CN1103408C - Internal combustion engine with hydraulic drive - Google Patents
Internal combustion engine with hydraulic drive Download PDFInfo
- Publication number
- CN1103408C CN1103408C CN98119020A CN98119020A CN1103408C CN 1103408 C CN1103408 C CN 1103408C CN 98119020 A CN98119020 A CN 98119020A CN 98119020 A CN98119020 A CN 98119020A CN 1103408 C CN1103408 C CN 1103408C
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- plunger
- internal combustion
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- curve
- piston
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Abstract
The present invention relates to a new inner combustion engine using the drive of a hydraulic body to replace a crank-connecting rod mechanism, particularly to an inner combustion engine with hydraulic drive, which is formed by combining opposed piston inner combustion cylinders, plunger pumps at both ends of the inner combustion engine with hydraulic drive and a plunger type inner curve or outer curve oil motor unit. A cam curve controls and optimizes the speed distribution of the opposed pistons, and a hydraulic cylinder is provided with a liquid supplementing mechanism, a cooling mechanism and a liquid exchanging mechanism.
Description
Technical field:
The invention belongs to a kind of internal-combustion engine that substitutes connecting rod with hydraulic transmission.
Background technique:
Internal-combustion engine adopts connecting rod, the to-and-fro motion of piston is changed into rotatablely moving, and is to go up a century to fix constant tradition.But connecting rod is not perfection, it has for example piston motion rule of many congenital unsurmountable limitation systems to be subjected to the restriction of garden week conversion of motion, can not be by optimizing the requirement design, the impossible complete equilibrium of movement parts, the quantity of friction member is many or the like, makes the development of internal-combustion engine be subjected to certain limitation.Therefore, have for these years allly to replace the imagination and the trial-production of connecting rods,, wherein also comprise hydraulic transmission as rotary-piston etc. with other forms.But for various reasons, main probably because the solution of technical problem, do not attain perfect, fail so far a kind of without connecting rod really can with the internal-combustion engine of traditional combustion engine competition.
Summary of the invention:
The objective of the invention is to replace connecting rod with hydraulic transmission, to overcome its geneogenous defective, can cross over some other obstacles in the present internal combustion engine development again simultaneously, the performance of special internal-combustion engine reaches a new high.
Internal combustion engine with hydraulic drive system forms (seeing accompanying drawing 1) by some unit combination.Each unit comprises internal combustion cylinder and hydraulic transmission two partly.The internal combustion cylinder partly adopts the opposed pistons structure.The two opposed pistons bottom dead-centres, one end connects a hydraulic plunger, and in company with piston reciprocates, in fact this is two important actor plunger type hydraulic pumps in the oil hydraulic cylinder at two ends.The oil cylinder the other end also respectively has a plunger, and roller is arranged at the top and radially inner curve or external curve cam ring contact.This plunger is the same with hydraulic pump plunger also with piston reciprocates by the fluid column in the oil hydraulic cylinder, to promote the cam ring rotation on both sides.Be actually two plunger types radially inner curve or the external curve oil hydraulic motor that are contained in same output shaft two ends.When piston is near inner dead centre, the expansion of catching fire of cylinder combustion oil, the ascent stage curve on the plunger actuating cam ring of oil hydraulic motor makes cam ring rotation, outputting power.Piston is to the bottom dead-centre, and cam ring relies on multi-cylinder effect and flywheel effect to continue rotation, and it is inside to make the descending branch curve promote piston, is to be compression stroke.Work cycle (two strokes) each time in the cylinder be equivalent to the angle that cam ring rotates a complete curved section, so the rotating speed of output shaft can slow down with the relative piston reciprocating frequence of complete curve hop count on the cam ring with integral multiple.If unit number is even numbers, oil hydraulic motor is made symmetry to the cam ring curve and is arranged, when the complete curve number on the cam ring also was even numbers, except that the moment of torsion output of output shaft, other various external force all can be owing to balance is offset.
The porting of internal combustion cylinder part is arranged on the cylinder two ends, and an end is a steam inlet, and the other end is a relief opening, and its keying enjoys the opposed pistons at two ends to control, and the motion of opposed pistons is controlled by the shape of cams at two ends curve then respectively again.Therefore the keying of porting, successively the speed of program and an opening and closing time and a piston jade-like stone stroke is distributed, and all can be controlled and is optimized by the curve shape of cams at two ends ring.
Because complete machine system is formed by unit combination, utilizes same unit, the curve number on available different unit number and the different cam ring is formed a series of types of different capabilities, different rotating speeds, to satisfy the needs of various different purposes.
According to said structure, internal combustion engine with hydraulic drive has many good qualities than general internal-combustion engine, now selects its main being described as follows:
1. opposed pistons has the movement parts symmetrical balance, friction, do not need cylinder head not need many advantages such as air inlet and exhaust valve, but when using connecting rod, exerting oneself of two ends be incorporated into an output shaft output, structure is quite complicated, and when using hydraulic transmission, as mentioned above, use opposed pistons, very convenient.
Since opposed pistons together with all movement parts such as hydraulic plunger symmetrical balance all, so complete machine friction, noise are little; Add that having cancelled intake and exhaust cuts down, noise more can reduce.
3. be located at the cylinder two ends owing to the porting branch, an end air inlet, an end exhaust forms uniflow scavenging, makes scavenging perfect.The velocity distribution of face amount and keying program and whole piston motion is all controlled during porting.Because the compressibility of fluid column, buffer function helps improving supercharging level, and therefore thermal performance can improve.Add factors such as reducing the cylinder head cooling loss, the thermal efficiency can improve.
4. because piston and fuel feed pump plunger do not have lateral force, the loss of reducing friction.Complete machine only needs two main bearings, and except that output torque, because the unit symmetrical balance, and the stressed hardly and zerofriction force of main bearing.Pump directly is connected with motor, does not have distributor.More than all factors, all impel the raising mechanical efficiency.
5. two strokes add opposed pistons, and exerting oneself of bulk density is inevitable bigger.More, only need the light hydraulic support of reaction torque because not vibration can be saved heavy fuselage and support.Add factors such as not needing reduction gear box, so complete machine has clear superiority from the volume weight aspect.
6. modular construction helps standardization, seriation and the scale and benefit using, safeguard and make.Part is few in addition, does not have big part, and manufactory's investment reduces, and cost reduces.
Description of drawings:
Embodiments of the invention as shown in drawings
Fig. 1 is a layout of general plan
Fig. 2 is cam curve figure
Structure and system diagram that Fig. 3 replenishes, cools off and renew for hydraulic medium
Fig. 4 is the unsteady connection diagram of piston and hydraulic pump plunger
Embodiment:
Complete machine is formed (accompanying drawing 1) by some unit, and the middle part is the internal combustion cylinder, and the both sides is an oil hydraulic cylinder, and two ends are inlet end cam and exhaust end cam.The relative cam in unit is made symmetry and is arranged.
Modular construction is seen accompanying drawing one, and wherein 1 is the admission end hydraulic pump plunger, and 2 is the inlet end piston, 3 is cylinder, and 4 is oil injecting nozzle, and 5 is the exhaust end piston, 6 is the exhaust end pump plunger, and 7 is inlet end oil hydraulic motor plunger, and 8 is suction port, 9 is relief opening, 10 is exhaust end motor plunger, and 11 is the inlet end cam, and 12 is the exhaust end cam, 13,14 is roller.
When 2,5 two-pistons during near the inner dead centre position, fire burns in oil injecting nozzle 4 oil spouts, and cylinder 3 internal pressures raise, and promote piston 2,5 and pump plunger 1,6 layman, up thereupon actuating cam ring 11, the 17 rotation works done of motor plunger 7,10.Curve major part on the cam ring 11,12 is identical, but near bottom dead-centre place, variant slightly.Cam ring 12 makes exhaust end piston 5 that relief opening 9 is opened earlier, and combustion gas promptly effluxes rapidly, and inlet end cam ring 11 makes inlet end piston 2 that suction port 8 is opened after a while, and pressurized air enters cylinder, the beginning scavenging.For the time face amount that obtains requiring, the cams at two ends ring all outside the dead center position one section garden segmental arc is arranged, it is motionless that promptly piston can be still in the bottom dead-centre, to prolong the scavenging time.After the static segment, piston 2,5 experts, the exhaust end cam ring is closed relief opening 9 earlier exhaust end piston 5, and this moment, suction port 8 was still opened, and continued inflation, can improve inflation pressure like this.Then piston 2 is closed suction port 8.Piston 2,5 continues expert, the beginning compression stroke, and until near inner dead centre the time, oil spout is caught fire, and cylinder 3 internal pressures improve, and make the piston layman, and the beginning expansion stroke moves in circles like this.
Because the motion of piston 2,5 is controlled by the curve shape of cams at two ends ring 11,12, optimize the curve design of cam ring, can make the interior compression of cylinder, swollenly rise, exhaust, scavenging, inflate each process and reach the optimum state.Accompanying drawing two is the plotted curve of four complete segment on the cam ring 11,12.Because of the exhausted major part of two ends curved section is all identical, it is partly slightly different to have only porting to open and close, and therefore two curves is lumped together, and can show the priority program that porting opens and closes.Footnote 1 refers to the inlet end curve among the figure, and footnote 2 refers to exhaust end curve, common ground on the finger two ends curve of no footnote.Cam ring turns to and is clockwise direction.Curved section comprises expansion arc ac
2, a point is an inner dead centre, until c
2The point exhaust open.Exhaust section c
2c
1, until c
1The point suction port is opened, the beginning scavenging.Scavenging section c
1g
2, until g
2The point exhaust close.Inflation section g
2g
1, until g
1The point inlet close, g
1A is the compressing section.Bottom dead-centre place also has static segment e
2f
2, e
1f
1, to prolong the scavenging time.Compression, two-piston and the pump plunger movement velocity equates, direction adds motor plunger symmetric arrangement on the contrary in the expansion curve section, so the whole symmetrical balances of all reciprocating parts, no external force, friction.The section of rising of splashing incipient stage ab section is high accelerating sections, make the two ends piston that big acceleration be arranged, shorten the time of high temperature in the cylinder on the one hand, reduce cooling loss, big on the other hand acceleration can make the inertial force of to-and-fro motion assembly, offset the pressure in a part of cylinder, to alleviate the contact stress between motor plunger upper roller and the cam ring curve.Also comprise c in the curve
1d
1, c
2d
2, f
2g
2, f
1g
1Make porting all speed open speed and close, to reduce the restriction loss of air-flow.When two-piston 2,5 during near the bottom dead-centre, the two ends curve is variant slightly.But difference is very little, does not influence the symmetrical balance of two-piston.
Stable compression ratio requires the length of fluid column in the oil hydraulic cylinder to remain unchanged.But the leakage in plunger gap can not be avoided fully, therefore fluid infusion at any time, and also amount infused will equal leak volume.Medium in the oil hydraulic cylinder also needs cooling and replacing in addition, and is too high and aging to avoid medium temperature.The system of fluid infusion, cooling and replacing such as accompanying drawing 3.
All hydraulic cylinder motor one end has an adjustable outage 15, and the other end has the fluid infusion hole 16 of a band check valve, and fluid infusion pressure is by a little pump supply, a little higher than barometric pressure of setting pressure.Be equivalent to piston bottom dead-centre place when the motor plunger arrives, plunger base is opened outage 15, and the oil hydraulic cylinder internal pressure is reduced to rapidly near barometric pressure, and this moment, the check valve in repairing hole was opened automatically, and fluid infusion enters in the cylinder.One stops 17 (seeing accompanying drawing 3) is arranged on the piston bottom dead-centre place cylinder, makes bottom dead-centre fixed-site, this moment the motor plunger also in the outermost end fixed position, no matter therefore leakage of oil amount size in the hydraulic system, liquid column length immobilizes, compression ratio is also stablized constant.Regulate the flow of outage oil extraction, and continuous automatic liquid supply, both can play cooling action, can work to change liquid again.
In order to reduce the impact of piston and stops 17, on the cam curve at c
1e
1, c
2e
2One section section d is at a slow speed arranged in the section
2e
2, d
1e
1, it is very low that velocity of piston is reduced to, and still machinery or hydraulic damping device can be set on the stops 17, and the collision of piston and stops is controlled within the permissible range.
The axial position of stops 17 on cylinder has a controlling mechanism.The outer time-delay of stops makes piston bottom dead-centre extension, and then fluid column shortens, and compression ratio reduces, otherwise prolongs in the stops 17, promptly prolong in the piston bottom dead-centre, and the fluid column lengthening, then compression ratio strengthens.Adjust the axial position of stops 17, can adjust compression ratio.Be to be variable compression ratio.
For concentricity and the parallelism that guarantees internal combustion cylinder inner carrier and hydraulic pump plunger, reduce the machining accuracy of oil hydraulic pump fluid cylinder and internal combustion cylinder simultaneously, being connected between piston and the pump plunger, adopt floating structure, as accompanying drawing four, piston base and plunger contacting point are the plane, and plunger and piston contacting point are sphere.Gapped between around the cover cap that plunger is connected with piston, but the therefore equal self adaption of the concentricity of the relative piston of plunger and parallelism.
Claims (5)
1. by opposed pistons internal combustion cylinder and base for post formula oil hydraulic pump, plunger type is the internal combustion engine with hydraulic drive formed of inner curve or external curve oil hydraulic motor radially, it is characterized in that steam-cylinder piston directly is connected with hydraulic pump plunger, there is fluid column to be communicated with between pump plunger and the motor plunger, internal combustion cylinder and hydraulic pump cylinder, oil hydraulic motor cylinder component units, some oil hydraulic motor cylinders middle part is a force-output shaft, respectively there is a cam ring at two ends, the complete machine unit number is even numbers, complete curved section on the cams at two ends ring also is even numbers, the relative cam ring curve of oil hydraulic motor is made symmetry and is arranged, complete curved section control and the speed of optimizing the whole stroke of piston are distributed on the cam ring, and fluid infusion is arranged on the oil hydraulic cylinder, cooling and liquid changing device.
2. by the described internal combustion engine with hydraulic drive of claim 1, each the complete curved section that it is characterized in that cams at two ends ring upper curve, comprise expansion arc, high accelerating sections, porting fast opening and closing section, the section of going slowly, static segment and compressing section, the two ends curve is except that the intake and exhaust part, all identical, the curve of two ends intake and exhaust parts is variant slightly to be that the relief opening of exhaust end is opened earlier earlier than the suction port of inlet end and closed.
3. by the described internal combustion engine with hydraulic drive of claim 1, it is characterized in that fluid infusion, cooling, liquid changing device are that oil hydraulic motor one end has a can regulate oil drainage hole that controlled by the motor plunger base in the fluid column, the other end has the fluid infusion hole of a band check valve in the fluid column.
4. by the described internal combustion engine with hydraulic drive of claim 1, it is characterized in that at opposed pistons bottom dead-centre place one stops being arranged on the opposed internal combustion cylinder, this stops can be adjusted axial position according to desired compression ratio.
5. by the described internal combustion engine with hydraulic drive of claim 1, it is characterized in that internal combustion cylinder piston and cylinder plunger float links together, piston base and plunger contacting point are the plane, and plunger end and piston base plane contact place are sphere, and the free gap is arranged around connector that both connect and the plunger.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN98119020A CN1103408C (en) | 1998-09-25 | 1998-09-25 | Internal combustion engine with hydraulic drive |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN98119020A CN1103408C (en) | 1998-09-25 | 1998-09-25 | Internal combustion engine with hydraulic drive |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1249397A CN1249397A (en) | 2000-04-05 |
| CN1103408C true CN1103408C (en) | 2003-03-19 |
Family
ID=5226218
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN98119020A Expired - Fee Related CN1103408C (en) | 1998-09-25 | 1998-09-25 | Internal combustion engine with hydraulic drive |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1103408C (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE602007010317D1 (en) * | 2007-11-05 | 2010-12-16 | Delphi Tech Holding Sarl | liquid pumps |
| CN101532427B (en) * | 2008-03-15 | 2013-04-03 | 熊艳 | Four-stroke hydraulic engine without crank link mechanism |
| CN102425494B (en) * | 2011-12-19 | 2013-04-24 | 欧益忠 | Hydraulic control type opposed piston engine |
| CN103410610A (en) * | 2013-05-31 | 2013-11-27 | 中国人民解放军理工大学 | Piston hydraulic turbine rotation two-stroke engine |
| CN103321745B (en) * | 2013-06-21 | 2015-09-30 | 李琦 | Internal combustion hydraulic composite flooding motor |
| CN112211723B (en) * | 2020-09-11 | 2022-05-27 | 李永志 | Opposed piston single-shaft internal combustion engine |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN85101085A (en) * | 1985-04-01 | 1985-10-10 | 陈友年 | Piston-type hydraulic conveying internal combustion engine with no crankshafts |
| CN2149483Y (en) * | 1993-02-20 | 1993-12-15 | 赵德成 | Multi-pump hydraulic driven piston engine without crankshaft |
-
1998
- 1998-09-25 CN CN98119020A patent/CN1103408C/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN85101085A (en) * | 1985-04-01 | 1985-10-10 | 陈友年 | Piston-type hydraulic conveying internal combustion engine with no crankshafts |
| CN2149483Y (en) * | 1993-02-20 | 1993-12-15 | 赵德成 | Multi-pump hydraulic driven piston engine without crankshaft |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1249397A (en) | 2000-04-05 |
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