CN105020008A - Gas storage chamber device of internal combustion engine - Google Patents
Gas storage chamber device of internal combustion engine Download PDFInfo
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- CN105020008A CN105020008A CN201410184451.5A CN201410184451A CN105020008A CN 105020008 A CN105020008 A CN 105020008A CN 201410184451 A CN201410184451 A CN 201410184451A CN 105020008 A CN105020008 A CN 105020008A
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- 238000002485 combustion reaction Methods 0.000 title claims abstract description 64
- 239000007789 gas Substances 0.000 claims abstract description 57
- 238000010304 firing Methods 0.000 claims description 28
- 239000000203 mixture Substances 0.000 claims description 6
- 239000002184 metal Substances 0.000 claims description 4
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 claims description 4
- 238000002347 injection Methods 0.000 claims description 3
- 239000007924 injection Substances 0.000 claims description 3
- 239000003345 natural gas Substances 0.000 claims description 2
- 230000006835 compression Effects 0.000 abstract description 26
- 238000007906 compression Methods 0.000 abstract description 26
- 239000003502 gasoline Substances 0.000 abstract description 9
- 238000004880 explosion Methods 0.000 abstract description 3
- 230000003247 decreasing effect Effects 0.000 abstract 2
- 239000002737 fuel gas Substances 0.000 abstract 1
- 239000002699 waste material Substances 0.000 abstract 1
- 238000010586 diagram Methods 0.000 description 25
- 239000000567 combustion gas Substances 0.000 description 14
- 238000010438 heat treatment Methods 0.000 description 8
- 125000004122 cyclic group Chemical group 0.000 description 5
- 230000009977 dual effect Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 239000000446 fuel Substances 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 239000002360 explosive Substances 0.000 description 3
- 230000001473 noxious effect Effects 0.000 description 3
- 238000005381 potential energy Methods 0.000 description 3
- 238000005474 detonation Methods 0.000 description 2
- 230000005465 channeling Effects 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
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Abstract
A gas storage device of an internal combustion engine is installed on a cylinder cover or an engine body of the internal combustion engine and is composed of an additional piston, an additional air cylinder, a baffle ring, a thrust spring, a channel and the like. The lower end face of the additional piston and the wall of the additional air cylinder form a gas storage chamber. The channel and the combustion chamber are arranged below the gas storage chamber. When the internal combustion engine bursts out, the pressure of the combustion chamber reaches the value close to a threshold value of knocking or close to a threshold value of hazard emission. The additional piston gets away from the baffle ring to form the gas storage chamber with the certain volume. Some fuel gas temporarily enters the gas storage chamber, so that the maximum pressure and temperature inside the combustion chamber are controlled. The gas storage device is applied to a spark ignition type gasoline engine, and the compression ratio can be greatly improved, so that the thermal efficiency is improved. The gas storage device is applied to homogeneous charge compression ignition (HCCI) gasoline engine and a diesel engine, the power per liter can be improved, and conditions are created for reaching the practical level. When the gas storage device is applied to a (CIE) diesel engine, the maximum explosion pressure and temperature can be decreased, and therefore the weight of the engine body is decreased and the hazard waste emission is reduced.
Description
Technical field
The invention belongs to technical field of internal combustion engines, particularly the field of combustion technology of internal-combustion engine.
Background technique
A large amount of internal-combustion engine used has diesel engine and petrol engine now.The compression ratio of diesel engine is high, so very fuel-economizing, but firing chamber maximum outbreak pressure and temperature are all high, cause rough running, and noise is large, high to the requirement of strength of body, makes body heavy, NO in noxious emission
xmore.At present still based on spark-ignition type petrol engine in petrol engine, this petrol engine can reach very high rotating speed, so its power per liter is very high, light structure, but its thermal efficiency is lower, tracing it to its cause is that its compression ratio is too low, and to restrict the obstacle that its compression ratio improves be pinking.A kind of homogeneous-charge compression-ignition (HCCI) petrol engine and homogeneous-charge compression-ignition (HCCI) diesel engine are there is again in recent years, introduce them according to data to have many good qualities, as noxious emission is low, the thermal efficiency is high, but their power per liter is very low, only reach 1/2 to 3/4 of spark-ignition gasoline machine, and the factor restricting the raising of its power per liter is also pinking.
Summary of the invention
The technical problem solved is: for diesel engine, and reduce its maximum outbreak pressure and maximum temperature, make it work soft, noise reduction, body lightens, and also reduces NO simultaneously
xdischarge.For Spark ignition type petrol engine, eliminate or alleviate its phenomenon of detonation, improve its compression ratio, thus improve its thermal efficiency, reduce oil consumption.For homogeneous-charge compression-ignition (HCCI) petrol engine and diesel engine, its power per liter be improved, make it to reach practical level.
The technical solution adopted for the present invention to solve the technical problems is: on the cylinder cap or body of internal-combustion engine, install gas storage chamber device of the present invention.Gas storage chamber device is made up of additional piston, additional cylinder, baffle ring, thrust spring and passage etc.Wherein additional piston is contained in additional cylinder, cooperation between them is slidably matched, its matching gap is less, there is good gas tightness, baffle ring is positioned at the corresponding site of additional cylinder and additional piston, play one-way check and location, make additional piston can not skid off and stop at baffle ring downwards.Additional piston upward sliding is freely, does not have fixing terminating point.The upper-end surface of additional piston is withstood in the lower end of thrust spring, and cylinder cap or the body of additional cylinder or internal-combustion engine are withstood in upper end.But the suitable little thrust of the elasticity coefficient of thrust spring is sufficiently large, and it forces additional piston to have the trend of slide downward all the time, if the lower end surface of additional piston does not stress or suffered power is large not, additional piston rests against baffle ring.The space of the lower end surface of additional piston and additional cylinder wall composition is exactly gas storage chamber, and our settings its volume when additional piston stops at baffle ring is zero.Thrust spring or metal, or compressed-air actuated, also or metal+compressed-air actuated.Passage is located at below gas storage chamber, communicates with gas storage chamber and firing chamber, if do not consider the dynamics problem of gas and additional piston, can think that firing chamber, passage are the same with the gas pressure in gas storage chamber.The working principle of gas storage chamber device is as follows: when the piston of internal-combustion engine soon terminates compression stroke and arrives near top dead center, internal-combustion engine starts outburst, pressure in firing chamber raises rapidly, this pressure not only acts on the piston of internal-combustion engine, also through the lower end surface of channeling in additional piston, additional piston is made to have the power moved up, when this power is less than and equal the power of thrust spring, additional piston is motionless, and the volume of gas storage chamber equals zero.If the intensity of firing chamber outburst is quite large, when combustion gas has exceeded the thrust of thrust spring to additional piston to the pressure of additional piston, additional piston will leave baffle ring and move up, namely the volume of gas storage chamber is increased to certain respective value from 0, and a part of combustion gas in firing chamber will enter into gas storage chamber through passage, consequently the pressure of combustion gas is controlled, clearly, internal-combustion engine larger to oil mass, outburst intensity is higher, the volume of gas storage chamber is larger, and the combustion gas flow into from firing chamber gas storage chamber is more.When the piston of internal-combustion engine is crossed after top dead center enters expansion stroke, thrust spring promotes additional piston, combustion gas and internal combustion engine and moves down acting, and this process is until when additional piston stops at baffle ring.After this promote internal combustion engine from the combustion gas of discharging gas storage chamber together with the combustion gas in firing chamber and complete expansion work stroke.
Be not difficult to understand, in one section of crank angle when operating time of gas storage chamber device is only limited to internal-combustion engine outburst, the time in addition comprises air-breathing and exhaust stroke, and it does not participate in work.Its effect temporarily stores a part of combustion gas when internal-combustion engine breaks out, and the peak of the pressure and temperature in firing chamber is controlled.The parameters of choose reasonable gas storage chamber device, can make the pressure of firing chamber remain in required level, and peak has and significantly declines.Can bring following good effect like this: 1. for spark-ignited internal combustion engine, can reduce maximum explosive pressure, thus can alleviate or eliminate pinking, and compression ratio significantly can improve, thus the thermal efficiency is improved.2. for homogeneous-charge compression-ignition (HCCI) petrol engine and diesel engine, maximum explosive pressure and the rate of pressure rise can be reduced, thus can alleviate or eliminate phenomenon of detonation, make it to reach realistic scale create condition for improving its power per liter.3. for heterogeneous diffusive combustion as after diesel engine, Gasoline direct injection engine reduce its maximum explosive pressure and temperature, noise and vibration can reduce, noxious emission NO
xreduce.
Accompanying drawing explanation
Below we the present invention is further illustrated by reference to the accompanying drawings.
Fig. 1 is the schematic diagram of a specific embodiment of the present invention.
Fig. 2 is the schematic diagram more simplified of the present invention, and this schematic diagram is convenient to combine with the indicator diagram of internal-combustion engine and is further described in detail effect of the present invention.
Fig. 3, Fig. 4 and Fig. 5 are the indicator diagram having installed internal-combustion engine of the present invention.
Fig. 6 is the indicator diagram not installing spark-ignition type petrol engine of the present invention.
Fig. 7 is the indicator diagram after the present invention installed by petrol engine shown in Fig. 6.
Fig. 8 is the partial structurtes schematic diagram of the specific embodiment of the invention.
1. gas storage chamber device, 2. additional piston, 3. additional cylinder, 4. baffle rings in figure, 5. passage, 6. thrust spring, 7. gas storage chamber, 8. firing chamber, 9. internal-combustion engine, 10. internal combustion engine, 11. lower end surfaces, 12. upper-end surfaces, 13. additional cylinder walls, 14. end face seals, 15. spark plugs, 16. pressurized air, 17. cushion plugs, 18. cushion dashpots, 19. buffer cells.
Please see Figure 1.On the cylinder cap that gas storage chamber device (1) is arranged on internal-combustion engine (9) or body, additional piston (2) is in additional cylinder (3), baffle ring (4) is located at the corresponding site of additional piston and additional cylinder, additional cylinder is withstood in the upper end of thrust spring (6), the upper-end surface (12) of additional piston is withstood in lower end, the elasticity coefficient of thrust spring should little but thrust sufficiently large and its size can regulate, the lower end surface (11) of additional piston and additional cylinder wall (13) composition gas storage chamber (7), passage (5) is between gas storage chamber (7) and firing chamber (8).
Fig. 1 is the schematic diagram of the present invention for spark-ignition type petrol engine.The thermal efficiency ratio diesel engine of a large amount of spark-ignition gasoline machine used is low now, and its basic reason is that compression ratio is low, is generally 6 ~ 10, and diesel engine is then 16 ~ 22.If want the thermal efficiency improving petrol engine, then first to improve the compression ratio of petrol engine.We get compression ratio ε=10 ~ 17 in the present embodiment, are to improve more than 4 on the basis of original type, and fuel used or former type fuel used, the working medium of internal-combustion engine is perfect gas one air.
We analyze indicator diagram and its good effect of this example below, ask for an interview Fig. 3.
1. compression stroke.After internal-combustion engine (9) completes suction stroke, its piston (10) is in lower dead center A-A line, then adiabatic compression is carried out, move on to top dead center B-B line by lower dead center A-A line, correspond to by the curve of 1 o'clock to 2 o'clock in indicator diagram, the pressure and temperature of 1 is set to p
1, T
1, the pressure and temperature of 2 is set to p
2, T
2.The p of 1
1, T
1the same with present petrol engine, but the p of 2
2, T
2more much higher than present petrol engine, this is because compression ratio significantly improves.
2. middle or smallly add heat burn cycle.
Plug ignition when internal combustion engine (10) is near top dead center, in firing chamber, the temperature and pressure of combustion gas sharply rises, this pressure is except the piston (10) acting on internal-combustion engine, also act on additional piston (2), if pressure is less than and equals the power that thrust spring (6) gives additional piston (2), then additional piston is motionless, the running of internal-combustion engine just as not having gas storage chamber device, this in, Smaller load time be like this.The indicator diagram of its compression-combustion-expansion is as the 1-2-3-4 line of Fig. 3.In indicator diagram curve, 2-3 line is heating explosion line, and the maximum pressure of firing chamber and temperature are 3 corresponding pressure and temperatures.Because the outburst of mixed gas completes within the extremely short time, the piston of internal-combustion engine is almost not dynamic, and additional piston does not also move, the volume of firing chamber from 2 o'clock to 3 time never become, be volume V during compression terminal
c, so 2-3 line is perpendicular to abscissa and the straight line by top dead center, the height of 3 is decided by volume read-out, and volume read-out is more, and the heat that firing chamber obtains is more, and 3 higher.3 is the combustion gas expansion work stage later, until till when exhaust valve is opened, corresponding points are now 4.
The constant volume combustion circulation of Here it is viewed from the shape of indicator diagram general point combustion petrol engine.The thermal efficiency formula of this circulation is
η＝1-1/ε
k-1，
Wherein k is the adiabatic index of air, k=1.4, from thermal efficiency formula, the thermal efficiency of this constant volume combustion circulation is only relevant with compression ratio, and compression ratio ε at least improves 4 in this example, if ε=6 of former type, this example is ε=10, after calculating, the former type thermal efficiency is η=0.51, and this example is η=0.60, and the latter is than the former fuel-economizing more than 15%.
More than say be in, the situation of Smaller load, the heat that circulation each time adds to firing chamber is fewer, makes the pressure and temperature p of 3
3, T
3do not reach the boundary of pinking, if pressure p
xbe the boundary of pinking, if this example will be made pinking not to occur, then must satisfy condition
p
3≤p
X，
P
xvalue depend mainly on the antiknock quality of fuel and the height of compression ratio, determined by experiment again after can calculating according to the technical data of existing petrol engine.Present supposition we have found p
x, be p in indicator diagram
x-p
xline.Regulate the thrust of gas storage chamber spring, make the minimum cracking pressure p of additional piston
open≤ p
x, so, no matter we add how many heats to firing chamber, can p be ensured
3≤ p
x, thus can not pinking be there is.The indicator diagram of Fig. 3 depicts p
openline, its value is decided by the pressure of spring, once the pressure setting of spring, p
opennamely line is determined.
3. heat burn cycle greatly.
Please see Figure 4.After internal-combustion engine completes suction stroke, carry out compression stroke, piston (10) moves on to top dead center B-B line from lower dead center A-A line, the plug ignition when near top dead center, a part of heat Q
1make the pressure of firing chamber from p
2be elevated to p
3=p
open, temperature is from T
2be elevated to T
3, be 2-3 line in indicator diagram.After this remaining heat Q
2make the temperature of combustion gas continue to raise, and pressure promote additional piston (2) toward moving left acting, the volume of gas storage chamber is increased, after-heat Q
2more, the temperature of firing chamber is higher, and the volume of gas storage chamber is larger, pressure then with the thrust-balancing of spring.If heat Q
2make additional piston (2) move on to e-e line from d-d line, the volume of gas storage chamber is increased to V from 0
storage, the middle pressure p of combustion gas
on averagework W=p
on average.V
storage.If the elasticity coefficient of spring is very little of pressurized air spring, p can be got
on average=p
open, then W=p
open.V
storage, merit W has changed into the potential energy of spring.Now the volume of firing chamber is V=V
c+ V
storage, temperature is T
e, pressure is p
e=p
3=p
open.Said process completes within the extremely short time, so internal combustion engine (10) is still at B-B line, indicator diagram is 1-2-3 line, 2-3 line is straight line, and the pressure and temperature of corresponding 3 is p
3, T
3, the heat that adds of 2-3 line is Q
1.Note, there is straight line d-e line on the left side of axis of ordinates, is the indicator diagram of additional piston, and additional piston (2) corresponds to d point when d-d line, and correspond to e point when e-e line, pressure is p
open, the increment of volume is V
storage, the temperature of e point is Te, and the heat corresponding to d-e is Q
2, be indicated in above d-e.
Heat Q
2after being all added to firing chamber, additional piston (2) has moved on to e-e line, heat Q
2spring is made to have potential energy W=p
open.V
storage.And then internal combustion engine (10) leaves top dead center and enters expansion work stroke, and the potential energy of thrust spring (6) will discharge, and its promotes additional piston, the piston of combustion gas and internal-combustion engine moves to right, and the size of its power is also p
on average=p
open, the volume of firing chamber is V=V all the time
c+ V
storage, and temperature is T
e, till when the volume that this process will proceed to gas storage chamber is always 0.In figure below Fig. 5, additional piston (2) has got back to d-d line from e-e line, and internal combustion engine (10) has arrived C-C line, and piston (10) is from B-B line to the inswept volume V of C-C line
n=V
storage, in superincumbent indicator diagram, 3-4 line represents the p-v curve of internal combustion engine (10) from B-B line to C-C, wherein 4 corresponding with the C-C position of piston (10).When piston (10) is from B-B line to C-C line, except pressure is constant, temperature is also constant, temperature T
4=T
e.Piston (10) starts adiabatic expansion until lower dead center A-A line after crossing C-C, and indicator diagram is 4-5 curve.
As can be seen from indicator diagram, 2-3 section is constant volume heating, and d-e section is level pressure heating, so large heat Heating Cyclic is dual cycle.
Reached a conclusion by above analysis: existing spark-ignition gasoline machine is being installed after compression ratio significantly improves by the present invention, in, Smaller load time be constant volume Heating Cyclic, be dual cycle when large load.
Theory about internal-combustion engine is pointed out, when compression ratio is identical, the thermal efficiency of dual cycle does not have the thermal efficiency of constant volume Heating Cyclic high.Present spark-ignition gasoline machine is all constant volume Heating Cyclic under various operating mode, and to have installed spark-ignition gasoline machine of the present invention be dual cycle when large load, whether will the thermal efficiency of the latter lower than the former? answer is negative.
Now lift an example explanation.Please see Figure 6.The initial data of a type is had to be, ε=7.5, diameter 92 millimeters, stroke 92 millimeters, 4 cylinders, power W=62.5KW/3800 rev/min, fuel RON90 gasoline.The heat Q=1.01KJ that when single cylinder swept volume 0.611 liter calculates at full capacity, every cylinder adds at every turn, middle pressure p
on average=1.65MPa, if ambient temperature T
1=300K, ambient pressure p
1=0.1MPa, air makes working medium, adiabatic index k=1.4, and by constant volume Heating Cyclic, we draw the indicator diagram of its compression and expansion stroke as Fig. 6.The area recording curve 1-2-3-4-1 is 1867 units.The basis of this type is installed gas storage chamber device of the present invention, then makes compression ratio ε=12, all the other are all constant, and the indicator diagram drawing compression and expansion stroke is as Fig. 7, and the area recording curve 1-2-3-4-5-1 is 1984 units, and the latter is than the former fuel-economizing 6%.This is fully loaded situation, and load is less, and fuel-economizing is more, can reach at most as previously mentioned 16% and more than.
As can be seen here, when large load, although combustion manner is transformed to constant volume-neutral combustion by constant volume combustion, its thermal efficiency seems and will reduce, but due to compression ratio improve after the increasing degree of its thermal efficiency be higher than the former, so final result or the thermal efficiency improves.
From discussing above, install Spark ignition type uniform charge engine of the present invention as petrol engine, natural gas engine, the thrust of gas storage chamber spring should be large as far as possible, will be adjusted to till closing on knock limits always.
Homogeneous-charge compression-ignition (HCCI) petrol engine and diesel engine, their burning belongs to constant volume combustion, so their indicator diagram is also similar with Spark ignition type petrol engine, obviously, HCCI petrol engine and the HCCI diesel engine of gas storage chamber device have been installed, the thrust of its spring also should be adjusted to closes on knock limits, when middle or small throttle, the maximum pressure of firing chamber is in knock limits, belonging to constant volume combustion circulation, have the higher thermal efficiency, is constant volume-constant pressure mixing theory burning when large throttle, because the compression ratio of HCCI machine is high, so the thermal efficiency is not low yet.
For heterogeneous diffusive combustion as in-cylinder injection petrol engine and diesel engine, the adjustment principle of spring thrust ensures minimum pressure of explosion and temperature, limits the highest harmful pressure and temperature, pressure and temperature is remained within the scope of optimum value.Claim according to data, diesel engine maximum combustion temperature does not discharge NO substantially when about 1700K
x, and when higher than 2400K temperature, NO
xdischarge be multiplied, so we can according to circumstances be considered, the thrust of Regulation spring suitably reduces maximum pressure and temperature, and maximum pressure and temperature are controlled in the preferred range.
Finally we are explained Fig. 2, Fig. 8
1. the gas tightness of gas storage chamber is very important, if gas leakage will produce the pressure loss, for this reason except the radial seal between additional piston (2) and additional cylinder (3), also to increase end face seal (14), the same as the cooperation between valve head with valve seat, end face seal is zero clearance seal, and when gas storage chamber device does not work, end face seal effectively can prevent the leakage of combustion gas.
2. have certain speed when additional piston moves during operation from top to bottom, it can produce impact in a flash what take a seat, and this impact can destroy end face seal (14), increases buffer cell (19) for this reason.Buffer cell is made up of cushion plugs (17) and cushion dashpot (18), the diameter phi d of cushion plugs (17) is that cylinder coordinates with the diameter phi D of cushion dashpot (18), its gap width is less, has certain gas tightness.Its working principle is: when additional piston (2) is taken a seat; buffer cell (19) is formed between cushion plugs and cushion dashpot; the inner gas of buffer cell (19) has little time to extrude in a flash; an air cushion is formed to additional piston; greatly can reduce the impact force of additional piston to baffle ring, thus effectively protect end face seal.
Claims (5)
1. the gas storage chamber device of an internal-combustion engine, it is characterized in that: on the cylinder cap being arranged on internal-combustion engine or body, by additional piston, additional cylinder, baffle ring, the composition such as thrust spring and passage, wherein additional piston is arranged in additional cylinder, be slidably matched between them, there is gas tightness, baffle ring is arranged on the corresponding site of additional piston and additional cylinder, baffle ring is stopped at when additional piston moves down, the upper-end surface of additional piston is withstood in one end of thrust spring, the other end withstands additional cylinder or internal combustion (IC) engine airframe, the lower end surface of additional piston and additional cylinder wall composition gas storage chamber, gas storage chamber communicates with the firing chamber of internal-combustion engine by passage, thrust spring or by metal, or by pressurized air, or be made up of metal+pressurized air.
2. according to the gas storage chamber device of the said a kind of internal-combustion engine of claim 1, it is characterized in that: thrust spring gives the power of additional piston, petrol engine is comprised for spark-ignition type (SIE) internal-combustion engine, the threshold pressure closing on pinking that natural gas engine equals firing chamber gives the power of additional piston, petrol engine is comprised for homogeneous-charge compression-ignition (HCCI) internal-combustion engine, the threshold pressure closing on pinking that diesel engine equals firing chamber gives the power of additional piston, diesel engine is comprised for heterogeneous body charge compression-ignition (CIE) internal-combustion engine, in-cylinder injection petrol engine, the optimum value pressure equaling firing chamber gives the power of additional piston.
3., according to the gas storage chamber device of the said a kind of internal-combustion engine of claim 1,2, it is characterized in that: the baffle ring of additional piston and additional cylinder has end face seal.
4. according to the gas storage chamber device of the said a kind of internal-combustion engine of claim 1,2, it is characterized in that: on additional piston, have cushion plugs, additional cylinder has cushion dashpot, cushion plugs and cushion dashpot composition buffer cell.
5. according to the gas storage chamber device of the said a kind of internal-combustion engine of claim 1,2,3, it is characterized in that: on additional piston, have cushion plugs, additional cylinder has cushion dashpot, cushion plugs and cushion dashpot composition buffer cell.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410184451.5A CN105020008A (en) | 2014-04-26 | 2014-04-26 | Gas storage chamber device of internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410184451.5A CN105020008A (en) | 2014-04-26 | 2014-04-26 | Gas storage chamber device of internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105020008A true CN105020008A (en) | 2015-11-04 |
Family
ID=54410244
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410184451.5A Pending CN105020008A (en) | 2014-04-26 | 2014-04-26 | Gas storage chamber device of internal combustion engine |
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| Country | Link |
|---|---|
| CN (1) | CN105020008A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106840684A (en) * | 2017-01-13 | 2017-06-13 | 西华大学 | A kind of constant volume constant pressure mixing theory Constant Volume Bomb and its control method |
| WO2025081311A1 (en) * | 2023-10-16 | 2025-04-24 | 谢国华 | Device for prolonging initial combustion time of internal combustion engine |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3204616A1 (en) * | 1982-02-10 | 1983-08-18 | Winkle, Erwin, 7151 Allmersbach | Combustion engine |
| GB2304151A (en) * | 1995-07-25 | 1997-03-12 | Guy Stewart Morton | Automotive i.c. engine with supplementary piston-and-cylinder energy accumulator |
| US5769042A (en) * | 1995-04-26 | 1998-06-23 | Popadiuc; Ovidiu Petru | Method of operating an internal combustion engine during a combustion process |
| CN1188845A (en) * | 1997-01-21 | 1998-07-29 | 株式会社五十铃硅酸盐研究所 | Combustion chamber structure of engine |
| JP2000230439A (en) * | 1999-02-09 | 2000-08-22 | Tokyo Gas Co Ltd | Premixed compression ignition engine and operation method thereof |
| CN103104339A (en) * | 2013-01-27 | 2013-05-15 | 浙江大学 | Diesel engine combustion device capable of changing clearance volume |
-
2014
- 2014-04-26 CN CN201410184451.5A patent/CN105020008A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3204616A1 (en) * | 1982-02-10 | 1983-08-18 | Winkle, Erwin, 7151 Allmersbach | Combustion engine |
| US5769042A (en) * | 1995-04-26 | 1998-06-23 | Popadiuc; Ovidiu Petru | Method of operating an internal combustion engine during a combustion process |
| GB2304151A (en) * | 1995-07-25 | 1997-03-12 | Guy Stewart Morton | Automotive i.c. engine with supplementary piston-and-cylinder energy accumulator |
| CN1188845A (en) * | 1997-01-21 | 1998-07-29 | 株式会社五十铃硅酸盐研究所 | Combustion chamber structure of engine |
| JP2000230439A (en) * | 1999-02-09 | 2000-08-22 | Tokyo Gas Co Ltd | Premixed compression ignition engine and operation method thereof |
| CN103104339A (en) * | 2013-01-27 | 2013-05-15 | 浙江大学 | Diesel engine combustion device capable of changing clearance volume |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106840684A (en) * | 2017-01-13 | 2017-06-13 | 西华大学 | A kind of constant volume constant pressure mixing theory Constant Volume Bomb and its control method |
| CN106840684B (en) * | 2017-01-13 | 2023-06-06 | 西华大学 | A constant volume-constant pressure mixed combustion simulation experimental device and its control method |
| WO2025081311A1 (en) * | 2023-10-16 | 2025-04-24 | 谢国华 | Device for prolonging initial combustion time of internal combustion engine |
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Application publication date: 20151104 |