing the moving radius of second connecting rod neck on bent axle time, main work done bent axle circles, and secondary work done swings bent axle several angle and to swing back and forth motion.
Further, in order to adapt to the design during outburst of main work doing pistons fuel, so porting listens position to be positioned at the below of the distalmost end of the stroke of time work doing pistons; And be positioned at the top position of piston when main work doing pistons reaches compression ratio extreme value simultaneously.
Further, in order to adapt with the piston set-up mode of this internal-combustion engine, so the position of porting and the position of inlet and exhaust valve adapt.
Further, in order to adapt to the needs of petrol engine, be also provided with spark plug, chew in order to the needs adapting to diesel engine are also provided with high pressure fuel injector, the position of the position of spark plug and the position of oil injecting nozzle and porting adapts.
Further, in order to better transmission, the quantity of described drive link can be one or more.
The invention has the beneficial effects as follows: make internal-combustion engine just have the desirable arm of force to exist when fuel explosive combustion starts work done, when making outburst, maximum energy can be utilized work done, improves the conversion ratio of the energy of fuel.
Accompanying drawing explanation
Fig. 1 is the structural representation of two cylinder embodiments in the present invention;
Structural representation when Fig. 2 is fuel of the present invention outburst;
In figure: cylinder 1, main work done bent axle 21, secondary work done swing bent axle 22, main work doing pistons 31, secondary work doing pistons 32, first connecting rod 41, second connecting rod 42, drive link 222, first connecting rod neck end 2221, first connecting rod neck end 2222, porting 5, cylinder head 6, intake and exhaust device 61, spark plug or oil injecting nozzle 62, arm of force L.
Specific embodiment
Below in conjunction with accompanying drawing, the invention will be further described.
As shown in Figure 1, 2, a kind of double-piston quartastroke engine, using two cylinder machines, (two cylinders herein do not limit as to the quantity of cylinder the present embodiment, three cylinders, four cylinders or more multi cylinder can be applied to) simultaneously, in two cylinders 1, include two pistons be oppositely arranged respectively, be respectively main work doing pistons 31 and time work doing pistons 32; Wherein main work doing pistons 31 connects main work done bent axle 21 by first connecting rod 41 and promotes its rotation; Secondary work doing pistons 32 connects time work done bent axle 22 by second connecting rod 42 and promotes its motion, and secondary work done bent axle 22 is connected with main work done bent axle 21 by drive link 222, and realizes promoting the motion that main work done swing bent axle 21 does same period.Main work done bent axle 21 is pto＝power take-off.
The quantity of drive link 222 is one, one end drive link 222 connecting main work done bent axle 21 is first connecting rod neck end 2221, one end drive link 222 connecting time work done bent axle 22 is first connecting rod neck end 2222, main work done bent axle 21 and time work done swing bent axle 22 and are respectively equipped with the connecting rod neck adapted with first connecting rod neck end 2221 and first connecting rod neck end 2222, wherein be arranged at main work done bent axle 21 adapts with first connecting rod neck end 2221 for first connecting rod neck 211, being arranged at time work done, to swing what bent axle 22 adapted with first connecting rod neck end 2222 be second connecting rod neck 221, the length of the turning radius of first connecting rod 211 is greater than the length of first connecting rod neck 221 turning radius, now, described main work done bent axle 21 circles, and secondary work done swings the motion swung back and forth that several angle made by bent axle 22.In acting process, when in cylinder, compression ratio reaches extreme value, the position of described secondary work doing pistons 32 is positioned at the distalmost end of its stroke, and the position of now described main work doing pistons 31 has turned over several angle after piston top dead center, not in the distalmost end of its stroke by bent axle; First connecting rod 41 has a non-vanishing larger arm of force L relative to main work done bent axle 21, so just produce a larger torque, owing to there being moment, the place fuel outburst stage just can ensure that it does work, and the stroke of described main work doing pistons 31 is less than the stroke of time work doing pistons 32, ensure that the extreme value reaching compression ratio in the distalmost end cylinder 1 of its stroke swinging bent axle 32 in secondary work done.
Cylinder body 9 also comprises porting 5, and porting 5 is positioned at the below of the distalmost end of the stroke of time work doing pistons 32; And be positioned at the top position of piston when main work doing pistons 31 reaches compression ratio extreme value simultaneously.Inlet and exhaust valve 61 is also being provided with suitable place, the position of porting 5.Simultaneously in order to meet the needs of petrol engine, be also provided with spark plug or diesel oil high pressure fuel injector chews 62, spark plug or diesel oil high pressure fuel injector chew the position of 62 and the position of porting 5 adapts.
Claims (7)
1. a double-piston quartastroke engine, comprise cylinder body (9), it is characterized in that: described cylinder body (9) comprises at least one cylinder (1), in described single cylinder (1), include two pistons be oppositely arranged, be respectively main work doing pistons (31) and time work doing pistons (32); Wherein said main work doing pistons (31) connects main work done bent axle (21) by first connecting rod (41) and promotes its rotation; Described secondary work doing pistons (32) connects time work done by second connecting rod (42) and swings bent axle (22) and promote its motion; Described main work done bent axle (21) and time work done are swung bent axle (22) and are connected by transmission device and the oscillating motion making same period; In the process of acting, when in cylinder, compression ratio reaches extreme value, the position of described secondary work doing pistons (32) is in the distalmost end of its stroke, and the position of now described main work doing pistons (31) is not in the distalmost end of its stroke; And the stroke of described main work doing pistons (31) is less than the stroke of time work doing pistons (32).
2. a kind of double-piston according to claim 1 four kinds of journey internal-combustion engines, is characterized in that: described main work done bent axle (21) is pto＝power take-off; Described start is swung bent axle (22) and is connected with main work done bent axle (21) by drive link (222), and realizes promoting the motion that main work done bent axle (21) does same period.
3. a kind of double-piston quartastroke engine according to claim 2, it is characterized in that: the upper one end connecting main work done bent axle (21) of described drive link (222) is first connecting rod neck end (2221), the upper one end connecting secondary work done swing bent axle (22) of described drive link (222) is first connecting rod neck end (2222), described main work done bent axle (21) and time work done swing on bent axle (22) and are respectively equipped with the connecting rod neck adapted with first connecting rod neck end (2221) and first connecting rod neck end (2222), wherein being arranged at main work done bent axle (21), upper what adapt with first connecting rod neck end (2221) is first connecting rod neck (211), be arranged at time work done to swing bent axle (22) upper what adapt with first connecting rod neck end (2222) is first connecting rod neck (221), the moving radius of the first connecting rod neck (211) on described main work done bent axle (21) is less than the moving radius that time work done swings the upper first connecting rod neck (221) of bent axle (22).
4. a kind of double-piston quartastroke engine according to claim 1, is characterized in that: also comprise relief opening (5), and described relief opening (5) is positioned at the below of the distalmost end of the stroke of time work doing pistons (32); And be positioned at the top position of piston when main work doing pistons (31) reaches compression ratio extreme value simultaneously.
5. a kind of double-piston quartastroke engine according to claim 4, is characterized in that: the position of described porting (5) and the position of inlet and exhaust valve (61) adapt.
6. a kind of double-piston quartastroke engine according to claim 4, is characterized in that: be also provided with spark plug (62), and the position of described spark plug (62) and the position of porting (5) adapt.
7. a kind of double-piston quartastroke engine according to claim 2, is characterized in that: the quantity of described drive link (22) is one or more.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510215323.7A CN104879212A (en) | 2015-04-30 | 2015-04-30 | Double-piton four-stroke internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510215323.7A CN104879212A (en) | 2015-04-30 | 2015-04-30 | Double-piton four-stroke internal combustion engine |
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| Publication Number | Publication Date |
|---|---|
| CN104879212A true CN104879212A (en) | 2015-09-02 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510215323.7A Pending CN104879212A (en) | 2015-04-30 | 2015-04-30 | Double-piton four-stroke internal combustion engine |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106382158A (en) * | 2016-12-06 | 2017-02-08 | 苗艇 | Single-air-cylinder multi-piston multi-crankshaft engine |
| CN107131272A (en) * | 2017-04-21 | 2017-09-05 | 海南华盈泰能源科技有限公司 | A kind of double-piston is moved back and forth and the mutual switching mechanism of rotary motion |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20030005896A1 (en) * | 2001-07-05 | 2003-01-09 | Sarcos, Lc | Rapid response power conversion device |
| CN101608574A (en) * | 2009-07-27 | 2009-12-23 | 楚兆鼎 | CZD differential speed type reciprocating IC engine |
| JP2011524488A (en) * | 2008-06-17 | 2011-09-01 | カルロス リーテ プロエンサ，ルイズ | Internal combustion engine with working piston and control piston |
| CN102312719A (en) * | 2010-07-07 | 2012-01-11 | 周向进 | Compression ignition type low-octane-value gasoline engine |
| CN103867295A (en) * | 2014-01-27 | 2014-06-18 | 刘景林 | Environmental-friendly and energy-saving type two-stroke opposed crankless crankshaft engine |
-
2015
- 2015-04-30 CN CN201510215323.7A patent/CN104879212A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20030005896A1 (en) * | 2001-07-05 | 2003-01-09 | Sarcos, Lc | Rapid response power conversion device |
| JP2011524488A (en) * | 2008-06-17 | 2011-09-01 | カルロス リーテ プロエンサ，ルイズ | Internal combustion engine with working piston and control piston |
| CN101608574A (en) * | 2009-07-27 | 2009-12-23 | 楚兆鼎 | CZD differential speed type reciprocating IC engine |
| CN102312719A (en) * | 2010-07-07 | 2012-01-11 | 周向进 | Compression ignition type low-octane-value gasoline engine |
| CN103867295A (en) * | 2014-01-27 | 2014-06-18 | 刘景林 | Environmental-friendly and energy-saving type two-stroke opposed crankless crankshaft engine |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106382158A (en) * | 2016-12-06 | 2017-02-08 | 苗艇 | Single-air-cylinder multi-piston multi-crankshaft engine |
| CN107131272A (en) * | 2017-04-21 | 2017-09-05 | 海南华盈泰能源科技有限公司 | A kind of double-piston is moved back and forth and the mutual switching mechanism of rotary motion |
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Application publication date: 20150902 |