CN86102231A - Internal-combustion piston engine - Google Patents
Internal-combustion piston engine Download PDFInfo
- Publication number
- CN86102231A CN86102231A CN198686102231A CN86102231A CN86102231A CN 86102231 A CN86102231 A CN 86102231A CN 198686102231 A CN198686102231 A CN 198686102231A CN 86102231 A CN86102231 A CN 86102231A CN 86102231 A CN86102231 A CN 86102231A
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- China
- Prior art keywords
- stroke
- master cylinders
- auxiliary steam
- steam cylinder
- master
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
- F02B41/02—Engines with prolonged expansion
- F02B41/06—Engines with prolonged expansion in compound cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B75/021—Engines characterised by their cycles, e.g. six-stroke having six or more strokes per cycle
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Exhaust-Gas Circulating Devices (AREA)
- Supercharger (AREA)
- Valve Device For Special Equipments (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
Internal-combustion engine has at least two with the master cylinders of six-stroke work with the auxiliary steam cylinder of two stroke operation.This group cylinder can co-operation, enters relief cylinder at the waste gas of master cylinders and alternately the relief cylinder supercharging is inflated with air before carrying out reexpansion.
Description
The present invention relates to a kind of internal-combustion piston engine that has two master cylinderses at least, master cylinders has suction valve and links to each other with a public auxiliary steam cylinder by intervening valve.Auxiliary steam cylinder alternately is used for the reexpansion of two master cylinders waste gas with the work of two-stroke system in a stroke, be used at least one the outlet valve combustion gas by being provided with on it in a back stroke, and it has the volume times over master cylinders.
In traditional two-stroke piston internal-combustion engine, what comprise primary energy in the fuel respectively 1/3rd has supplied with waste gas and cooling system.Be transformed into remaining 1/3rd energy of mechanical work, because the pneumatic and hydraulic slip in the motor, the useful horsepower that makes motor output is only for being slightly more than 1/4th of input primary energy.
The characteristics of " Otto " fast burn engine are, under the working state when the unit of fuel consumption rate is minimum in the waste gas content of oxynitrides higher; In maximum power rating,, partial combustion increases owing to making the unit of fuel consumption rate.The exhaust after-treatment of doing for minimizing discharge harmful matter has improved the unit of fuel consumption rate too.
The discharge of its fuel consumption and harmful matter all is less than " Otto " motor with same power in the diesel engine of working preferably.But in this internal-combustion engine, also have more than 50% original chemical energy consumption in waste gas and cooling system.The part of waste gas dump energy can be reclaimed engine booster by an exhaust gas turbine is installed.When exhaust gas turbine was installed on the outlet of motor, because the reduction gear box of a costliness of the very high needs of rotating speed, this gear-box also must be adjustable in motor car engine, and causes mechanical loss.
In addition, knownly in " thermal insulation " motor, take heat insulation measures to reduce because the energy loss that caused of cooling.But thus obtained most of energy has improved the dump energy of waste gas, and these energy only can be used by exhaust gas turbine, but cost is very high.
Other some solutions (US-PS4289097 and 4367000, DE-SS3240563) be a kind of six-stroke motor of design, they have only utilized the sub-fraction of institute's off-energy in the cooling system, compare with conventional internal-combustion engine energy loss in waste gas identical or even bigger because be equal to or greater than allowance for expansion by six-stroke circuit total compression volume.How emission of harmful substances does not reduce basically in this motor.
Also have known internal-combustion piston engine in addition, they have at least two four-stroke master cylinderses and a two-stroke auxiliary steam cylinder that is mounted thereon, and are used for utilizing the expansion energy that also is present in waste gas after the working stroke of master cylinders.Yet this moment, the pressure drop in auxiliary steam cylinder was very big, made the utilization ratio of residue expansion energy very low.As the impossible perfect combustion of conventional engines fuel in this motor, emission of harmful substances does not reduce in addition.In EP-OS6747, introduced a kind of like this motor.
The object of the present invention is to provide a kind of simple as far as possible internal-combustion engine, it is provided with the shortcoming of above-mentioned available engine and has higher efficient, the less harmful matter of discharge.This purpose is realized by following characteristics with the internal-combustion engine of the principle work of " Otto " motor and diesel engine by type described in the introduction:
Auxiliary steam cylinder is with independent bent axle work, and its angular velocity is 2/3rds of master cylinders angular velocity of crankshaft,
Before the waste gas of a master cylinders enters auxiliary steam cylinder, can with by another master cylinders precompression fresh air or precompression fresh air-fuel mixture to auxiliary steam cylinder supercharging inflation,
Stagger two master cylinderses of three strokes mutually with the work of six-stroke system, wherein first three stroke is corresponding with first three stroke of general four stroke engine, the reexpansion stroke that always carries out then with auxiliary steam cylinder, in the 5th stroke, suck fresh air or fresh air-fuel mixture, these fresh airs or mixture by precompression, are then inflated the auxiliary steam cylinder supercharging being used in the 6th stroke of cylinder.
The organization plan of internal-combustion engine of the present invention can carry out the burning during pre-expansion stroke in the master cylinders (this stroke is corresponding to the working stroke of common four stroke engine after air-breathing and compression stroke) under the condition in anoxic, and the burning of (during reexpansion) can be carried out under the condition of oxygen enrichment in auxiliary steam cylinder.Oxygen deficiency when burning under high temperature levels in master cylinders makes that the oxidation of nitrogen reduces in the air, in auxiliary steam cylinder,, can under lower temperature, carry out utilizable completely secondary combustion there owing to supercharging in advance makes oxygen excessive.Because temperature is lower, the oxynitrides of Xing Chenging has also reduced there.Perfect combustion has reduced the harmful matter of discharging.
The supercharging inflation of auxiliary steam cylinder fresh air, its pressure is to being approximately pre-expansion stroke pressure at the end in the master cylinders.The pressure loss when having avoided the reexpansion stroke to begin thus.
The middle purge that carries out with air in master cylinders the 5th and six-stroke has reduced cooling loss.Reexpansion in auxiliary steam cylinder has reduced waste gas loss, and the volume of auxiliary steam cylinder is two times to five times of a master cylinders volume.Therefore the primary energy consumption of motor of the present invention significantly reduces, and the efficient that changes mechanical energy from chemical energy into improves.
In addition, the organization plan of internal-combustion engine of the present invention makes before near the reexpansion end of stroke in order to feedback waste gas from that master cylinders of being in the reexpansion end of stroke to being in another master cylinders that first suction stroke ends, all cylinders are communicated with by intervening valve, feedback by waste gas and can adjust the effective aspirated volume of master cylinder.Therefore can under the condition that reduces oxynitrides and carbon monoxide discharge capacity, regulate moment of torsion.
The bent axle of the bent axle of master cylinders and auxiliary steam cylinder is that 2 to 3 driving mechanism is connected by a speed ratio in the motor of the present invention.
Certainly with a plurality of by the internal-combustion engine unit combination that respectively has at least two master cylinderses and an auxiliary steam cylinder of the present invention co-operation together.
The invention will be further described with reference to accompanying drawing by means of the embodiment of an internal-combustion piston engine of the present invention below.
Fig. 1 is the motor schematic representation,
Fig. 2 is the volume change curve in time of three cylinders of motor shown in Figure 1,
Fig. 3 is the different operating state of similar motor shown in Figure 1,
As seen the master cylinders HZ1 and the HZ2 that respectively have a suction valve EV1 and EV2 from Fig. 1.Two master cylinders HZ1 and HZ2 link to each other with a public auxiliary steam cylinder HZ by intervening valve ZV1 and the ZV2 that is contained in above them respectively.The whole system that auxiliary steam cylinder HZ has countercylinder HZ1, a HZ2 and HZ is public outlet valve AV.The swept volume of auxiliary steam cylinder is a master cylinders HZ1 or HZ2 swept volume three times to four times.
The auxiliary steam cylinder piston is worked on independent bent axle NK, and it links to each other with K2 with the bent axle K1 of master cylinders HZ1 and HZ2 by transmission device G.
The position of piston shown in Fig. 1 and valve is corresponding to Fig. 3 .1, just corresponding to the position of piston and valve during with 1 represented time point among Fig. 2.Be represented by dotted lines the position of the piston and the bent axle at dead point on the other side.
Be that (last figure is HZ1 for the swept volume change curve of three cylinder HZ1, HZ2, NZ shown in Fig. 2; Middle figure is NZ; Figure below is HZ2), provided cylinder displacement V(t) relation (bent axle K1, K2, NK angle speed constant) over time.
Its symbolic representation:
IT ... extremely ... 6T first stroke ... extremely ... six-stroke
OT upper dead center UT lower dead centre
The air-breathing K compression of A
The VE NE reexpansion of expanding in advance
VK precompression L supercharging inflation
RE residue expansion V exhaust
ARF waste gas is feedback
Engine behavior shown in Fig. 3 .1 to 3.8 represent master cylinders HZ1 and HZ2 and auxiliary steam cylinder NZ selected as the time shaft t in Fig. 2 in the piston of the time point of 1 to 8 expression and the position of valve.
In Fig. 2, can see two master cylinders HZ1, the following working stroke of HZ2 order, these two master cylinderses are with six stroke work, and they differ three strokes mutually, and alternately the cylinder capacity of auxiliary steam cylinder NZ are exerted an influence.
First stroke (from upper dead center to lower dead centre): suck fresh air or fresh air-fuel mixture; Waste gas enters the master cylinders that is in first end of stroke through auxiliary steam cylinder from being in another master cylinders back coupling that ends near four-stroke.
Second stroke (from lower dead centre to upper dead center): compression inhaled air or air-fuel mixture.
The 3rd stroke (from upper dead center to lower dead centre): burning is expanded in advance.
Four-stroke (from lower dead centre to upper dead center): reexpansion enters auxiliary steam cylinder; Imperfect combustion fuel secondary combustion,
The 5th stroke (from upper dead center to lower dead centre): suck fresh air or fresh air-fuel mixture for the second time.
Six-stroke (from lower dead centre to upper dead center): precompression inhaled air or air-fuel mixture also are inflated to the end of a period pressure that is approximately the 3rd stroke to the auxiliary steam cylinder supercharging.
Relief cylinder NZ is according to the work of Fig. 2 with following stroke order:
First stroke (from upper dead center to lower dead centre):
A) inflate in the upper dead center supercharging by a master cylinders
B) reexpansion, and carry out secondary combustion jointly with another master cylinders where necessary
C) residue expands until lower dead centre
Second stroke (from lower dead centre to upper dead center):
A) by outlet valve AV combustion gas
B) inflate by another master cylinders supercharging at upper dead center
First stroke (from upper dead center to lower dead centre): first stroke as the aforementioned, but be another master cylinders
Second stroke (from lower dead centre to upper dead center): second stroke but be another master cylinders as the aforementioned
In Fig. 3 .1 to Fig. 3 .8, schematically provided the following working state of cylinder:
Fig. 3 .1 is that the piston of master cylinders HZ1 is in its upper dead center and sucks fresh air or fresh air fuel mixture during its first stroke.Master cylinders HZ2 communicates with the auxiliary steam cylinder of supercharging by the intervening valve ZV2 that opens; From the reexpansion stroke of master cylinders HZ2 to auxiliary steam cylinder NZ; Can begin secondary combustion.
Fig. 3 .2 is that the piston of master cylinders HZ1 approaches lower dead centre, and the piston of another master cylinders HZ2 approaches upper dead center.All cylinder HZ1, HZ2, NZ are connected by intervening valve ZV2, ZV1 at this time point, make the end of a period waste gas in this suction stroke be imported into the back coupling of master cylinders HZ1(waste gas), and this piston moves to lower dead centre.
For preventing that waste gas from entering import, the steam inlet valve EV1 of master cylinders HZ1 closes.Can regulate the aspirated volume of master cylinders by this way.
Fig. 3 .3 is the dead point that the piston of master cylinders HZ1, HZ2 has reached them.Intervening valve ZV1, ZV2 close, and suction valve EV2 opens.Compression stroke begins in master cylinders HZ1, is another suction stroke in master cylinders HZ2.Remain expansion to finish its first stroke in auxiliary steam cylinder NZ, piston moves to lower dead centre.
Fig. 3 .4 is the lower dead centre that the piston of auxiliary steam cylinder NZ has reached it, and outlet valve AV opens, the beginning combustion gas.In master cylinders HZ1, HZ2, continue compression and suction stroke.
Fig. 3 .5 is upper dead center and the lower dead centre that the piston of master cylinders HZ1, HZ2 reaches them.Beginning is pre-under the condition of fuel combustion in master cylinders HZ1 expands.The suction valve EV2 of master cylinders HZ2 closes, and precompression begins.The piston of auxiliary steam cylinder NZ is positioned at half position of about up stroke, continues combustion gas.
Fig. 3 .6 is that the piston of master cylinders HZ1, HZ2 is approximately finished their half of stroke at that time.The piston of auxiliary steam cylinder NZ approaches its upper dead center, and the waste gas major part is discharged.Outlet valve AV closes, and the intervening valve ZV2 of master cylinders HZ2 opens.Master cylinders HZ2 is to continuing pre-the expansion among the auxiliary steam cylinder NZ supercharging inflation master cylinders HZ1.
Fig. 3 .7 is lower dead centre and the upper dead center that master cylinders HZ1, HZ2 reach them respectively.The supercharging inflation of auxiliary steam cylinder NZ finishes, and its piston also is near upper dead center in the way of downward dead point motion.Intervening valve ZV1 opens, and intervening valve ZV2 closes, and suction valve EV2 opens.From the reexpansion stroke of master cylinders HZ1 to auxiliary steam cylinder NZ; Secondary combustion among the auxiliary steam cylinder NZ can begin.This state is corresponding with Fig. 3 .1, but master cylinders HZ1 and HZ2 to have exchanged.
Fig. 3 .8 is that state is corresponding with Fig. 3 .2, but master cylinders HZ1, HZ2 to have exchanged.
Claims (4)
1, the internal-combustion piston engine that has two master cylinderses (HZ1, HZ2) at least, master cylinders have suction valve (EV) and link to each other with a public auxiliary steam cylinder (NZ) by intervening valve (ZV).Auxiliary steam cylinder is with the work of two-stroke system and alternately be used for the waste gas reexpansion of two master cylinderses (HZ1, HZ2) in a stroke, and in the next stroke of following by being arranged at least one outlet valve (AV) combustion gas above it.Auxiliary steam cylinder has the volume times over master cylinders (HZ1, HZ2), it is characterized by;
Auxiliary steam cylinder (NZ) is gone up work at its independent bent axle (NK), and its angular velocity is 2/3rds of master cylinders (HZ1, HZ2) bent axle (K1 and K2) angular velocity.
Auxiliary steam cylinder (NZ) can be by being inflated by another master cylinders (HZ2, HZ1) precompressed fresh air or precompressed fresh air-fuel mixture supercharging before the waste gas of a master cylinders (HZ1, HZ2) enters.
Staggering these two master cylinderses (HZ1, HZ2) of three strokes mutually can be by the work of six stroke systems, and wherein three strokes are corresponding to first three stroke of common four stroke engine, the reexpansion stroke of following that always carries out with auxiliary steam cylinder.The 5th stroke sucks fresh air or fresh air-fuel mixture, and these fresh airs or mixture by precompression, are then inflated the relief cylinder supercharging being used in the 6th stroke of master cylinders.
2, according to the described internal-combustion piston engine of claim 1, it is characterized by, before the end of a period near reexpansion, for waste gas being feedback to being in another master cylinders that first suction stroke ends from that master cylinders (HZ2 or HZ1) of being in the reexpansion end of stroke with from auxiliary steam cylinder (NZ), all cylinders (HZ1, HZ2, NZ) can be communicated with to get up by intervening valve (ZV), and at this moment the effective aspirated volume of master cylinders (HZ1 and HZ2) can be feedback by waste gas and be adjusted.
3, according to claim 1 or 2 described internal-combustion piston engines, it is characterized by, burning in the master cylinders (HZ1, HZ2) (during pre-expansion stroke) can be carried out under the condition in anoxic, and in auxiliary steam cylinder (NZ) burning can condition at oxygen enrichment under (during the reexpansion stroke) carry out.
4, according to the described internal-combustion piston engine of one of claim 1 to 3, it is characterized by, the bent axle of master cylinders (HZ1, HZ2) and the bent axle of auxiliary steam cylinder (NZ) are that 2 to 3 driving mechanism (G) couples together by a velocity ratio.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AT990/85 | 1985-04-02 | ||
| AT99085A AT397838B (en) | 1985-04-02 | 1985-04-02 | PISTON PISTON ENGINE |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN86102231A true CN86102231A (en) | 1986-12-31 |
Family
ID=3504407
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN198686102231A Pending CN86102231A (en) | 1985-04-02 | 1986-04-01 | Internal-combustion piston engine |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP0200714A3 (en) |
| CN (1) | CN86102231A (en) |
| AT (1) | AT397838B (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2005042944A1 (en) * | 2003-08-06 | 2005-05-12 | Shengli Zhang | Piston type internal-combustion engine with second expanding operation |
| CN100360773C (en) * | 2006-04-06 | 2008-01-09 | 郑哲立 | Superhigh boosting double-circulation variable discharge I.C. engine |
| CN100449127C (en) * | 2006-11-20 | 2009-01-07 | 张建元 | Divided cylinder type diesel engine |
| CN108625981A (en) * | 2018-05-03 | 2018-10-09 | 哈尔滨工程大学 | A kind of diesel engine with assistant cylinder |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BE1002364A4 (en) * | 1988-12-30 | 1991-01-15 | Schmitz Gerhard | TWO - STAGE INTERNAL COMBUSTION ENGINE. |
| IT1260918B (en) * | 1993-04-20 | 1996-04-29 | Fiat Auto Spa | INTERNAL COMBUSTION ENGINE WITH THREE CYLINDERS OF WHICH A SUPPLY AND EXHAUST INTERMEDIATE. |
| GB2339844A (en) * | 1998-07-24 | 2000-02-09 | John Eric Dowell | Quieter parallel-twin four-stroke i.c. engine with additional expansion cylinder |
| US7143725B1 (en) | 2005-11-22 | 2006-12-05 | Lung Tan Hu | Dual six-stroke self-cooling internal combustion engine |
| DE102008049088B4 (en) * | 2008-09-26 | 2019-07-25 | Audi Ag | Internal combustion engine with expansion cylinders with variable piston stroke |
| WO2013038228A1 (en) * | 2011-09-18 | 2013-03-21 | Gabora Akram Mohammed Abbashar | Six stroke internal combustion engine |
| DE102013221937B4 (en) | 2012-11-02 | 2021-08-05 | GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) | Piston composite internal combustion engine with expander stroke reduction |
| CN104179570B (en) * | 2014-07-09 | 2017-05-17 | 中国人民解放军国防科学技术大学 | Microminiature thermo-motive power generating set |
| AT518217A1 (en) * | 2015-12-15 | 2017-08-15 | Ing Markus Dornauer Dipl | Use of exhaust enthalpy in the two-stroke diesel engine |
| CN112555022B (en) * | 2020-12-28 | 2022-04-05 | 高勇立 | Four-to-two moving cylinder two-stroke engine |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE299978C (en) * | ||||
| FR364048A (en) * | 1906-03-12 | 1906-08-13 | Felix Karmeli | Working mode for two-stroke combustion engines and turbines |
| DE363855C (en) * | 1920-10-08 | 1922-11-14 | Hans Thormeyer | Compound internal combustion engine |
| FR629505A (en) * | 1926-02-22 | 1927-11-12 | Combustion engine | |
| DE546460C (en) * | 1930-02-11 | 1932-03-12 | Carl H Knudsen | Double-acting two-stroke internal combustion engine |
| FR910136A (en) * | 1945-04-05 | 1946-05-28 | Four stroke engine | |
| NL7807179A (en) * | 1978-07-03 | 1980-01-07 | Wilhelmus Johannes Van Hoeven | Opposed piston type IC engine - has two pistons in cylinder driving crankshafts at different speeds in set proportion |
| AU5006479A (en) * | 1978-11-24 | 1980-05-29 | Lang, T.N. | Internal combustion engine |
| US4289097A (en) * | 1979-11-13 | 1981-09-15 | Ward Charles P | Six-cycle engine |
-
1985
- 1985-04-02 AT AT99085A patent/AT397838B/en not_active IP Right Cessation
-
1986
- 1986-03-20 EP EP86890075A patent/EP0200714A3/en not_active Withdrawn
- 1986-04-01 CN CN198686102231A patent/CN86102231A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2005042944A1 (en) * | 2003-08-06 | 2005-05-12 | Shengli Zhang | Piston type internal-combustion engine with second expanding operation |
| CN100360773C (en) * | 2006-04-06 | 2008-01-09 | 郑哲立 | Superhigh boosting double-circulation variable discharge I.C. engine |
| CN100449127C (en) * | 2006-11-20 | 2009-01-07 | 张建元 | Divided cylinder type diesel engine |
| CN108625981A (en) * | 2018-05-03 | 2018-10-09 | 哈尔滨工程大学 | A kind of diesel engine with assistant cylinder |
Also Published As
| Publication number | Publication date |
|---|---|
| EP0200714A3 (en) | 1987-08-19 |
| ATA99085A (en) | 1993-11-15 |
| AT397838B (en) | 1994-07-25 |
| EP0200714A2 (en) | 1986-11-05 |
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| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| WD01 | Invention patent application deemed withdrawn after publication |