CN2343357Y - Swing stem IC engine - Google Patents
Swing stem IC engine Download PDFInfo
- Publication number
- CN2343357Y CN2343357Y CN 98230001 CN98230001U CN2343357Y CN 2343357 Y CN2343357 Y CN 2343357Y CN 98230001 CN98230001 CN 98230001 CN 98230001 U CN98230001 U CN 98230001U CN 2343357 Y CN2343357 Y CN 2343357Y
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- gear
- shaft
- double pendulum
- combustion engine
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Abstract
The utility model relates to a swing rod internal combustion engine, which is an energy conversion and output device of an internal combustion engine. A crankshaft of the existing internal combustion engine is removed. The utility model is composed of a gas cylinder (1), a piston (2), a piston connecting rod (3), a double-swing rod (4), a central gear (5), a central gear shaft O1, a pin shaft (6) of the double-swing rod, a single-swing rod (7), a pin shaft (8) of the single-swing rod, a connecting rod (9), a flywheel (10), a flywheel shaft O2, an eccentric pin shaft (11), a gear (12), a one-way clutch (13), an output shaft O3, a gear (14), a one-way clutch (15), a gap bridge shaft O4, and gap bridge gears (16), (17). The utility model has the advantages that the effective efficiency of the internal combustion engine can be increased, the consumption rate of the fuel oil can be reduced, the friction loss can be reduced, the service lives of the critical motion members can be increased, the maintenance period can be extended, the turning moment is very small, the operational state of the internal combustion engine is smooth comparatively, the manufacture difficulty of the parts with the improved structures is lower than the crankshaft, the axial dimension is shortened, and the whole structure is more compact.
Description
The utility model belongs to internal-combustion engine transformation of energy output unit.
The known manner of existing internal-combustion engine transformation of energy output is: the effect of the gas in the jar swelling pressure and the addition of the piston set reciprocal inertia force P that makes a concerted effort
ΣPass to crank pin by connecting rod, on crank pin, obtain moment of torsion and export (see figure 7) by bent axle with tangential force t.The mathematic(al) representation of its tangential force t value is t=P
LSin (alpha+beta)=P
Σ[sin (alpha+beta)/cos β].As seen the t value is at zero extremely about P
ΣChange between arriving zero again, such as α during in the 15 degree left and right sides, the gas in the jar swelling pressure reach peak, and effect this moment is P with joint efforts
ΣBe worth very highly, but that the t value is reported because of α, β value are less is low.When α spends in 120 degree scopes 60, be the zone that the t value obtains big value, but but side pressure P occurred
NHigh value district, aggravated the friction between piston and the casing wall and the vibration of internal-combustion engine.When α spent near 180, though pressure reduces greatly in the cylinder, reciprocal inertia force was progressively near maximum value, the effect of this moment P that makes a concerted effort
ΣValue is still than higher, but the t value is less very low because of a, β value again.This just makes that existing internal-combustion engines crank-connecting rod mechanism energy conversion efficiency is not high.
The purpose of this utility model is the bent axle of the existing internal-combustion engine of cancellation, and by adopting fork---one-way clutch mechanism, improves the energy conversion efficiency of internal-combustion engine and working life etc.
Its technological scheme is: the bent axle that will have internal-combustion engine now removes, and changing one into is the center with former crankshaft rotating center, and both sides have the rigid bar of equal length, and the utility model is called the double pendulum bar.There is a rigidly connected central gear center of double pendulum bar, is used for energy output.Cylinder, piston and a piston rod respectively are installed on the body at double pendulum bar two ends, and the lower end of piston rod and double pendulum bar two ends are flexibly connected.The distance at two-cylinder piston center is 2L, and the distance at the pin-and-hole center at double pendulum bar two ends and the piston center of local terminal cylinder is L1, and the distance at pin-and-hole center, double pendulum bar two ends and double pendulum bar center is L+L
1L must be greater than piston stroke S during design, and piston stroke S can suitably extend than existing internal-combustion engine simultaneously.The pivot angle of double pendulum bar in whole piston stroke is less than 60 degree like this, and piston rod pivot angle β is about 5 degree.Act on the P that makes a concerted effort on the piston
ΣPass to the double pendulum bar by piston rod, pass to output shaft through central gear, overrunning clutch again, make the output shaft rotation and energy is exported.
Major advantage of the present utility model is:
1, can improve the effective efficiency of internal-combustion engine, reduce fuel consumption rate.
2, the loss of reducing friction in the working life of having improved the critical movements part, has prolonged service cycle.
3, turning torque is very little, and the working state of internal-combustion engine will compare steadily.
4, it is lower than bent axle to change the part manufacture difficulty of structure, and axial dimension shortens simultaneously, makes overall structure more compact.
The mathematic(al) representation of gained active force is P on the double pendulum bar
Σ[sin (alpha+beta)/cos β].Because of α finishes to 120 degree since 60 degree, β is also very little, so the gained active force is exactly from about 0.9P on the double pendulum bar
ΣTo P
ΣArrive about 0.9P again
ΣBetween change, do not have null value, the energy conversion efficiency of internal-combustion engine is improved greatly.Very little because of β simultaneously, piston is also just very little to the side pressure of casing wall; Only spend with interior swing 60 because of the double pendulum bar again, the pin-and-hole of piston rod lower end is very little with respect to the rotation of double pendulum lever pin axle; The frictional loss that this has just reduced between these parts has improved working life.
Deficiency of the present utility model is that the number of spare parts increase is more, and structure is complicated.
Fig. 1 is the utility model master TV structure schematic representation, Fig. 2 is the plan structure schematic representation, Fig. 3 is the main export structure schematic representation of looking, Fig. 4 is for overlooking the export structure schematic representation, Fig. 5 is a two-stroke Otto cycle master TV structure schematic representation, Fig. 6 is the left TV structure schematic representation of two-stroke Otto cycle, and Fig. 7 is connecting rod energy conversion relation mechanics figure.In conjunction with the accompanying drawings, the structure of the fork internal-combustion engine of narration the utility model release.
The utility model fork internal-combustion engine is by cylinder (1), piston (2), piston rod (3), double pendulum bar (4), central gear (5), sun gear shaft O
1, double pendulum lever pin axle (6), single wobbling pole (7), single wobbling pole bearing pin (8), connecting rod (9), flywheel (10), flywheel shaft O
2, eccentric pin shaft (11), gear (12), overrunning clutch (13), output shaft O
3, gear (14), overrunning clutch (15), an axle O passes a bridge
4, carrier gear (16), (17) form.
Cylinder (1), piston (2), piston rod (3), double pendulum bar (4), sun gear shaft O
1, double pendulum lever pin axle (6), single wobbling pole (7), single wobbling pole bearing pin (8), connecting rod (9), flywheel (10), flywheel shaft O
2, eccentric pin shaft (11) forms transformation of energy part of the present utility model.On the body at double pendulum bar (4) two ends a cylinder (1) is installed respectively, piston set (2) is housed in the cylinder, the lower end pin-and-hole of piston rod (3) is connected with double pendulum lever pin axle (6) with double pendulum bar (4) outer end pin-and-hole, between should relatively rotate.Double pendulum bar (4) outer end pin-and-hole center to center gear shaft O
1The distance at center is L+L
1,
About.Its effect is when the gas in the jar swelling pressure are the highest, piston rod (3) is in cylinder-bore axis overlaps, and this coincidence is occurred twice in a stroke.So just make piston rod (3) a spot of swing be arranged, help the lubricated of piston rod (3) lower end pin-and-hole along the cylinder-bore axis both sides.Double pendulum bar central shaft is sun gear shaft O also
1On rigidly connected single wobbling pole (7) is installed.Single wobbling pole (7) one ends have a single wobbling pole bearing pin (8), are connected with eccentric pin shaft (11) on the flywheel (10) by connecting rod (9), and by the stroke S and the upper and lower stop of eccentric distance e control piston (2).The flywheel that rotates (10) plays the energy storage effect and keeps the motion normally of all mechanisms of internal-combustion engine with cooperatively interacting.Like this, go up effect P with joint efforts at piston (2)
ΣEffect under, existing rotatablely moving of I. C. engine crankshaft become double pendulum bar (4) with sun gear shaft O
1Be the center, pivot angle α spends the swing of spending in these best efficiency ranges to 120 60.
This mechanism both had been suitable for Otto cycle, also was suitable for diesel cycle.But the structure of two-stroke Otto cycle and small-power two-stroke diesel cycle should design by Fig. 5, Fig. 6.Utilize the following cylinder space of piston (2) to make scavenging, air-exchanging chamber, cylinder (1) lower end is established the pilot hole (18) of a piston rod (3) and is added Sealing (19), just piston rod (3) only can move up and down and can not swing, and sets up a pair of fork connecting rod (20) simultaneously.And with short pin shaft (21) double pendulum bar (4) is connected with double pendulum bar connecting rod (20) one ends, with the axle (22) of having strong market potential the other end of piston rod (3) with double pendulum bar connecting rod (20) is connected, replace the swing of piston rod (3) by the swing of double pendulum bar connecting rod (20).
Cylinder number of the present utility model must become even number, and every pair of cylinder is established a double pendulum bar (4), a central gear (5).When the cylinder number more for a long time, can expansion stroke be staggered in order by corresponding mechanism such as distributions.In case of necessity can also be at flywheel shaft O
2On adorn the stagger flywheel (10) of respective angles of two or more throw of eccentric, and corresponding single wobbling pole (7), single wobbling pole bearing pin (8), connecting rod (9), eccentric pin shaft (11), the cylinder in its same expansion stroke is staggered, with further balance output torque, under this state, central shaft O
1Should be separated into independently corresponding separately hop count.
Central gear (5), gear (12), overrunning clutch (13), output shaft O
3, gear (14), overrunning clutch (15), carrier gear (16), (17), an axle O passes a bridge
4Form energy output system of the present utility model (Fig. 3, Fig. 4).Central gear (5) is installed in sun gear shaft 0
1Go up and be and be rigidly connected, central gear (5) meshes for tooth with gear (12), (14).Gear (12) is one group with overrunning clutch (13), and gear (14) is another group with overrunning clutch (15), and its structure is that the outer ring is gear (12), (14), and inner ring and other parts are formed overrunning clutch (13), (15).Carrier gear (16), (17) are tooth engagement, output shaft O
3With overrunning clutch (13), carrier gear (17) for being rigidly connected, an axle O passes a bridge
4With overrunning clutch 15), carrier gear (16) is for being rigidly connected.When expanding acting in the cylinder (1) on the right side, the P that makes a concerted effort of the effect on the piston (2)
ΣDrive central gear (5) and clockwise rotate by this end piston rod (3), double pendulum bar (4), central gear (5) drives output shaft O by gear (12) and overrunning clutch (13)
3To be rotated counterclockwise and energy exported.When expanding acting in the cylinder (1) on the left side, the P that makes a concerted effort of the effect on the piston (2)
ΣDrive central gear (5) and rotate counterclockwise by this end piston rod (3), double pendulum bar (4), central gear (5) is done by gear (14) and overrunning clutch (15) drive carrier gear (16) and is clockwise rotated, and drives carrier gear (17) and output shaft O by carrier gear (16) again
3Do and be rotated counterclockwise and energy is exported.During normal operation, the cylinder on the right side (1) is if interior piston (2) is descending, and the piston (2) in the cylinder on the left side (1) must be up.Otherwise the cylinder on the left side (1) inner carrier (2) is descending, and the piston (2) in the cylinder on the right side (1) must be up.No matter right side cylinder (1) or left side cylinder (1), so long as piston (2) is up, overrunning clutch (13), (15) all are in idling conditions.
In this mechanism, each will adorn two gears (12), (14) and two overrunning clutch (13), (15) that outbound course is opposite to cylinder (1), and gear (12), (14) number of teeth equate.Change the gear ratio of (5) and (12), (14), can change output shaft O
2Rotating speed.
In this mechanism, a flywheel (10) needs only a pair of carrier gear (16) and (17), and (16) equate with the number of teeth of (17).A plurality of when having eccentric flywheel (10) when being necessary to load onto, carrier gear (16), (17) need corresponding logarithm, bridge gear shaft O
3Also need be divided into independently corresponding hop count.
In addition, energy output also can be exported with the mode of hydraulic pressure or air pressure separately, and promptly each cylinder (1) directly drives an oil hydraulic cylinder that is complementary or a pneumatic cylinder by double pendulum bar (4).As required, also can machinery and hydraulic pressure or this dual mode mixing use simultaneously of air pressure.
Inertial force during internal combustion engine has the reciprocal inertia force of all inertial force in the garden of fly wheel system and piston set.The easy balance of garden week inertial force.And the reciprocal inertia force of piston set from the testing machine working order (this testing machine is not also installed output mechanism at present) of theory analysis and my completed two-stroke Otto cycle fork internal-combustion engine, all is necessary to increase a cover specialized agency and solves very much.Its solution has energy storage balancing method and two kinds of acting balancing methods.The energy storage balancing method is exactly on the frame of piston rod (3) upper and lower, the spring of one coupling respectively is set, when making piston (2) move near last lower dead center, directly this spring is compressed by piston rod (3), absorb most of inertia energy of this moment by spring, after lower dead center in piston (2) arrival and commutation motion, the spring delivered energy helps piston (2) to continue operation.Thereby the reciprocal inertia force that be harmful to this moment becomes useful reciprocal inertia force.The acting balancing method changes spring into hydraulic pressure or pneumatic cylinder exactly, can do pressurization system or the lubricated wet goods back work of discharge pressure with hydraulic pressure or air pressure.More than two kinds of methods also can mix simultaneously and use.These two kinds of balancing methods all require organically to connect with velocity of piston, and when promptly velocity of piston was high, spring or liquid, atmospheric pressure will correspondingly increase.When velocity of piston was zero, spring or liquid, atmospheric pressure also correspondingly were zero.Velocity of piston suitably can be reduced than existing internal-combustion engine in the design simultaneously.So both help balance reciprocal inertia force better, maximally utilised reciprocal inertia force, do not occurred additional drag in the time of can making engine starting again.
Claims (3)
1. fork internal-combustion engine is by cylinder (1), piston (2), piston rod (3), double pendulum bar (4), central gear (5), sun gear shaft O
1, double pendulum lever pin axle (6), single wobbling pole (7), single wobbling pole bearing pin (8), connecting rod (9), flywheel (10), flywheel shaft O
2, eccentric pin shaft (11), gear (12), overrunning clutch (13), output shaft O
3, gear (14), overrunning clutch (15), an axle O passes a bridge
4Carrier gear (16), (17) form, it is characterized in that on the body at double pendulum bar (4) two ends a cylinder (1) being installed respectively, piston set (2) is housed in the cylinder, the lower end pin-and-hole of piston rod (3) is connected with double pendulum lever pin axle (6) with double pendulum bar (4) outer end pin-and-hole, between can relatively rotate, double pendulum bar central shaft also is equipped with rigidly connected single wobbling pole (7) on the sun gear shaft O1, one end of single wobbling pole (7) has a single wobbling pole bearing pin (8), be connected with eccentric shaft (11) on the flywheel (10) by connecting rod (9), central gear (15) is installed on the sun gear shaft O1 and is and is rigidly connected, central gear (5) and gear (12), (14) be the tooth engagement, gear (12) is one group with overrunning clutch (13), gear (14) is another group with overrunning clutch (15), its structure is that the outer ring is gear (12), (14), inner ring and other parts are formed overrunning clutch (13), (15), carrier gear (16), (17) be the tooth engagement, output shaft O3 and overrunning clutch (13), carrier gear (17) is for being rigidly connected gap bridge axle O4 and overrunning clutch (15), carrier gear (16) is for being rigidly connected.
2. the fork internal-combustion engine of narrating according to claim 1, it is characterized in that for two stroke IC engine, the lower end of cylinder (1) is established the pilot hole (18) of a piston rod (3) and is added Sealing (19), set up a pair of fork connecting rod (20) simultaneously, and with short pin shaft (21) double pendulum bar (4) is connected with double pendulum bar connecting rod (20) one ends, axle (22) is connected the other end of piston rod (3) with double pendulum bar connecting rod (20) with having strong market potential.
3. the fork internal-combustion engine of narrating according to claim 1 or claim 2 is characterized in that respectively being provided with a spring that mates on the frame of piston rod (3) upper and lower, also spring can be changed into hydraulic pressure or pneumatic cylinder, or mix simultaneously and use.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 98230001 CN2343357Y (en) | 1998-01-01 | 1998-01-01 | Swing stem IC engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 98230001 CN2343357Y (en) | 1998-01-01 | 1998-01-01 | Swing stem IC engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2343357Y true CN2343357Y (en) | 1999-10-13 |
Family
ID=33979780
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 98230001 Expired - Fee Related CN2343357Y (en) | 1998-01-01 | 1998-01-01 | Swing stem IC engine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2343357Y (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007033593A1 (en) * | 2005-09-22 | 2007-03-29 | Huarong Xia | Crankshaftless engine |
| CN101117916B (en) * | 2007-07-12 | 2010-09-08 | 闫官清 | Double-pendulum internal-combustion engine |
| WO2011029221A1 (en) * | 2009-09-14 | 2011-03-17 | 中国农业大学 | Piston-type large torque engine |
| CN102094709A (en) * | 2010-09-17 | 2011-06-15 | 肖多娇 | Piston lever type actuating device |
| CN101440746B (en) * | 2008-12-23 | 2011-07-20 | 江苏省高新技术发展研究所有限公司 | Implementing method and apparatus of stepless speed regulating eccentric swinging type internal combustion engine |
| CN102787942A (en) * | 2012-08-31 | 2012-11-21 | 杨永顺 | External combustion engine and transmission mechanism thereof |
| 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 |
| CN117404177A (en) * | 2023-11-27 | 2024-01-16 | 北京氢璞创能科技有限公司 | Internal combustion engine |
-
1998
- 1998-01-01 CN CN 98230001 patent/CN2343357Y/en not_active Expired - Fee Related
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007033593A1 (en) * | 2005-09-22 | 2007-03-29 | Huarong Xia | Crankshaftless engine |
| CN101117916B (en) * | 2007-07-12 | 2010-09-08 | 闫官清 | Double-pendulum internal-combustion engine |
| CN101440746B (en) * | 2008-12-23 | 2011-07-20 | 江苏省高新技术发展研究所有限公司 | Implementing method and apparatus of stepless speed regulating eccentric swinging type internal combustion engine |
| WO2011029221A1 (en) * | 2009-09-14 | 2011-03-17 | 中国农业大学 | Piston-type large torque engine |
| CN102094709B (en) * | 2010-09-17 | 2015-01-21 | 肖多娇 | Piston lever type actuating device |
| CN102094709A (en) * | 2010-09-17 | 2011-06-15 | 肖多娇 | Piston lever type actuating device |
| CN102787942A (en) * | 2012-08-31 | 2012-11-21 | 杨永顺 | External combustion engine and transmission mechanism thereof |
| CN102787942B (en) * | 2012-08-31 | 2015-04-22 | 杨永顺 | External combustion engine and transmission mechanism thereof |
| 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 |
| CN117404177A (en) * | 2023-11-27 | 2024-01-16 | 北京氢璞创能科技有限公司 | Internal combustion engine |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |