CN1388307A - Engine with less exhaust - Google Patents
Engine with less exhaust Download PDFInfo
- Publication number
- CN1388307A CN1388307A CN 02114670 CN02114670A CN1388307A CN 1388307 A CN1388307 A CN 1388307A CN 02114670 CN02114670 CN 02114670 CN 02114670 A CN02114670 A CN 02114670A CN 1388307 A CN1388307 A CN 1388307A
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- Prior art keywords
- engine
- gear
- camshaft
- cam
- crankshaft
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- 230000006835 compression Effects 0.000 claims abstract description 15
- 238000007906 compression Methods 0.000 claims abstract description 15
- 239000000446 fuel Substances 0.000 abstract description 10
- 230000001105 regulatory effect Effects 0.000 abstract description 4
- 230000002349 favourable effect Effects 0.000 abstract 1
- 239000007789 gas Substances 0.000 abstract 1
- 239000002912 waste gas Substances 0.000 abstract 1
- 238000002485 combustion reaction Methods 0.000 description 6
- 239000007787 solid Substances 0.000 description 6
- 230000002000 scavenging effect Effects 0.000 description 5
- 230000000694 effects Effects 0.000 description 2
- 238000010304 firing Methods 0.000 description 2
- 230000007613 environmental effect Effects 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
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Abstract
The small-exhaust engine includes cylinder assembly, piston assembly, crankshaft-link lever mechanism and gas distribution phase unit. It has designed working exhaust less than whole piston stroke volume. When the air intake phase changes, the practical air intake amount will change accordingly. Using partial volume of whole piston stroke as the designed working exhaust is favorable to the complete burning of fuel and the decrease of waste gas pollution. Air intake phase may be regulated to compensate the air intake amount and regulate the compression ratio.
Description
Technical field
The present invention relates to a kind of engine with less exhaust, belong to a kind of new working form of Reciprocating engine.
Background technique
Reciprocating engine of the prior art generally all is to utilize piston total travel volume as the design work discharge capacity, and promptly set solid amount working form is unfavorable for the abundant burning of fuel and reduces exhaust emission pollution.In addition, in case the Reciprocating engine design typification of set solid amount working form, its air inflow and compression ratio generally all are difficult to regulate, unless adopt complicated air inlet boosting device to compensate air inflow.
Summary of the invention
The technical problem that the present invention solves: design a kind of engine with less exhaust, the a part of volume that utilizes piston total travel volume is as the design work discharge capacity, help the abundant burning of fuel and reduce exhaust emission pollution, also can be by regulating the air inlet termination phase, with compensation air inflow and adjusting compression ratio.
Technical solution of the present invention:
1, design philosophy: in order to improve the service behaviour of Reciprocating engine; to adapt to more and more stricter environmental protection emission standard; and lay in some corresponding function that can further utilize-air inlet compensation and compression ratio adjustment etc., a kind of Reciprocating engine of few discharge capacity working form is invented in research.
2, design proposal: a kind of engine with less exhaust, comprise cylinder assembly (1), piston assembly (2), crankshaft ﹠ connecting (3) and port timing device (4), its invention main points are: design work discharge capacity V
1' less than piston total travel volume V
1And when the air inlet termination phase changed, actual air inflow and work compression ratio were understood corresponding increase or are reduced.
V
1-corresponding to the volume of cylinder of S stroke, V
1'-corresponding to the cylinder aspirated volume of S ' stroke,
Work compression ratio ε
g=(v
1+ v
2)/v
2Definition compression ratio ε
d=(v
1'+v
2)/v
2K=s '/s (k＜1)
ε
d＝(ε
g-1)/k+1 ε
g＝k(ε
d-1)+1 ε
g＜ε
d
ε
gOptimum value can select to determine according to fuel used and firing mode.The k value is a controlled variable, when the k value, will have initiatively to cover tolerance function and raising ε during initial value greater than design
gFunction; When the k value during initial value, can make ε less than design
gReduce, only be applicable to that generally fuel band changes after, the situation when its capability of antidetonance is lower than the design initial value.
Port timing device (4) by be installed in crankshaft timing gear (5) on the bent axle, be installed in the middle follower gear (6) on the cylinder body, camshaft timing gear (7) and the cam (8) that is installed on the camshaft formed, crankshaft timing gear (5) is meshed with middle follower gear (6), middle follower gear (6) is meshed with camshaft timing gear (7), cam (8) withstands on the tappet (9), one end of push rod (10) and tappet (9) are hinged, one end of the other end and valve rocker (11) is hinged, and the other end of valve rocker (11) touches mutually with valve stem (12).The ratio of the number of teeth of the protruding timing camshaft timing gear of the number of teeth of crankshaft timing gear (5) and cam (7) is 1: 2.The phase angle that distribution opens and closes is by the lift angle decision of the outer profile curve of the cam on the camshaft (8).
Advantage that the present invention has and effect:
1, compares with the set solid amount working form of equal piston stroke, begin under the same situation of phase place in exhaust, the relative combustion stroke of few discharge capacity standard and time increase, and help the abundant burning of fuel and reduce exhaust emission pollution, and exhaust initial pressure and associated exhaust sound reduction.
2, can be according to rotating speed and temperature conditions or the altitude and the air pressure conditions of motor, by regulating the air inlet termination phase, i.e. k value is with compensation air inflow and adjusting compression ratio.
But 3 based on fuel combustion performance and knock resistances, by regulating the air inlet termination phase, promptly the k value with compensation air inflow and adjusting compression ratio, is conveniently used pluralities of fuel.
Description of drawings
Fig. 1 is a piston stroke schematic representation of the present invention,
S-is the stroke distances of piston between last lower dead center,
The O-top dead center, O '-lower dead center,
S '-go downwards to the stroke distances that A is ordered from top dead center for piston,
A-air inlet terminal point, B-exhaust terminal point,
V
2-combustion chamber volume,
Fig. 2 is the structural representation of an embodiment of the present invention.
Embodiment
1,2 a kind of embodiment of the present invention is described in conjunction with the accompanying drawings: adopt the fixedly engine with less exhaust of port timing device.
1, engine type: four-journey single cylinder diesel.
2, technical parameter:
Work compression ratio ε
g=17.0: 1, definition compression ratio ε
d=23.9: 1, k value=0.7 of s '/s.
3, fixing port timing device: form by crankshaft timing gear, middle follower gear, camshaft timing gear and cam.The number of teeth of crankshaft timing gear is 1: 2 with the ratio of the number of teeth of the protruding timing camshaft timing gear of cam.
Drive connection: drive middle follower gear by crankshaft timing gear, drive camshaft timing gear by middle follower gear again, thereby make the camshaft rotation, drive cam and determine port timing by tappet, push rod, valve rocker, valve stem.The phase angle that distribution opens and closes is by the lift angle decision of the cam outer profile curve of camshaft.
Air inlet: opening point, 20 ° of top dead center precontracts are closed close point, cross about 110 ° of atdc.
Exhaust: opening point, 65 ° of lower dead center precontracts are closed close point, cross about 20 ° of atdc.
4, work cycle: piston is moved to top dead center by lower dead center, and when arriving 20 ° of top dead center precontracts, intake cam begins to back down intake valve, and exhaust valve does not also cut out in this moment cylinder, is in scavenging period; Cross about 20 ° of atdc at piston, exhaust valve cuts out fully, and scavenging finishes, and cylinder is in intake stroke; When piston continues descendingly, when arriving the position of s '/s=k=0.7, when that is to say the about 110 ° position of atdc, intake valve is closed fully, sucks the v corresponding to s ' stroke this moment in the cylinder
1The air of ' volume.
Piston continues to the lower dead center motion, because intake valve is closed, inhaled air begins negative pressure expansion disturbance.When arriving lower dead center, negative pressure expands and finishes.
Piston to the top dead center motion, begins compression stroke after after bottom dead center.When a certain corner of piston arrives budc, oil nozzle commencement of fuel injection igniting (suitable premature ignition).
Work compression ratio ε during the piston arrives top dead center
gThough less than definition compression ratio ε
d, but the selection of its numerical value setting is just the same with the set solid amount working form of equal operating mode, so the thermal efficiency can not reduce.
Piston is crossed atdc, under the promotion of firing pressure, and the beginning working stroke.When 65 ° of piston arrives lower dead center precontracts, exhaust valve is opened in advance, begins exhaust under the residual pressure after gaseous combustion finishes.
Because few discharge capacity working form is compared with the set solid amount working form of equal conditions, its piston stroke equates that therefore relative work by combustion stroke and time increase, and helps full combustion of fuel and reduces exhaust emission pollution.
Piston is after after bottom dead center, to the top dead center motion, continues exhaust, when piston when arriving 20 ° of top dead center precontracts, intake valve is opened ahead of time, exhaust this moment is also being carried out, exhaust valve, intake valve are all opened, and are in scavenging period; When piston was crossed about 20 ° of atdc, exhaust valve cut out fully, and scavenging finishes, and enters next circuit intake stroke.
Because the set solid amount working form of few discharge capacity working form and equal conditions all adopts same optimization exhaust phase place and scavenging phase place, so exhaust initial pressure and associated exhaust sound reduction, but scavenge effect keeps the same.
Claims (5)
1, a kind of engine with less exhaust comprises cylinder assembly (1), piston assembly (2), crankshaft ﹠ connecting (3) and port timing device (4), it is characterized in that: design work discharge capacity V
1' less than piston total travel volume V
1
2, engine with less exhaust according to claim 1 is characterized in that: when the air inlet termination phase changed, actual air inflow and work compression ratio were understood corresponding increase or are reduced.
3, according to claim 1 and 2 described engine with less exhaust, it is characterized in that: port timing device (4) is by the crankshaft timing gear (5) that is installed on the bent axle, be installed in the middle follower gear (6) on the cylinder body, the camshaft timing gear (7) and the cam (8) that are installed on the camshaft are formed, crankshaft timing gear (5) is meshed with middle follower gear (6), middle follower gear (6) is meshed with camshaft timing gear (7), cam (8) withstands on the tappet (9), one end of push rod (10) and tappet (9) are hinged, one end of the other end and valve rocker (11) is hinged, and the other end of valve rocker (11) touches mutually with valve stem (12).
4, engine with less exhaust according to claim 3 is characterized in that: the ratio of the number of teeth of the protruding timing camshaft timing gear of the number of teeth of crankshaft timing gear (5) and cam (7) is 1: 2.
5, engine with less exhaust according to claim 3 is characterized in that: the phase angle that distribution opens and closes is by the lift angle decision of the outer profile curve of the cam on the camshaft (8).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 02114670 CN1268835C (en) | 2002-07-03 | 2002-07-03 | Engine with less exhaust |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 02114670 CN1268835C (en) | 2002-07-03 | 2002-07-03 | Engine with less exhaust |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1388307A true CN1388307A (en) | 2003-01-01 |
| CN1268835C CN1268835C (en) | 2006-08-09 |
Family
ID=4743231
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 02114670 Expired - Fee Related CN1268835C (en) | 2002-07-03 | 2002-07-03 | Engine with less exhaust |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1268835C (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2005116417A1 (en) | 2004-05-26 | 2005-12-08 | Zengli Yang | An internal combustion engine with super expansion |
-
2002
- 2002-07-03 CN CN 02114670 patent/CN1268835C/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2005116417A1 (en) | 2004-05-26 | 2005-12-08 | Zengli Yang | An internal combustion engine with super expansion |
| US7438025B2 (en) | 2004-05-26 | 2008-10-21 | Zengli Yang | Ultra-expansion four-stroke internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1268835C (en) | 2006-08-09 |
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| PB01 | Publication | ||
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| SE01 | Entry into force of request for substantive examination | ||
| 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 |