CN1298472A - High power density diesel engine - Google Patents
High power density diesel engine Download PDFInfo
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- CN1298472A CN1298472A CN99805504A CN99805504A CN1298472A CN 1298472 A CN1298472 A CN 1298472A CN 99805504 A CN99805504 A CN 99805504A CN 99805504 A CN99805504 A CN 99805504A CN 1298472 A CN1298472 A CN 1298472A
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- 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
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
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- 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
- F02B19/00—Engines characterised by precombustion chambers
- F02B19/02—Engines characterised by precombustion chambers the chamber being periodically isolated from its cylinder
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G3/00—Combustion-product positive-displacement engine plants
- F02G3/02—Combustion-product positive-displacement engine plants with reciprocating-piston engines
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- 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
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
- Supercharger (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
An engine (10) having an engine block (12) with a compression cylinder (22) and an expansion cylinder (24) defined therein. A compression piston (34) is located in the compression cylinder (22) and an expansion piston (36) is located in the expansion cylinder (24). Each piston is connected to a crankschaft (26, 28). A rotary prechamber tube (44), having two, constant volume, combustion chambers (48) defined therein, is positioned within a housing (14) coupled to the engine block (12). Induction and expansion ports respectively forming passageways communicating the compression cylinder (22) and the expansion cylinder (24) with the chambers (48) of the tube (44). The tube (44) itself is rotatably supported in the housing (14) and oriented with its axis (46) being generally transverse to cylinder axes. The engine (10) is operated such that the chambers (48) are successively brought into communication via the induction port with the compression cylinder (22), separated from communication with said compression cylinder (22), brought into a position to receive fuel from said fuel injector (62) and to initiate combustion, and then brought into communication via the expansion port with the expansion cylinder (24) to complete combustion.
Description
The present invention relates generally to motor, relate in particular to the diesel engine and the work cycle thereof of high power density.
Now developed multiple different engine design, the design of motor is a kind of mature technique.Two kinds of the most frequently used gas circulation that are used for maneuvering engine are diesel cycle that Otto cycle and diesel engine adopted that internal-combustion engine adopts.
Spark-ignition internal combustion engine SI motor in other words uses light volatile fuel, i.e. gasoline, and utilize spark in its cylinder, to cause burning.Compression member in the circulation and dilation all carry out in same cylinder.High power density (term herein " high power density " be meant horsepower and the ratio of weight or horsepower with cubic inch ratio be at least 1.0) the evolution of SI motor in, run into two subject matters, i.e. the volatilization of fuel consumption and gasoline.The volatilization of gasoline has had a lot of documents to prove, with store, transportation and use relevant problem too much not discuss in this article at a distance.Consider Economy and durability, aspect the fuel economy of SI motor and the durability important breakthrough is being arranged in recent years, but these motors also lack the performance of its diesel engine homologue.
Different with the SI motor, the diesel oil compression ignition engine, the CI motor causes burning by producing high pressure and arrive autoignition temperature in cylinder in other words.When temperature and pressure was enough high, fuel was lighted automatically and is not needed spark.Although fuel economy and diesel oil than low volatility on be better than the SI motor, the power density ratio SI motor of CI motor is low.In the past the effort that increases specific power, reduces the diesel engine size was subjected to the puzzlement of following problem, that is: the problem of bulky two stroke pressurized machines, limited pressures cycle, the structure durability that causes owing to excessive machinery and thermal load and the fuel consumption of extreme difference.
Consider the above-mentioned of various prior art motors and other restriction, as can be seen, need a kind of diesel engine of high power density.Therefore, an object of the present invention is to provide a kind of like this motor.The present invention also has a purpose to provide a kind of new gas circulation that is used to make this engine operation.
In order to realize above-mentioned and other purpose, the invention provides a kind of diesel engine design scheme with potentiality of attractive high power density, also keep desirable fuel economy simultaneously.The prerequisite of the basic principle of this motor self is: by the expansion ratio of the working fluid in the reduction reciprocator, and utilize reclaiming system withdrawal exhaust energy and supercharging is provided, can increase mean effective pressure.But, they are different with common diesel engine, common diesel engine automatic igniter pressure when starting is not enough, need very heavy parts and delayed injection technology to control peak combustion pressure, and design proposal of the present invention is separated compression process with inflation process, thereby independently compression ratio and expansion ratio can be arranged, and (port-controlled) expansion of port controlling is combined with constant volume combustion.This makes the present invention be better than existing motor and gas circulation, and carries out work under lower swelling pressure peak value, is similar to petrol engine.
Gas circulation of the present invention is carried out in three chambers that are mutually related simultaneously, i.e. compression cylinder, firing chamber and expansion cylinder.During starting, compression cylinder is introduced fresh air by bottom air inlet, and this is similar to common two-stroke diesel engine.Subsequently, the material in the compression cylinder by compression piston upwards or compression stroke be compressed, and pass through suction port and import in the firing chamber.A little after a while, with the pressurized contents that be included in wherein suddenly with compression cylinder separate behind the upper dead center (TDC) by the firing chamber for compression piston.Because head room is very little, therefore in compression cylinder, only stay minimum volume.Then, compression piston moves downward and carries out its expansion stroke, and the pressure in the compression cylinder reduces earlier fast, slowly reduces then until near vacuum.When compression piston continued its downward stroke, bottom air inlet was opened, and live gas pours in and is full of this zone near vacuum.Carry out next time upwards or in the process of compression stroke, soon, compression piston begins to compress second material behind the semi-closure suction port at compression piston.Arrive upper dead center (BTDC) before, second firing chamber is communicated with second pressurized contents, and up to having crossed TDC a little, at this moment this second pressing chamber also separates with compression cylinder suddenly.Then, compression piston begins its downward stroke, and repeats its circulation.
After separating or separate with compression cylinder, fuel is injected the firing chamber that includes pressurized contents.Self can have glowing plug this firing chamber, and initial fuel is to be directly injected to hot-wire ignition beyond the Great Wall, to light compressor.Fuel sprays when proceeding, and glowing plug is removed from the position that fuel sprays, and causes fuel to spray and breaks through the firing chamber, distributes thereby produce good fuel in the firing chamber.In this moment of circuit, in the firing chamber, fully carry out constant volume combustion.
The firing chamber that includes partially combusted injection fuel is communicated with expansion cylinder again.Before opened facing to expansion cylinder the firing chamber, expansion piston began its compression stroke, and covered relief opening and scavenging (scavenging) mouth in the movement process that it makes progress.When expansion piston when the TDC, the scavenging material in the cylinder and the mixture of residual substance are compressed.At this moment, the material of the partial combustion in the combustion cylinders is introduced in the interior pressurized contents of expansion cylinder.Because the high pressure combustion mixture enters from the firing chamber, so the pressure in the expansion cylinder raises.Then, when burning being continued owing to the new oxygen of introducing, the material that the expansion cylinder compression is mixed.
In the expansion stroke of expansion piston, expansion piston passes through combustion process and output work.When expansion piston carried out downward stroke, this piston led to relief opening, and residue is discharged.When expansion piston continued its downward stroke, expansion piston led to scavenging port, and the ozone scavenging is carried out in expansion cylinder.After having crossed lower dead centre (BDC), expansion piston is closed scavenging port and relief opening, begins to compress its interior scavenging material and the mixture of residue, and prepares to mix with the combustible substance in second firing chamber.After mixing and further compression and burning, this expansion piston begins its downward stroke again, and the while is output work once more.Expansion piston repeats its circulation then.
After expansion cylinder is discharged, the firing chamber separates with expansion cylinder suddenly, and opens opening to clear away the afterflaming product in the firing chamber.After the scavenging, the firing chamber is closed, and the circulation of preparing to lead to compression cylinder and repeating the firing chamber.
By following description of a preferred embodiment and additional claims, and in conjunction with the accompanying drawings, those skilled in the art can understand other advantage of the present invention and benefit.
Brief description
Figure 1 shows that the schematic representation of the motor that embodies the principle of the invention;
Fig. 2 is the schematic representation of motor shown in Figure 1, has also shown critical piece of the present invention and their contacts each other, and the compression piston shown in it is near BDC;
Fig. 3 a and 3b are the schematic representation that is similar to Fig. 2, and wherein compression piston is at TDC, and defined some design parameter of the present invention;
Fig. 4 a, 4b and 4c have schematically illustrated the different stream conditions of gas circulation of the present invention;
Fig. 5 a and 5b are the schematic representation that is similar to Fig. 1, its represent respectively suction port among the present invention close with air vent open and fuel enters in the firing chamber;
Fig. 6 a is the schematic representation of the piston position of the expression geometrical compression ratio that is used for determining compressor;
Fig. 6 b is the schematic representation of the compressor piston position of the expression geometrical compression ratio that is used to determine to comprise compression cylinder and firing chamber;
Fig. 6 c is the schematic representation of the expansion piston position of the expression geometrical compression ratio that is used for determining expansion cylinder;
Fig. 6 d is the schematic representation of the piston position of the expression geometrical compression ratio that is used for determining expansion cylinder and firing chamber;
Fig. 7 is the perspective view that is used for rotation precombustion chamber pipe of the present invention, has also represented to be formed at one of them firing chamber;
Fig. 8 is the sectional view of pipe shown in Figure 7, has also shown coolant channel that passes this pipe and the removable insert that is used for determining firing chamber self;
Fig. 9 is a perfect gas circuit plotted curve of the present invention;
Figure 10 and 11 is schematic representation of another embodiment of the present invention;
Figure 12 a, 12b, 13a and 13b have schematically illustrated and can be used for timing of the present invention (timing) mechanism.
With reference to the accompanying drawings, Fig. 1 schematically shows the motor that embodies the principle of the invention, and it is totally with label 10 expressions.This motor mainly comprises base unit or engine cylinder 12, top unit or housing 14, is contained in timing belt, exhaust manifold 18 (this exhaust manifold can change with the cylinder number in the motor 10) and the scavenging air trunk 20 who links to each other with housing 14 as shown in the figure below the lid 16 as shown in the figure.Before the internal work situation that motor 10 is discussed, earlier perfect gas circulation shown in Figure 9 is described.
As shown in Figure 9, perfect gas circulation is actual to comprise two circulations that connect each other, and one is used for compression cylinder or compressor, and one is used for expansion cylinder or decompressor.Introduce the compression cylinder circulation below earlier.Obviously, said volume is that in fact it depend on the concrete performance of motor 10 for illustrative purposes in desirable circuit explanation.
In the stroke bottom, as shown in the figure, the volume (VBDC) that is in the compression cylinder of lower dead centre or BDC is just greater than eight cubic inches.When compression cylinder was led in the firing chamber, combined volume was increased to about 9 cubic inches.Then, compression piston makes progress or compression stroke, and quality or volume to air in the combined volume of compression cylinder and firing chamber compress, up to pressure greater than 35 barometric pressure and volume less than two cubic inches.When compression piston is in TDC, the unexpected and compression cylinder disconnection in firing chamber.Therefore, the volume of compression cylinder is reduced to and is lower than one cubic inch.Compression piston begins downwards or expansion stroke again, and as can be seen, the pressure in the compression cylinder descends earlier fast, and is more and more slower then, up at the BDC place near vacuum.This circulation repeats self again.
In the Ideal Cycle of expansion cylinder, when expansion piston was in BDC, the volume of expansion cylinder was just less than 13 cubic inches.When expansion cylinder began its compression stroke, at first, volume reduced fast, and pressure slowly increases.When expansion piston during near TDC, the pressure increase is more and more faster, reaches about 47 atmospheric peak values up to about 2 cubic inches of volume the time.At this moment, expansion cylinder is led in the firing chamber, all corresponding increase of volume and pressure, and this is owing to carried out waiting the appearance heating in the firing chamber before exhaust port is opened facing to expansion cylinder.In the initial period of leaving TDC, the firing chamber of combination and the volume of expansion cylinder increase, and the maintenance of the pressure in it is constant.This is because isobaric heating.When volume was approximately 4 cubic inches, expansion piston continued downward stroke and causes pressure to reduce to increase with volume.In expansion stroke, output work.When expansion piston arrived BDC, volume was just less than 14 cubic inches, the firing chamber suddenly with the expansion cylinder disconnection, the volume of expansion cylinder reduces.When pressure near barometric pressure and volume during just less than 13 cubic inches, this expansion cylinder repeats its circulation.
With reference to figure 2, schematically show the internal work situation of motor 10 among the figure again.At least, this motor 10 comprises two cylinders, i.e. a compression cylinder 22 and an expansion cylinder 24.Bent axle 26 links to each other with expansion piston 36 with compression piston 34 with 32 by connecting rod 30 respectively with 28.Usually at place, bottom suction port 38 and 40 are arranged towards each cylinder 22 and 24.When piston 34 and 36 when the BDC, this suction port exposes or opens, and makes fresh air enter in the compression cylinder 22, and the dual product (bi-product) that will burn and residual substance are cleared away from expansion cylinder 24.In order more to help the scavenging of expansion cylinder 24, expansion cylinder 24 also has relief opening 42.This relief opening 42 can be arranged in suction port 40 and open before opening.
Usually there is rotation precombustion chamber pipe 44 center between two tops of compression cylinder 22 and expansion cylinder 24.Should manage 44 and rotatably install and be supported in the housing 14, so that tubular axis 46 rotations (in Fig. 2, extending in the page substantially) of extending around vertically passing pipe 44.As shown in Figure 7, pipe 44 is cylindrical substantially, also defines two precombustion chambers or firing chamber 48 in its body.
Also define the passage 54 at the center of passing pipe 44 basically.Coolant fluid such as oil is by 54 circulations of this passage, thus cooling combustion chamber 48 not only, also to pipe 44 self and can have one or more axially and the Sealings of radial groove 56 provide lubricated.Lubricant oil can provide by the unshowned centrifugal pipeline of managing in 44.
When pipe 44 rotations, firing chamber 48 alternately is communicated with compression cylinder 22 and expansion cylinder 24.Be communicated with by suction port 58 with compression cylinder 22 and undertaken, carry out and be communicated with by air vent 60 with expansion cylinder 24.
When firing chamber 48 rotated between compression cylinder 22 and expansion cylinder 24, fuel injected the firing chamber from fueling charger 62.
In addition, in housing 14 and engine cylinder 12, be limited with coolant channel 64.This passage 64 makes freezing mixture such as water and ethylene glycol mixture circulate, thereby cools off whole motor 10.
Again with reference to figure 3b, show among the figure and defined some correlations between the different parts of the present invention.Be defined as the angle between the central shaft of the central shaft of compression cylinder 22 and expansion cylinder 24 by the tilt angle of arrow 66 expression.Preferably, the scope at the tilt angle 66 between compression cylinder 22 and the expansion cylinder 24 is to spend to 90 degree from 60.This scope makes two cylinders 22 and 24 to manage 44 with one.The opening angle is by 68 expressions, and be defined as from tubular axis 46 draw and line by suction port 58 centers with draw from tubular axis 46 and pass through angle between the line at air vent 60 centers.Preferably, the scope of this opening angle 68 is to spend to 95 degree, so that high speed operation from 85.Such opening angle makes and injects when fuel is closed between two cylinders 22 and 24 in firing chamber 48, and caused burning before opening is opened facing to expansion cylinder 24 in firing chamber 48.Be defined as when the tdc position expansion piston 36 with respect to compression piston 34 and leading angle by the phase angle of label 70 expression.Preferably, these phase angle 70 scopes are spent to 65 degree 55, thereby can change the compression ratio of expansion cylinder.Shown in Fig. 3 b, with the bowl angle of label 72 expression be defined as the line of drawing from tubular axis 46 and firing chamber 48 leading edges 74 and the line of drawing from tubular axis 46 and firing chamber 48 trailing edges 76 between angle.Preferably, the scope of this bowl angle is to spend to 65 degree from 45, similar with opening angle 68, inject when this bowl angle also can make fuel close between cylinder 22 and 24 in firing chamber 48, and before opening is opened facing to expansion cylinder 24 in firing chamber 48, cause burning.
In the working procedure of motor 10, about 120 ° the time, compression piston 34 is fully return, thereby opens suction port 38 behind TDC, makes that the fresh air with arrow 78 expressions enters compression cylinder 22.At this moment, as can be seen, the firing chamber 48 of scavenging also is not communicated with compression cylinder 22.
Before TDC about 120 ° the time, compression piston 34 enough distances that moves up, thus close suction port, open with respect to compression cylinder 22 by suction port 58 firing chamber 48.When compression piston 34 continued its stroke that makes progress, shown in Fig. 4 b, the quality/volume in the compression cylinder 22 was compressed, and enters firing chamber 48 by suction port 58, shown in arrow 80.When compression piston 34 arrives TDC, the head room minimum in the compression cylinder 22.Again a little after a while, firing chamber 48 separates with compression cylinder suddenly, shown in Fig. 5 a.Then, compression piston 34 beginning its downward stroke or expansion strokes shown in Fig. 4 c, cause the volume of compression cylinder to increase, and pressure reduces (near vacuum).At this moment, compression piston is fully return, thereby opens suction port 38, once more shown in Fig. 4 a.At this moment, this compression piston 34 repeats above-mentioned circulation, and just quality/the volume in the compression cylinder 22 will be compressed in two another ones in the firing chamber 48.
Shown in Fig. 5 a, after leaving compression cylinder 22 or separating with compression cylinder 22, fuel injects firing chamber 48 by fueling charger 62 at once.At first, fuel directly sprays on the glowing plug 82.In the start-up function process of motor 10, the effect of this glowing plug is the generation that strengthens the constant volume combustion in the firing chamber 48.But, motor 10 start working and warming-up after, the temperature and pressure conditions in the firing chamber 48 are enough to produce automatic igniting.On the other hand, by changing the relative phase between precombustion chamber pipe 44 and the compression cylinder 22, can when cold starting, adopt higher compression ratio, and behind motor 10 warming-ups, reduce compression ratio.
In order not need circulating plug when the cold starting, can adopt higher starting compression ratio, and the effective compression ratio when adopting lower work.By making pipe 44 post ignitions, the effective compression ratio during engine warm-up reduces, thereby has reduced the pressure peak in the firing chamber 48.The post ignition of these pipe 44 relative compression cylinders 22 or premature ignition can realize by the timing belt or the chain 104 of this pipe of bias voltage.In Figure 12 a and 12b, schematically show this point, wherein, by pipe 44 premature ignition and the post ignitions respectively of expansion bent axle 28 drivings, in Figure 13 a and 13b, by pipe 44 premature ignition and the post ignitions respectively of compression crankshaft 26 drivings.Timing spare 106 is bias voltage belt 104 selectively, so that carry out post ignition and premature ignition.
Shown in Figure 12 a, 12b, 13a and 13b, compression crankshaft and expansion bent axle are by belt/chain 108 become asynchronous mutually (time off).By adopting similar timing spare 110, cylinder phase relationship each other can change equally, and phase place shifts to an earlier date among Figure 12 a and the 13a, phase delay among Figure 12 b and the 13b.Such variability makes this start function to optimize under multiple operating conditions, and this point it will be appreciated by those skilled in the art that.
Because manage 44 around its central shaft 46 rotations, the while is owing to the fixed position of the fueling charger 62 in the engine cylinder 12, so fuel is not that sustained firing is to same position 82.But in the fuel injection process, the leading edge of firing chamber 48 is left in the injection of fuel gradually, makes the injection of injecting fuel break through firing chamber 48, shown in Fig. 5 b.By making the injection of injecting fuel break through firing chamber 48, the fuel in the firing chamber 48 is distributed well, thereby make that the mixing and burning in the firing chamber 48 is more complete.Owing to burn in the firing chamber of fixed volume, so the pressure in the firing chamber 48 significantly increases.In Ideal Cycle, the pressure in the firing chamber 48 is opened prior to the air vent 60 between expansion cylinder 24 and the firing chamber 48, makes to be approximately 85 barometric pressure less than the pressure in one cubic inch the volume.In the Ideal Cycle of Fig. 9, this state of firing chamber is generally with label 84 expressions.
In a preferred embodiment of the invention, three fueling chargers 62 have been adopted.Work that each injection syringe 62 is every when spraying for the third time once, so motor 10 can run up.Because the field of turbulent flow that injection of relatively long constant volume and material produce when being transported to expansion cylinder 24 by firing chamber 48, injection syringe 62 can be single hole low pressure parts, and therefore, the present invention can adopt the injection syringe and the syringe pump of standard.
When burning in firing chamber 48, pipe 44 makes firing chamber 48 rotations, thereby makes air vent 60 lead to expansion cylinder 24 effectively.At this moment, expansion piston 36 is near TDC, and shown in Fig. 4 c, the compressor in expansion cylinder 24 mixes with comburant and residue in the firing chamber 48.Compressor in new charge and the expansion cylinder 24 with comburant and mixing of residue cause the secondary heat release in the firing chamber, improved the combustion efficiency of motor simultaneously.It is aforesaid that fuel is injected firing chamber 48 is to carry out on the basis of rich oil.Inject by rich oil, make to begin to exit and mixes the heat release of back generation secondary with the expansion cylinder of fresh scavenging by air vent 60.By the secondary heat release is provided, combustion efficiency is increased, reduced NO
xFormation.Represent with arrow 86 on the mixed population of the compressor in comburant in the firing chamber 48 and residue and the expansion cylinder 24.When piston arrives TDC, can guarantee the generation of automatic igniting to the further compression of mixture.
In order to dispel the heat from the process of exitting in expansion cylinder 24 in firing chamber 48 by air vent 60, air vent 60 is arranged along steel sleeve (insert) 100.This lining 100 as shown in Figure 2.When firing chamber 48 continued to discharge in expansion cylinder 24 by air vent 60, expansion piston 36 its expansion of beginning or downward strokes burnt away and motor 10 external works done simultaneously.Subsequently, exhaust and residue are discharged by relief opening 42, and final product discharges from firing chamber 48, and this is respectively with arrow 88 and 90 expressions.Before expansion piston 36 arrived BDC, suction port 40 was opened, and utilized with the scavenging air of arrow 92 expressions and remove combustion by-product and residue from expansion cylinder 24.The scavenging of expansion cylinder 24 is shown in Fig. 4 b.In order to guarantee effective scavenging of expansion cylinder 24, be provided with the positive pressure source that scavenging air is provided to suction port 40.This malleation source of the gas can provide by several different methods, includes but not limited to utilize blower, pressurized machine float chamber scavenging technology.
In the compression stroke of expansion cylinder 24, moving on of expansion piston makes scavenging port and relief opening 42 close, and the material that re-fills in expansion cylinder 24 is compressed.Afterwards, having carried out self circuit second firing chamber 48 faces toward expansion cylinder 24 by air vent 60 and opens.Expansion cylinder 24 repetitions are for the above-mentioned circulation of second firing chamber 48 then.
Fig. 6 a to 6d has represented the geometrical compression ratio of compression cylinder 22 and expansion cylinder 24 respectively.The difference of geometrical compression ratio and effective compression ratio is, effective compression ratio is that the piston position when just closing with all cylinder-bore is a benchmark and definite, and geometrical compression ratio is benchmark and definite when the lower dead centre with piston.And compression ratio and expansion ratio comprise combustion chamber volume and its influence to the compression ratio of compression cylinder 22 and expansion cylinder 24 for each cylinder.The compression ratio of compressor and the expansion ratio of decompressor all comprise the volume of firing chamber, and the compression ratio of the expansion ratio of compressor and decompressor does not comprise the volume of firing chamber.
Time relationship between the motion of the motion of adjusting compression cylinder 22 and expansion cylinder 24 provides the timing chain or the belt that cooperate with the bent axle 26 and 28 of cylinder 22 and 24.And the rotation of pipe 44 also can be controlled by the similar timing chain or the belt that cooperate with one of the bent axle 26 of compression cylinder or bent axle 28 of expansion cylinder 24.The rotating speed of this pipe is half of speed of crankshaft.
Before closing the back from expansion cylinder 24 and leading to compression cylinder 22, scavenging is carried out in firing chamber 48, so that from firing chamber 48, remove residue.The scavenging of firing chamber 48 can realize that these mechanisms include but not limited to the crankcase scavenging system by various mechanism, or by adopting the malleation scavenging system to realize.In order to carry out scavenging, porose (not shown) on the housing 14 under the situation of utilizing the malleation scavenging, uses upstream blower (not shown).
The simulation of above-mentioned motor 10 proves that the overall power density of this diesel engine can be greater than 1.0.By to the research based on the turbosupercharged engine of following design parameter, specific power can reach 1.78 horsepowers/cubic inch.Design parameter is as follows:
| Parameter | Compression cylinder | Expansion cylinder |
| The expansive phase parallactic angle | ????60° | |
| Cylinder-bore | ????5.72cm | ????7.54cm |
| The bent axle stroke | ????4.83cm | ????5.59cm |
| Length of connecting rod | ????12.12cm | ????11.68cm |
| How much expansion ratios | ????90.16 | ????12.50 |
| Effective expansion ratio | ????76.86 | ????8.33 |
| Geometrical compression ratio | ????16.5 | ????17.52 |
| Effective compression ratio | ????14.19 | ????11.53 |
| Clearance volume | ????1.39cc | ????15.12cc |
| Discharge volume | ????123.80cc | ????249.78cc |
| Pipe/combustion-chamber parameter | |
| The firing chamber axial length | ????2.54cm |
| The bowl angle | ????55° |
| The opening angle | ????92.77° |
| The bowl volume | ????6.60cc |
| Engine performance result | |
| Volumetric efficiency | ????58.4％ |
| Motor indicated power | ????84.4hp |
| Engine brake power | ????78.3hp |
| Total braking force | ????81.0hp |
Motor 10 provides the output power except the bent axle 28 by expansion cylinder 24, because managing 44 directly or indirectly cooperates with bent axle 28, therefore also can provide power for multiple device to manage 44 output terminal 102, the output terminal 102 of this pipe stretches out from housing 14 and passes housing 14, and rotating speed is engine speed half.By explanation rather than limit, provide two devices of power or element comprise provides freezing mixture to housing 14 and engine cylinder 12 water pump 104 (see figure 1)s and properller by the output terminal 102 of pipe 44.
Though illustrated motor 10 adopts hyperbolic axle 26 and 28,, by changing compression cylinder 22 and expansion cylinder 24 position, can at an easy rate motor 10 be adopted single common crankshaft instead with respect to pipe 44.When the cylinder that uses surpasses two (compression cylinder and an expansion cylinder), both can adopt the single axle, also can adopt the hyperbolic axle.When using the hyperbolic axle, can adopt single pipe 44 and cylinder in inboard positioned opposite.When using the single axle, can be provided in the motor of four cylinders of outside positioned opposite.In such structure, can adopt two pipes, each pipe is used for a pair of cylinder in outside positioned opposite, and these two pipes can use common crankshaft and asynchronous fully.The design proposal of hyperbolic axle single tube four cylinders, inboard positioned opposite as shown in figure 10, and the embodiment four cylinders, outside positioned opposite, that the single axle is two-tube is as shown in figure 11.
Though the preferred embodiments of the present invention have been introduced in above-mentioned explanation, should be known at the proper range that does not break away from the accessory claim book and knowing under the situation of meaning, can improve, change and change the present invention.
Claims (45)
1. motor comprises:
One engine cylinder is limited with a compression cylinder and an expansion cylinder in this engine cylinder;
Reciprocating compressor structure in described compression cylinder, the reciprocal expansion mechanism in described expansion cylinder, described each reciprocator links to each other with a crankshaft, and described each reciprocator is mounted to can to-and-fro motion in described cylinder;
One precombustion chamber pipe is limited with two constant volume combustion chambers, and is limited with the vertical tubular axis that passes wherein in this precombustion chamber pipe, described firing chamber is positioned at the opposite side of described pipe, and becomes the outwards shape of depression basically;
One housing, this housing has the part that defines a cavity, be used to install described pipe in this cavity, described housing cooperates with described engine cylinder, and comprise the part that defines suction port and expansion hatch, described opening is forming passage between described pipe and the described compression cylinder and between described pipe and the described expansion cylinder respectively, described pipe is rotatably by described housing supporting, and described tubular axis towards vertical with the cylinder-bore axis that limits by compression cylinder and expansion cylinder basically, make the whirligig of described pipe rotation in addition;
Tarry device is so that coordinate the motion of described reciprocator and rotatablely moving of described pipe;
One fueling charger, the position of this fueling charger are suitable for injecting fuel in described firing chamber; And
Described pipe is rotation like this, that is, described firing chamber is successively by described suction port and being communicated with described compression cylinder, and disconnection and described compression cylinder is communicated with then, and enter the position of accepting fuel from described fueling charger, be communicated with described expansion cylinder by described expansion hatch then.
2. motor according to claim 1, wherein: described suction port and expansion hatch have been determined an opening angle, described opening angle is less than 120 degree.
3. motor according to claim 1, wherein: described suction port and expansion hatch have been determined an opening angle, described opening angle is in from about 85 degree to the scope of 100 degree.
4. motor according to claim 1, wherein: described suction port and expansion hatch have been determined an opening angle, described opening angle is in from about 90 degree to the scope of 95 degree.
5. motor according to claim 1, wherein: described compression cylinder and expansion cylinder have been determined a tilt angle, described tilt angle is less than 90 degree.
6. motor according to claim 1, wherein: described tilt angle is in from about 40 degree to the scope of 70 degree.
7. motor according to claim 1, wherein: a bowl angle has been determined in described firing chamber, described bowl angle is less than 90 degree.
8. motor according to claim 1, wherein: described bowl angle is in from about 45 degree to the scope of 65 degree.
9. motor according to claim 1, wherein: described housing comprises and defines the part of passing coolant channel wherein.
10. motor according to claim 9, wherein: water circulates by described coolant channel.
11. motor according to claim 1, wherein: described pipe comprises and defines the part of passing coolant channel wherein.
12. motor according to claim 11, wherein: oil circulates by described coolant channel.
13. motor according to claim 12, wherein: described oil makes the seal ring on the described pipe lubricated.
14. motor according to claim 13, wherein: described oil is supplied with described seal ring eccentrically by the pipeline in the described pipe.
15. motor according to claim 13, wherein: radial peg prevents the relative rotation of described seal ring with respect to described pipe.
16. motor according to claim 1, wherein: described tarry device is variable, to change the leading amount of described reciprocal expansion mechanism with respect to described reciprocating compressor structure.
17. motor according to claim 1, wherein: described tarry device is variable, so that described pipe is with respect to described reciprocating compressor structure and reciprocal in the expansion mechanism or with respect to described reciprocating compressor structure and back and forth expansion mechanism and premature ignition and post ignition.
18. motor according to claim 1, wherein: described reciprocator links to each other with a common crankshaft.
19. motor according to claim 1, wherein: described each reciprocator links to each other with independent bent axle.
20. motor according to claim 1, wherein: described firing chamber is determined by the inserting member that is removably mounted on the described pipe.
21. motor according to claim 20, wherein: described inserting member can exchange with not isometric other inserting member.
22. motor according to claim 20, wherein: described inserting member is made of steel.
23. motor according to claim 1, wherein: described expansion hatch comprises that one is loaded on lining wherein.
24. motor according to claim 23, wherein: described lining is made of steel.
25. motor according to claim 1, wherein: the described cavity of described housing comprises the lining inserting member that is loaded on wherein.
26. motor according to claim 25, wherein: described lining is made of steel.
27. motor according to claim 1, wherein: described expansion cylinder comprises scavenging port and the relief opening that is defined in wherein.
28. motor according to claim 27, wherein: described scavenging port cooperates with the crankcase that surrounds described bent axle, and the crankcase scavenging of positive pressure air for use in described expansion cylinder is provided.
29. motor according to claim 1, wherein: described compression cylinder comprises the scavenging port that is defined in wherein, and suction valve is arranged in described cylinder, and in its expansion stroke described compression cylinder is inflated.
30. motor according to claim 1 also comprises: the scavenging arrangement that described firing chamber is carried out scavenging.
31. motor according to claim 30, wherein: described scavenging arrangement comprises blower.
32. motor according to claim 1 also comprises: a water pump, described pump cooperate with the output shaft of described pipe and are driven by this output shaft.
33. motor according to claim 1, wherein: described motor is a diesel engine.
34. the operating method of a motor said method comprising the steps of:
In compression cylinder, introduce the air of a constant volume;
The air of this volume of compression in first cylinder of motor;
The air of minimum cylinder volume is input to a constant volume firing chamber from this first cylinder;
In the firing chamber with the air mixing of fuel and minimum cylinder volume;
The AIR MIXTURES of fire fuel and minimum cylinder volume in the firing chamber;
Ignition mixture in the firing chamber;
Make the air mixing of the minimum cylinder volume in the expansion cylinder of the mixture of burning and motor;
Beginning facing to behind the expansion cylinder opening, the further mixture of compression and combustion, thereby in expansion cylinder further ignition mixture, increase the combustion efficiency of motor;
Make the cubical expansion of the mixture after the burning in expansion cylinder and firing chamber;
In the cubical expansion process of the mixture after the burning in expansion cylinder and firing chamber, external output work; And
Combustion by-product is discharged from expansion cylinder.
35. method according to claim 34 is further comprising the steps of: the air volume of the compression in the firing chamber and compression cylinder are separated.
36. method according to claim 34, wherein: described blend step may further comprise the steps: fuel is injected the firing chamber, and make the firing chamber spray into a motion with respect to fuel when burner oil.
37. method according to claim 34, wherein: described lighting up procedure is caused by compression.
38. method according to claim 34, wherein: described blend step may further comprise the steps: make the air movement of the volume compression in the firing chamber and through fueling charger, and through out-of-date fuel is injected air compression volume in the firing chamber at minimum cylinder volume.
39. according to the described method of claim 38, wherein: through out-of-date, during whole, burn basically in the firing chamber.
40. method according to claim 34, wherein: the mixing of described fuel has produced oil-rich mixture.
41. the method for an output work from combustible fluid said method comprising the steps of:
Compress the air of a constant volume;
Fuel is injected the air of volume compression, to generate fuel/air mixture;
This fuel/air mixture of burning makes volume keep constant simultaneously in the part of carrying out combustion disposal;
Part is compressed the air of second volume;
To just introduce in second air volume of part compression, thereby form the 3rd volume, strengthen the burning of fuel/air mixture at burnt fuel/air mixture;
Compress the 3rd volume, and burn away; And
Make the 3rd cubical expansion, and in the inflation process of the 3rd volume output work.
42. according to the described method of claim 41, further comprising the steps of: the air with the volume compression behind described compression step separates.
43. according to the described method of claim 41, wherein: described implantation step may further comprise the steps: change spraying into a little of fuel with respect to the volume that compresses, this change can be carried out in the whole process of implantation step.
44. according to the described method of claim 41, also comprise: the step of carrying out compression cycle, this step comprises the step of the air of described compression one constant volume, and it is further comprising the steps of: the major component and the remaining volume of the air of volume compression are separated, residual volume is expanded, thereby its pressure is decreased near vacuum, sucks air in certain amount replacing described vacuum, and compress this air volume and repeat this circulation.
45. according to the described method of claim 41, also comprise: the step of carrying out expansion cycle, this step may further comprise the steps: part is compressed the air of second volume, burnt fuel/air mixture is introduced in second air volume, to form the 3rd volume, compress the 3rd volume and this fuel/air mixture of further burning, make the 3rd cubical expansion and output work, utilize the air of a constant volume to discharge the 3rd volume, part is compressed this air volume and is repeated this circulation.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US7823698P | 1998-03-17 | 1998-03-17 | |
| US60/078,236 | 1998-03-17 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1298472A true CN1298472A (en) | 2001-06-06 |
Family
ID=22142790
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN99805504A Pending CN1298472A (en) | 1998-03-17 | 1999-03-17 | High power density diesel engine |
Country Status (9)
| Country | Link |
|---|---|
| EP (1) | EP1064458A4 (en) |
| JP (1) | JP2002506949A (en) |
| KR (1) | KR20010041930A (en) |
| CN (1) | CN1298472A (en) |
| AU (1) | AU3089899A (en) |
| BR (1) | BR9909653A (en) |
| CA (1) | CA2324102C (en) |
| MX (1) | MXPA00009112A (en) |
| WO (1) | WO1999047804A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105697141B (en) * | 2016-03-24 | 2019-02-01 | 张忠友 | Air-cooled Λ type two-stroke double stopper type diesel supercharging engine |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6543225B2 (en) | 2001-07-20 | 2003-04-08 | Scuderi Group Llc | Split four stroke cycle internal combustion engine |
| WO2003040530A2 (en) | 2001-11-02 | 2003-05-15 | Scuderi Group Llc | Split four stroke engine |
| MY138166A (en) | 2003-06-20 | 2009-04-30 | Scuderi Group Llc | Split-cycle four-stroke engine |
| US6986329B2 (en) | 2003-07-23 | 2006-01-17 | Scuderi Salvatore C | Split-cycle engine with dwell piston motion |
| US7597084B2 (en) * | 2005-03-09 | 2009-10-06 | Caterpillar Inc. | Internal combustion engine and operating method therefor |
| US7513224B2 (en) * | 2006-09-11 | 2009-04-07 | The Scuderi Group, Llc | Split-cycle aircraft engine |
| US9097178B2 (en) * | 2011-11-30 | 2015-08-04 | Tour Engine, Inc. | Crossover valve in double piston cycle engine |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1211950A (en) * | 1912-07-30 | 1917-01-09 | Hector Vivian Lough | Internal-combustion engine. |
| GB266386A (en) * | 1926-02-22 | 1927-08-18 | Fernand Laguesse | Improvements relating to internal combustion engines |
| GB1481802A (en) * | 1973-09-07 | 1977-08-03 | Cross Mfg Co | Internal combustion engines |
| US4015424A (en) * | 1975-04-11 | 1977-04-05 | Sakuta Shinohara | Combustion engine with dual function motor element and rotary valve for cyclical fuel and exhaust metering |
| CH654067A5 (en) * | 1982-09-24 | 1986-01-31 | Roger Bajulaz | COMBUSTION ENGINE AND METHOD FOR ACTIVATING IT. |
| US4553385A (en) * | 1983-11-18 | 1985-11-19 | Lamont John S | Internal combustion engine |
| US4739615A (en) * | 1986-01-14 | 1988-04-26 | Staheli Arthur A | Internal combustion engine in which compressed fuel mixture is combusted externally of the cylinders of the engine in a rotating combustion chamber |
| US4876992A (en) * | 1988-08-19 | 1989-10-31 | Standard Oil Company | Crankshaft phasing mechanism |
| JP3287846B2 (en) * | 1992-11-06 | 2002-06-04 | エイ イー ビショップ リサーチ プロプライエタリー リミテッド | Gas sealing system for rotary valve |
| US6199369B1 (en) * | 1997-03-14 | 2001-03-13 | Daniel J. Meyer | Separate process engine |
| GB9711058D0 (en) * | 1997-05-30 | 1997-07-23 | Douglas John L | A rotary internal combustion engine |
-
1999
- 1999-03-17 AU AU30898/99A patent/AU3089899A/en not_active Abandoned
- 1999-03-17 EP EP99912541A patent/EP1064458A4/en not_active Withdrawn
- 1999-03-17 CN CN99805504A patent/CN1298472A/en active Pending
- 1999-03-17 CA CA002324102A patent/CA2324102C/en not_active Expired - Lifetime
- 1999-03-17 KR KR1020007010238A patent/KR20010041930A/en not_active Application Discontinuation
- 1999-03-17 BR BR9909653-6A patent/BR9909653A/en not_active IP Right Cessation
- 1999-03-17 MX MXPA00009112A patent/MXPA00009112A/en unknown
- 1999-03-17 JP JP2000536966A patent/JP2002506949A/en active Pending
- 1999-03-17 WO PCT/US1999/005632 patent/WO1999047804A1/en not_active Application Discontinuation
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105697141B (en) * | 2016-03-24 | 2019-02-01 | 张忠友 | Air-cooled Λ type two-stroke double stopper type diesel supercharging engine |
Also Published As
| Publication number | Publication date |
|---|---|
| CA2324102C (en) | 2007-12-04 |
| EP1064458A1 (en) | 2001-01-03 |
| KR20010041930A (en) | 2001-05-25 |
| BR9909653A (en) | 2000-11-21 |
| AU3089899A (en) | 1999-10-11 |
| CA2324102A1 (en) | 1999-09-23 |
| JP2002506949A (en) | 2002-03-05 |
| WO1999047804A1 (en) | 1999-09-23 |
| EP1064458A4 (en) | 2004-07-14 |
| MXPA00009112A (en) | 2004-09-10 |
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| SE01 | Entry into force of request for substantive examination | ||
| ASS | Succession or assignment of patent right |
Owner name: NEXTEL DIESEL MOTOR CO.,LTD. Free format text: FORMER OWNER: TECAT ENGINEERING, INC. Effective date: 20020509 |
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| C41 | Transfer of patent application or patent right or utility model | ||
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| CB04 | Change of attorney information |
Agent after: Fan Li Agent before: Yi Yongmei |
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| TA01 | Transfer of patent application right |
Effective date of registration: 20020509 Address after: Michigan Applicant after: Nekes Tell diesel engines Address before: Michigan Applicant before: Tecat Engineering, INC. |
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