CN101253316A - Steam enhanced double piston cycle engine - Google Patents
Steam enhanced double piston cycle engine Download PDFInfo
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- CN101253316A CN101253316A CNA2006800184102A CN200680018410A CN101253316A CN 101253316 A CN101253316 A CN 101253316A CN A2006800184102 A CNA2006800184102 A CN A2006800184102A CN 200680018410 A CN200680018410 A CN 200680018410A CN 101253316 A CN101253316 A CN 101253316A
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Abstract
A steam enhanced dual piston cycle engine utilizes a unique dual piston apparatus that includes: a first cylinder housing a first piston therein, wherein the first piston performs only intake and compression strokes; a second cylinder housing an inner power piston that forms an inner internal chamber of the second cylinder, and either a ring-shaped outer power piston surrounding the inner power piston, wherein the outer power piston forms an outer internal chamber of the second cylinder and is configured to convert engine heat into additional work, and/or an outer boiler which is configured to produce steam to be converted into additional work.
Description
Related application
The application relates on March 9th, 2006 and submits the total U.S. Patent application 11/371st of exercise question for " DOUBLE PISTON CYCLE ENGINE (DPCE) " to, the follow-up application of 827 part, its full content with referring to mode include this paper in, and the exercise question that it relates on March 11st, 2005 submits to is the temporary patent application the 60/661st of " DOUBLE PISTONCYCLE ENGINE (DPCE) ", 195, its full content with referring to mode include this paper in.The exercise question that the application also relates on April 18th, 2005 and submits to is the U.S. Provisional Application the 60/672nd, 421 of " STEAM ENHANCEDDOUBLE PISTON CYCLE ENGINE (SE-DPCE) ", its full content with referring to mode include this paper in.
Background of invention
Technical field
Relate generally to internal-combustion engine of the present invention, and relate more specifically to strengthen double piston cycle engine (SE-DPCE) than the more effective steam of conventional internal-combustion engine.
The explanation of association area
Be appreciated that internal-combustion engine is ubiquitous and used more than 100 year now.Usually, internal-combustion engine comprises one or more cylinders.Each cylinder comprises carries out four-stroke single piston, and that described four strokes are commonly referred to is air-breathing, compression, burning/power and exhaust stroke, and they form the complete cycle of conventional piston together.
The subject matter of conventional internal-combustion engine is that fuel efficiency is low.A greater part of fuel oil potential heat energy of conventional engine generation dissipates by engine structure and does not increase any useful mechanical work according to estimates.The main cause of this thermal waste is the basic cooling needs of conventional engine.Compare with the total amount of heat that in fact changes into useful work, cooling system (for example, radiator) self dissipates with bigger speed and bigger amount.Another problem of conventional internal-combustion engine is to regenerate with heat or method for recycling when higher combustion temperature is provided, and they can not increase efficient.
Another reason that conventional engine runs into efficiency be air-breathing and compression stroke during high temperature in the cylinder make that the piston operation is more difficult, therefore efficient is lower in these strokes.
Another shortcoming about existing internal-combustion engine is that they can not further increase combustion temperature and improve compression ratio; Although improve chamber temperature and increase compression specific energy improvement efficient at power stroke.
Another problem of conventional engine is that their incomplete chemical combustion process produces harmful toxic emission.
Although these devices may be suitable for the special purpose that they will solve, but they are effective unlike the twin cylinder SE-DPCE that utilizes the temperature differentiation that is proposed, the latter is divided into two low temperature strokes (air-breathing and compression) and two high temperature strokes (power and exhaust) by each execution in the corresponding double-piston with the conventional four-stroke of a piston, the heat of also utilizing the high temperature stroke to produce simultaneously produces steam, and steam is used for additional heat energy is changed into mechanical energy.
Although other document had before disclosed the Dual-piston IC engine structure, all do not provide essence efficient of the present invention and improvement in performance.For example, the U.S. Patent No. 1,372,216 of authorizing Casaday has disclosed the Dual-piston IC engine of cylinder and the setting of piston corresponding pairs.The piston of combustion cylinder moves prior to the piston of compression cylinder.The U. S. Patent the 3rd, 880,126 of authorizing people such as Thurston has disclosed two-stroke cycle separate cylinders internal-combustion engine.The induction cylinder piston before the piston of actuating cylinder a little fewer than half stroke move.Respond to a charging of cylinder compresses, and actuating cylinder is transferred in charging, charging mixes with the remaining charging of previous circuit products of combustion there, and further compression before lighting.The U.S. Patent application No.2003/0015171 A1 that authorizes Scuderi has disclosed a kind of Otto (cycle) engine.Power piston in first cylinder is connected on the crankshaft and carries out the power and the exhaust stroke of four stroke cycle.Compression piston in second cylinder also is connected to crankshaft and carries out the air-breathing and compression stroke of same four stroke cycle during the same rotation of crankshaft.The power piston of first cylinder moves prior to the compression piston of second cylinder.The U.S. Patent No. 6,880,501 of authorizing people such as Suh has disclosed the internal-combustion engine with a countercylinder, and each cylinder comprises the piston that is connected to a crankshaft.A cylinder is suitable for air-breathing and compression stroke.Another cylinder is suitable for power and exhaust stroke.The U.S. Patent No. 5,546,897 of authorizing Brackett has disclosed can carry out two, four or many cylinders of diesel powered circuit reciprocating IC engine.
But how these data distinguishes cylinder temperature with (power) cylinder and compression cylinder and the surrounding environment isolation of will burning effectively if not disclosing.These data do not disclose the mutual temperature effect minimum that how to make between each cylinder and the surrounding environment yet.In addition, these data do not have to disclose yet and exceed conventional cylinder of internal combustion engine and further raise the temperature of combustion cylinder and the engine modifications of temperature that reduces compression cylinder to promote engine efficiency and performance.Specifically, make the minimum permission of temperature of compression cylinder reduce the compression work input, and the temperature of increase actuating cylinder allow to increase heat regeneration.In addition, the center-aisle that the cylinder that respectively separates that discloses in these documents all passes through delivery valve or some type connects, and they produce " dead space " of a constant volume between cylinder, makes gas can accumulate between the cylinder and the further efficient that reduces motor.In addition, above-mentioned these prior art documents are not all taught a kind of relative or " V " cylinder and crankshaft structure, and this structure makes dead space minimum between the cylinder, makes each cylinder adiabatic to keep the temperature difference of promoting between the cylinder simultaneously.At last, these prior art documents all disclose will burn/power house is divided into two chamber bodies that separate and utilizes the steam in the outside cabin can be used for extra engine efficiency and merit.In addition, the prior art document does not all have to disclose or propose to comprise the level two of main combustion chamber, and it can change into extra kinetic energy by the superfluous heat energy that the hot cell produces.
The U.S. Patent No. 5,623,894 of authorizing Clarke has disclosed two compressions and two expansion internal-combustion engine.The inner housing that holds two pistons moves in the frame of the separate chambers body that is formed for compressing and expands.But Clarke has comprised the single chamber body of carrying out all engine strokes, prevents the isolation and/or the raising temperature difference such as those each cylinder bodies of the present invention's announcement.Clarke does not have to disclose the chamber that separates that is formed for utilizing by the thermogenetic additional energy of too much motor (for example, hot air or steam) yet.
Authorize the U.S. Patent No. 3 of Thomas, 959,974 have disclosed the internal-combustion engine of the combustion cylinder that comprises that part is made by the material that can bear high temperature, and this combustion cylinder comprises power piston and is connected to the annular portion that comprises another piston that remains on lower temperature at no loop section.But whole Thomas motor is not only in whole burning and exhaust stroke, and is in the temperature of raising during the part compression stroke.In addition, Thomas does not disclose with relative or " V " structure and isolates engine cylinder can improving the method for the temperature difference, and has disclosed in the air inlet that connects cylinder and comprise sizable dead space.At last, Thomas does not disclose the chamber that separates that is formed for utilizing by the thermogenetic additional energy of superfluous motor (for example, hot air or steam).
In these areas, deviate from the conventional conception and the design of prior art basically according to SE-DPCE of the present invention, and provide like this than the more effective significantly improved internal-combustion engine of conventional internal-combustion engine.
Summary of the invention
Consider the aforementioned inherent defect of the known type internal-combustion engine that exists now in the prior art, the new invention that proposes provides SE-DPCE internal-combustion engine, it utilizes the temperature difference cylinder that more effectively fuel oil is converted to energy or merit than conventional internal-combustion engine, and converts the engine thermal of surplus to extra useful work.
In an embodiment of the present invention, steam strengthens double piston cycle engine (SE-DPCE) and utilizes the temperature difference cylinder that more effectively fuel oil is converted to energy or merit than conventional internal-combustion engine, as U.S. Provisional Application the 60/661st, as described in 195, its full content with referring to mode include this paper in, and can and convert thereof into extra useful motor merit and further promote the DPCE device by utilizing engine thermal to produce steam.
In one embodiment of this invention, motor comprises first cylinder that connects with second cylinder, and first piston is positioned at first cylinder and is configured to carry out air-breathing and compression stroke, and second piston is positioned at second cylinder and is configured to carry out power and exhaust stroke.Perhaps, can consider that first and second cylinders are the single cylinder with two separate chambers that are coupled to each other in single cylinder, wherein first piston is positioned at first indoor and second piston and is positioned at second indoor.
In another embodiment, motor also comprises the Aspirating valves that connects with first cylinder, outlet valve that connects with second cylinder and the interstage valve that the interior chamber of first cylinder is connected to the interior chamber of second cylinder.
In another embodiment, motor comprises two-piston connecting rod, compression crankshaft, power crank axle and two crankshaft connecting rods.These connecting rods are connected to respective pistons on their corresponding crankshafts.The compression crankshaft will rotatablely move and convert the to-and-fro motion of first piston to.The power crank axle converts second reciprocating motion of the pistons to the engine revolution output movement.The crankshaft connecting rod converts the power crank axle rotation of to compression crankshaft.
In another embodiment, motor comprises fuel injector, water/steam inlet valve and water/steam discharge valve.First compression cylinder holds the part of compression piston, Aspirating valves and interstage valve.Second actuating cylinder comprises two cylinders that separate: outer cylinder and inner cylinder.Externally with in the inner cylinder double-piston arranged: dish type internal piston and annular, outer piston.In addition, second actuating cylinder comprises a part, fuel injector, spark plug, steam/water valve (and/or sparger) and the steam/water/bleed air valve of outlet valve, outside exit casing (outlet pipe of packing), thermal-protective coating, interstage valve.First compression piston is carried out air-breathing and compression engine stroke.The internal motivation piston carries out the oil inflame power stroke and exhaust (gas after the burning) discharges stroke.The external impetus piston has or does not have the hot compressed air of steam/water to produce power and absorb the motor excess heat by utilization.Connecting rod all is connected to compression piston and two power pistons on their corresponding crankshafts.The compression crankshaft will rotatablely move and convert the compression piston to-and-fro motion to.The power crank axle converts the to-and-fro motion of inside or external impetus piston to the engine revolution output movement.The crankshaft connecting rod converts the power crank axle rotation of to compression crankshaft.
In another embodiment, the motor Aspirating valves comprises the axle with cone seal surface, with used identical in most of four stroke engine.Outlet valve comprises the axle with cone seal surface, with used identical in most of four-stroke compressors.Interstage valve (in preferred embodiment) is made up of the axle with cone seal surface.
In another embodiment, a kind of method of improving the efficiency of internal combustion engine comprises separates air-breathing and pressing chamber (cold punching journey) and burning and exhaust chamber (hot stroke), and therefore can reduce temperature and increase temperature in combustion stroke in air-breathing and compression stroke, improve engine efficiency thus.
In another embodiment, a kind of method of improving engine efficiency comprises that the temperature that makes air-breathing and compression stroke is minimum or reduces.Air-breathing and pressurized air/feeding temperature is low more, engine efficiency is high more.
In another embodiment, the method for improvement compressor efficiency comprises regeneration and utilizes exhausting heat energy.
In another embodiment, provide a kind of Dual-piston IC engine, it greatly reduces the external refrigeration demand, and it has increased the potential available heat that is used for the conversion of heat output merit during the power stroke again, its also more effectively burn fuel oil and reduce noxious emission thus.
In another embodiment, a kind of method that the internal-combustion engine that improves efficient is provided is included in carries out air-breathing and compression and carry out power and exhaust stroke in second cylinder in first cylinder, and wherein first cylinder remains on the temperature lower than second cylinder.In another embodiment, this method also comprises from first cylinder pressurized air and fuel oil mixture is ejected in second cylinder, cools off second cylinder thus.
In another embodiment, steam strengthens Dual-piston IC engine and also comprises doughnut in the combustion cylinder holding pressurized gas and/or liquid, thereby utilizes superfluous engine thermal to produce extra power and increase engine efficiency.In another embodiment, steam enhancing Dual-piston IC engine comprises that also the interior doughnut of compression cylinder is so that pressurized gas and/or liquid are transferred to vaporium effectively.In another embodiment, steam strengthens Dual-piston IC engine and comprises two power generation systems that separate, and main system is utilized the Fuel Air burning, and the engine thermal of auxilliary system utilization surplus is carried out steam power regeneration.
Description of drawings
Fig. 1 is the simplified side cross-sectional view of DPCE device according to an embodiment of the invention, and wherein crankshaft angular is depicted as 270 degree.
Fig. 2 is the simplified side cross-sectional view of the DPCE device of Fig. 1, and wherein crankshaft angular is depicted as 315 degree.
Fig. 3 is the simplified side cross-sectional view of the DPCE device of Fig. 1, and wherein crankshaft angular is depicted as 330 degree.
Fig. 4 is the simplified side cross-sectional view of the DPCE device of Fig. 1, and wherein crankshaft angular is depicted as 0 degree.
Fig. 5 is the simplified side cross-sectional view of the DPCE device of Fig. 1, and wherein crankshaft angular is depicted as 45 degree.
Fig. 6 is the simplified side cross-sectional view of the DPCE device of Fig. 1, and wherein crankshaft angular is depicted as 90 degree.
Fig. 7 is the simplified side cross-sectional view of the DPCE device of Fig. 1, and wherein crankshaft angular is depicted as 135 degree.
Fig. 8 is the simplified side cross-sectional view of the DPCE device of Fig. 1, and wherein crankshaft angular is depicted as 180 degree.
Fig. 9 is the simplified side cross-sectional view of the DPCE device of Fig. 1, and wherein crankshaft angular is depicted as 225 degree.
Figure 10 is the simplified side cross-sectional view that has the DPCE device of air cooling compression cylinder and exhaust heating actuating cylinder according to one embodiment of the invention.
Figure 11 is the simplified side cross-sectional view that has the DPCE device of water cooling pressing chamber cylinder and exhaust heating power house according to one embodiment of the invention.
Figure 12 is that 3 dimensions (3D) of DPCE compression according to an embodiment of the invention and power piston are simplified view.
Figure 13 is that 3 dimensions (3D) of DPCE compression according to an embodiment of the invention and power crank axle are simplified view.
Figure 14 is that 3 dimensions (3D) of DPCE compression according to an embodiment of the invention and power crank axle are simplified view.
Figure 15 is that 3 dimensions (3D) of DPCE crankshaft system are according to an embodiment of the invention simplified view, shows the crankshaft connecting rod.
Figure 16 is that 3 dimensions (3D) of DPCE crankshaft system are according to an embodiment of the invention simplified view, shows two crankshaft connecting rods.
Figure 17 is that 3 dimensions (3D) of DPCE crankshaft system are according to an embodiment of the invention simplified view, shows different crankshaft angular.
Figure 18 is that 3 dimensions (3D) of DPCE crankshaft system are according to an embodiment of the invention simplified view, has a crankshaft connecting rod that combines with timing tape (or chain or V-belt).
Figure 19 is that 3 dimensions (3D) of DPCE crankshaft system are according to an embodiment of the invention simplified view, only has timing tape (or chain or V-belt).
Figure 20 is that 3 dimensions (3D) of DPCE crankshaft system are according to an embodiment of the invention simplified view, has the crankshaft gear wheel as bindiny mechanism.
Figure 21 is that 3 dimensions (3D) of DPCE crankshaft system are according to another embodiment of the present invention simplified view, has the crankshaft gear wheel as bindiny mechanism.
Figure 22 is the simplified cross-sectional view of interstage valve according to an embodiment of the invention.
Figure 23 simplifies inter-stage relief valve sectional view according to an embodiment of the invention.
Figure 24 is the simplified cross-sectional view of semi-automatic interstage valve according to an embodiment of the invention.
Figure 25 is the simplified cross-sectional view of DPCE device according to an embodiment of the invention, has boosting capability.
Figure 26 be according to an embodiment of the invention the DPCE device 3 the dimension reduced graphs, have compression cylinder and actuating cylinder on Different Plane.
Figure 27 is the 3D reduced graph of DPCE device according to an embodiment of the invention, and wherein two cylinders are parallel to each other and two-piston moves in mode one in front and one in back.
Figure 28 is the side simplified cross-sectional view of SE-DPCE device according to an embodiment of the invention.
Figure 29 is the 3D simplified cross-sectional view of inside and outside actuating cylinder according to an embodiment of the invention.
Figure 30 be according to an embodiment of the invention power piston 3 the dimension reduced graphs, also comprise inside and outside piston.
Figure 31 is the 3D simplified cross-sectional view of inside and outside according to an embodiment of the invention actuating cylinder and respective inner and external impetus piston.
Figure 32 is the side simplified cross-sectional view that has the SE-DPCE device of two independent compression pistons according to an embodiment of the invention, and one of them piston is used for combustion process, and another piston is used for water/vaporium.
Figure 33 uses two simplified side cross-sectional view of separating the SE-DPCE device of output shaft according to an embodiment of the invention, and wherein the combustion process part is separated with steam enhancing part.
Figure 34 is the sectional view that comprises the SE-DPCE device of ebullator chamber according to another embodiment of the present invention.
Embodiment
Following with reference to the present invention of accompanying drawing detailed description, wherein similar component all is marked with like numerals will.Be to be understood that what accompanying drawing was not necessarily drawn in proportion.All details of each exemplary embodiment shown in they also not necessarily show.On the contrary, they only show some feature and the member that exemplary embodiment of the present can be described.
Referring to Fig. 1, according to one embodiment of the invention, the DPCE cylinder comprises: compression cylinder 01, actuating cylinder 02, compression piston 03, power piston 04, two-phase are answered piston connecting rod 05 and 06, compression crankshaft 07, power crank axle 08, crankshaft connecting rod 09, Aspirating valves 10, outlet valve 11 and interstage valve 12.Compression cylinder 01 is the piston engine cylinder that holds the part of compression piston 03, Aspirating valves 10 and interstage valve 12.Actuating cylinder 02 is the piston engine cylinder towards the lip-deep spark plug (not shown) of the firing chamber of cylinder 02 that holds the part of power piston 04, outlet valve 11, interstage valve 12 and be positioned at power piston 04 surperficial the place ahead.Compression piston 03 is used for air-breathing and the compression engine stroke.Power piston 04 is used for power and exhaust stroke.Connecting rod 05 and 06 is connected to their corresponding piston on their corresponding crankshafts.Compression crankshaft 07 will rotatablely move and convert the to-and-fro motion of compression piston 03 to.The to-and-fro motion of power piston 04 converts rotatablely moving of power crank axle 08 to, and it converts rotatablely moving of motor or merit (that is, crankshaft 08 is as the DPCE output shaft) again to.Crankshaft connecting rod 09 is transformed into the rotation of power crank axle 08 rotation of compression crankshaft 07.
In one embodiment, Aspirating valves 10 is made up of the axle with cone seal surface, and is identical with Aspirating valves used in the most conventional four stroke engine.Outlet valve 11 is made up of the axle with cone seal surface, and is identical with outlet valve used in the most conventional four stroke engine.Interstage valve 12 also is made up of the axle with cone seal surface.
Referring to Fig. 1, in compression cylinder 01 B of interior chamber, be compression piston 03 again.The direction that compression piston 03 is pointed out with respect to arrow shown in compression cylinder 01 edge moves.In actuating cylinder 02 C of interior chamber is power piston 04.The direction that power piston 04 is pointed out with respect to arrow shown in actuating cylinder 02 edge moves.Compression cylinder 01 and compression piston 03 B of delimit chamber.Actuating cylinder 02 and power piston 04 C of delimit chamber.In preferred embodiment, the power piston pressure surface has the shaping alcove 26 (seeing Figure 12) of additional chamber C, and it is used as additional combustion chamber volume in combustion process.Chamber B is communicated with chamber C fluid by inter-stage mechanically operated valve 12.Compression cylinder 01 has Aspirating valves 10.Chamber B is communicated with gasified fuel/air feed A fluid by Aspirating valves 10.Actuating cylinder 02 has outlet valve 11.Chamber C is communicated with ambient air D fluid by outlet valve 11.When at open position, outlet valve 11 can be discharged waste gas.During combustion stroke, power piston 04 propulsion power connecting rod 06, power crank axle 08 is turned clockwise.In exhaust stroke, inertial force (by flywheel mass produce-not shown) make power crank axle 08 continue it to turn clockwise, and cause that power connecting rod 06 moves power piston 04, it discharges waste gas after the oil inflames by valve 11 again.08 rotation of power crank axle is hinged with synchronous rotation (that is, two crankshafts are with identical speed and dynamic angular rotation) with compression crankshaft 07 by crankshaft connecting rod 09.In one embodiment, two-piston, promptly power piston 04 and compression piston 03 pass through their upper dead center (TDC) position and their lower dead centre (BDC) position of process simultaneously.In another embodiment, according to desired timing structure, but the amount that the relative position phase shifts one of power piston 04 and compression piston 03 is required, in one embodiment, DPCE twin cylinder device uses conventional pressurization cooling and oil lubrication method and system (not shown).Although in an embodiment according to the present invention, power house C-structure parts (such as cylinder 02 and piston 04) keep the temperature more much higher than conventional internal-combustion engine, and in one embodiment, the parts of power house C carry out temperature control with cooling system.In addition, some or all of parts can be made by exotic material, such as pottery, carbon or stainless steel.In further embodiments, applicable known high voltage timing of DPCE device and spark plug electrical system (not shown) and electric starter motor are controlled plug ignition, timing and engine start rotation.
Shown in Fig. 1 to 9, when electric starter cooperates DPCE output shaft 6 ' (Figure 15), they turning clockwise and two-piston 03 and 04 their to-and-fro motion of beginning of two crankshafts 07 and 08 beginning.As shown in Figure 5, compression piston 03 and power piston move along the direction that increases chamber B and chamber C volume.Because Aspirating valves 10 is at its open position and because continue to increase at this stage chamber B volume, (expression Carburetor delivery outlet for example) flows to chamber B by Aspirating valves 10 from an A for gasified fuel or fresh air charging (when using fuel injection system).Correspondingly shown in Fig. 6 to 8, chamber B volume increases and Fuel Air charging inflow.Along with compression piston 03 arrives its BDC point, Aspirating valves 10 cuts out air-fuel oil charging content of the B of dust trapping chamber.Simultaneously crankshaft continues rotation clockwise, and respectively shown in Fig. 9 and Fig. 1 to 3, air-fuel oil feeding temperature that chamber b volume reduces and it captures now and pressure rise.Along with compression piston 03 near predetermined point (Fig. 3), interstage valve 12 is opened and air-fuel oil incoming flow of chamber B is entered the room C.Along with compression piston near its TDC point (may introduce some delays or in advance) according to some embodiments, interstage valve 12 is closed and plug ignition simultaneously.
Fig. 5-8 shows power stroke.Owing to burn, chamber C pressure increase is propulsion power piston 04 effectively, and its mobile again connecting rod 06 is with rotating power crankshaft 08, it be connected to DPCE output shaft 06 '.Simultaneously and since compression piston 03 from its tdc position to pushing back, Aspirating valves 10 is opened and is made the new air oil charging A can suction chamber B.
When arriving its BDC point, power piston 04 begins exhaust stroke (Fig. 8).Outlet valve 11 is opened and chamber C volume reduces, and waste gas after burning is released by the outlet valve of opening 11 from chamber C and entered surrounding environment D.
Therefore, the DPCE motor will be divided into two cylinders that thermal characteristics is different with the stroke that cylinder is carried out by a piston of conventional internal-combustion engine, and wherein each cylinder is carried out half of four stroke cycle." cold " cylinder is carried out air-breathing and compression stroke and heat insulation " heat " cylinder is carried out burning and exhaust stroke.Compare with conventional engine, this novel system and process make the DPCE motor can be with higher chamber temperature with lower air-breathing and pressing chamber temperature work.Adopt higher combustion temperature, keep lower air-breathing and compression temperature can reduce the engine cooling demand simultaneously again, reduced the compression energy demand and therefore improved engine efficiency.In addition, actuating cylinder and external environment condition be heat insulation to have limited the external heat loss, makes same heat can re-use at one-stroke down, and the still less fuel oil that burns in each circulation.
In one embodiment, compression cylinder 01 is similar to the classic piston engine cylinder, and it holds the part of compression piston 03, Aspirating valves 10 and interstage valve 12.Compression cylinder 01 and compression piston 03 joint work are with the air and/or the fuel oil charging that suck and compression is come in.In preferred embodiment, cooled compression cylinder.Figure 10 shows the air cooled compression cylinder with thermal absorption and radiation rib 20.Figure 11 shows the liquid cooling compression cylinder with cooling liquid path 22.In preferred embodiment, cooling air source or liquid coolant source can with prior art in known identical.In preferred embodiment, compression cylinder 01 and actuating cylinder 02 should be heat insulation mutually and heat insulation with surrounding environment.Figure 26 shows the embodiment of two cylinder configuration on Different Plane, and therefore realizes minimum mutual heat conduction between two cylinders.
In a preferred embodiment, actuating cylinder 02 except with external insulation also use waste heating.Figure 10 and 11 shows when waste gas and conduct the heat to waste gas heat utilization in the actuating cylinder heat tunnel 24 in their exhaust air flow process.
As explained above, compression connecting rod 05 connects compression crankshaft 07 and compression piston 03, makes that piston 03 can be with respect to the cylinder to-and-fro motion.Power connecting rod 06 connects power crank axle 08 and power piston 04.At combustion phase, power connecting rod 06 is transferred to power crank axle 08 so that its rotation with piston 04 motion.At exhaust phase, the rotation of power crank axle 08 and impulse force are to pushing back moving power piston 04 towards compression cylinder 01, and the gas after it will burn by outlet valve is again discharged (exhaust stroke).
Referring to Figure 13, compression crankshaft 07 will rotatablely move and convert compression piston 03 to-and-fro motion to.Compression crankshaft 07 will rotatablely move and convert compression piston 03 to-and-fro motion to.Compression crankshaft 07 connects compression connecting rod 05 and crankshaft connecting rod 09 (Fig. 1).The motion of crankshaft connecting rod 09 causes 07 rotation of compression crankshaft.The motion that the rotation of compression crankshaft 07 produces compression connecting rod 05, it again with compression piston 03 with respect to its cylinder casing 01 to-and-fro motion.
In various embodiments of the present invention, compression crankshaft 07 and power crank axle 08 structure construction can be according to desired engine construction with designs and different.For example, some crankshaft design factors are: double cylinder quantity, cylinder position relatively, crankshaft gear wheel mechanism and sense of rotation.For example, if compression crankshaft 07 and power crank axle 08 along the equidirectional rotation, crankshaft 07 and 08 axis should be mutually positioning become 180 degree, as shown in figure 13.Perhaps, if compression and power crank axle 07 and 08 rotation in opposite direction respectively, two crankshaft axis should be relative to each other with the homophase location, as shown in figure 14.
Power crank axle 08 connects power connecting rod 06 and crankshaft connecting rod 09.When burning took place, power piston 04 moved, and by its power connecting rod 06, made power crank axle 08 rotation that also is connected to the engine output shaft (not shown), the to-and-fro motion that it makes connecting rod 09 rotation compression crankshaft 07 and produces compression piston 03.
Figure 17 shows the stereogram of the connecting rod 09 that is connected to corresponding crankshaft 07 and 08, two corresponding crankshafts are connected to respective pistons connecting rod 05 and 06 again, and it is poor that wherein crankshaft 07 and 08 relative to each other is oriented other that piston 03 and 04 are provided the predetermined phase between being synchronized with the movement.The predetermined phase difference mean for realize as shown in Figure 4 the compression piston tdc position and the time difference between the power piston tdc position, can or introduce each piston in advance with relative piston phase delay.Figure 17 show piston brace rod 05 and 06 relative to each other out-phase reach the desired phase delay or in advance of their corresponding tdc positions between the time so that piston 03 and 04 to be provided, in one embodiment, introducing phase delay makes the piston of actuating cylinder move in advance than the piston of compression cylinder a little, the charging of compression can almost be transmitted under whole compression stroke, and make power piston can finish full exhaust stroke.In the U.S. Patent No. 1,372,216 of authorizing Casaday with authorize some advantages of also having described the phase delay of the leading compression piston of power piston among the U.S. Patent application No.2003/0015171 A1 of Scuderi.In another embodiment, introduce opposite phase and postpone to make compression piston move, the wherein power piston charging that also compression comes from compression cylinder before igniting prior to power piston.Authorize people's such as Thurston U.S. Patent No. 3,880,126 and authorize the advantage that this method has been discussed in the U.S. Patent No. 3,959,974 of Thomas.
In a further embodiment, for the rotation of the suitable direction of strengthening compressing crankshaft 07 and power crank axle 08, use the second crankshaft connecting rod 13, as shown in figure 16.
With reference to Figure 18, can be by a crankshaft connecting rod 14 be combined implement another device of the sense of rotation of setting up crankshaft 07 and 08 with timing tape or chain mechanism 15.As shown in figure 19, in another embodiment, chain mechanism or timing tape mechanism 15 can itself as any one alternative form in the above-mentioned crankshaft bindiny mechanism.
Figure 20 and 21 shows another mechanism that substitutes crankshaft connecting rod 09.Figure 20 shows crankshaft connection gear mechanism 30, comprises three gears 32 that are engaged with each other.In this embodiment, two crankshafts 07 and 08 are along one-sided direction rotation (using 3 gears).Figure 21 shows the crankshaft connection gear mechanism 40 of the gear 32 with equal number and two embodiments of 42, is configured to rotating crank axle 07 and 08 in opposite direction thus.
In one embodiment, Aspirating valves 10 is made up of the axle with cone seal surface, and is employed identical with Aspirating valves in most of four stroke engine.When ambient air or carburetted air/fuel oil charging flows into compression cylinder 01 Aspirating valves 10 controls they.Compression cylinder 01 has at least one Aspirating valves.In preferred embodiment, with respect to compression piston 03 instantaneous position, Aspirating valves position, function, timing and operation can be similar or identical with the Aspirating valves of conventional quartastroke engine.
In one embodiment, outlet valve 11 is made up of the axle with cone seal surface, and is employed identical with outlet valve in most of four stroke engine.Be positioned at the gas discharge currents that the outlet valve 11 on the actuating cylinder 02 is controlled after burning.Actuating cylinder 02 has at least one outlet valve.In preferred embodiment, exhaust valve positions, function, timing and operating method can be similar or identical with the outlet valve found in the known conventional quartastroke engine.
Referring to Figure 22, in one embodiment, interstage valve 12 is made up of the axle with cone seal surface.Flow rate from compression cylinder 01 internal volume B during volume C it is pushed into actuating cylinder 02 in of interstage valve control pressurized air stream or compressed boil-off air/fuel charging (this paper is referred to as " fuel oil " or " fuel oil mixture ").Interstage valve 12 prevents that also fuel oil from flowing back to any reverse flow of volume B from volume C.When at open position, interstage valve 12 makes the compression fuel oil flow into actuating cylinder 02 from compression cylinder 01.Burning and during the power stroke interstage valve 12 keep closing.In one embodiment, the interstage valve operating device can be similar or identical with known internal-combustion engine inlet valve or exhaust valve mechanism.The closed or open position of interstage valve 12 is by cooperating with one of dynamic DPCE axle/parts (for example, piston 03) mechanical connection or meshing and operate.It is also understood that valve timing depends on a lot of engineering designs considerations accurately; But as general rule, interstage valve 12 should be opened near 11 shut-in times and keeps closing during power stroke and most of at least exhaust stroke at outlet valve.
Referring to Figure 23, in another embodiment, reloading spring operation relief valve 17 is as interstage valve 12.This embodiment provides without any need for the self-acting valve based on the operating device that links.At air-breathing and expansion stroke, working pressure and reloading spring 16 force valve stem 17 to keep closing and sealing.In compression and exhaust stroke, the exhaust pressure that the compression fuel pressure that increases in the volume B reduces in volume C overcomes valve reloading spring 16 power, and therefore opens valve stem 17, makes the compression fuel oil can flow into actuating cylinder 02 Room C thus.
Figure 24 shows the combination of the semi-automatic interstage valve of firing chamber E and uniqueness, and interstage valve comprises the valve 18 that has around the cylindrical or annular portion of plug valve 19.In this embodiment, firing chamber E is sealed to divide with pressing chamber B by valve 18 and comes and come by valve 19 and acting chamber C sealing branch.Spring 20 promotes two valves 18 and 19 simultaneously towards they corresponding closed positions.Spark plug 21 is positioned at firing chamber E cavity inside.Firing chamber E and interstage valve operation are as follows: shown in stage J, during initial compression and exhaust stroke, spring 20 promotes valve stem 18 and valve stem 19, makes two valves remain on the closed position of sealing.At stage H, along with compression stroke is advanced, its pressurized air/feed pressure rises and in a certain stage, this unlifting pressure acts on the valve 18, overcomes spring 20 preload force, forces valve 18 to be opened thus and pressurized air/charging flows into firing chamber E.At stage G, when compression and acting piston during near their tdc position, the projection 23 of spark plug 21 igniting and power piston 22 mechanically cooperates with valve 19, forces it to move and open valve 19, and it cooperates with valve 18 again and to its closed position promotion valve 18.In addition, the combustion volume pressure of rising and power piston synergy are closed to force valve 18.In stage F, when burning took place, chamber E pressure rose immediately tempestuously, and valve 18 has cut out and the hot burning gas stream propulsion power piston 22 by valve 19 leaves valve 19.
When power piston 22 was recalled (at power stroke), because the pressure reduction that exists between chamber C high combustion pressure and the much lower pressure that exists in being in the chamber B of expiratory phase now, valve 19 stayed open.Firing chamber and interstage valve circulate in when power stroke stops and stop.When power piston 22 its exhaust strokes of beginning, spring 20 back into its closed position with valve 19 then.
Figure 25 shows the DPCE twin cylinder structure that has boosting capability according to one embodiment of the invention.As shown in figure 25, compression cylinder part 50 is bigger than actuating cylinder part 52, therefore makes the air/fuel mixture of big volume can be contained among the pressing chamber B and compression therein.When compression stroke was finished, the pressurized air/fuel oil mixture (i.e. the fuel oil mixture of " supercharging ") of larger volume and boost pressure was injected firing chamber C by interstage valve 12 in the pressing chamber B.Therefore, the firing chamber C that fuel oil mixture relatively large and/or elevated pressures can be injected actuating cylinder 52 to be providing bigger blast in power stroke, and therefore produces more energy and merit.
As mentioned above, Figure 26 shows the DPCE twin cylinder structure that substitutes according to an embodiment of the invention, and wherein compression cylinder 60 is from actuating cylinder 62 skews, so that the minimum heat conduction between two cylinders to be provided.In this embodiment, the little overlapping region of interstage valve 12 between two cylinders.
Figure 27 shows according to another embodiment of the present invention wherein, and two cylinder configuration become to be parallel to each other and two DPCE twin cylinder structures that piston moves in tandem mode.In this embodiment, air-breathing, exhaust and interstage valve can above-mentioned same way as operations.But as shown in figure 27, interstage valve is arranged in the side direction pipeline that connects first and second cylinders.
In alternate embodiment according to the present invention, steam enhancing double piston cycle engine (SE-DPCE) is configured to use the superfluous heat in the firing chamber to convert the water that adds to steam increases engine efficiency and output.As aforesaid DPCE, compression stroke position and power stroke position separated making significantly that higher chamber temperature increase becomes possibility.In this embodiment, above-mentioned DPCE expands the unique annular steam cylinder that also comprises between firing chamber and exhaust passage to.SE-DPCE uses the heat of concentrating on zone between the internal surface of firing chamber and exhaust shell, the exhaust shell is around the coiling of burning bucket cylinder.
According to one embodiment of the invention, Figure 28 shows the sectional view of the SE-DPCE that comprises above-mentioned a lot of similar characteristics: compression cylinder 01, actuating cylinder 02, compression piston 03, power piston 04, two-phase are answered the part of piston connecting rod 05 and 06, compression crankshaft 07, power crank axle 08, crank connecting rod 09, Aspirating valves 10, burning and gas-exhausting valve 11 and interstage valve 12.Compression cylinder 01 is the piston engine cylinder that holds compression piston 03, Aspirating valves 10 and interstage valve 12.Actuating cylinder 02 is the piston engine cylinder that holds the part of power piston 04, outlet valve 11 and interstage valve 12.Actuating cylinder 02 also comprises inner cylinder 02a and outer cylinder 02b.Power piston 04 also comprises double-head piston, and double-head piston also comprises dish type internal piston 04a and annular, outer piston 04b.Actuating cylinder 02 also comprises: be positioned at external impetus cylinder 02b and extend to compression cylinder 01 compressed air valve 16, be positioned at external impetus cylinder 02b steam/air outlet valve 13, comprise the outside exit casing and the heat insulation layer 15 of the outlet pipe 14 of coiling.In one embodiment, actuating cylinder 02,02a and 02b make further to utilize heat energy with highly heat-conductive material.
In a preferred embodiment, compression piston 03 is used for sucking and the compression engine stroke.Internal motivation piston 04a is used for oil inflame power and exhaust (burning back gas) stroke.The hot compressed air that external impetus piston 04b produces extra power and has or do not have steam/water simultaneously by use absorbs the superfluous heat energy of motor and is used for cooling chamber c and power piston 04a.Connecting rod 05 and 06 is connected to their corresponding crankshafts 07 and 08 with compression piston 03 and two power piston 04a and 04b.Compression crankshaft 07 will rotatablely move and convert compression piston 03 to-and-fro motion to.Power crank axle 08 converts inside and outside power piston 04a and 04b to-and-fro motion to the engine revolution output movement.Crankshaft connecting rod 09 converts power crank axle 08 07 rotation of to compression crankshaft.Motor suction valve 10 is made up of the axle with cone seal surface, with employed identical in most of four stroke engine.Outlet valve 11 is made up of the axle with cone seal surface, with employed identical in most of four stroke engine.Interstage valve 12 is made up of the axle with cone seal surface.
Figure 29 shows the sectional block diagram of actuating cylinder 02: be positioned at the spark plug 22 of inner cylinder 02a, the water/steam nozzle/valve 21 that is positioned at the fuel nozzle 20 of inner cylinder 02a and is positioned at outer cylinder 02b.In other embodiments, the SE-DPCE device can use electric starter, high pressure oil lubrication system, controlled water/vapour system with the control water yield, pressure and temperature, known high voltage regularly and spark plug electronics and output shaft flywheel in addition.Burning and gas-exhausting valve 11 comprises the axle with cone seal surface, with use in most of four stroke engine identical.When opening, valve 11 can make the hot gas after the burning discharge the firing chamber and make steam enter exhaust coiling shell 14.Interstage valve 12 is made up of the axle with cone seal surface.When opening, interstage valve 12 makes compression charging (fuel air mixture) push the firing chamber from pressing chamber.Steam/water outlet valve 13 is configured to mechanically open and close.When opening, valve 13 makes the steam water mixture of expansion be released and to be turned back to water supply closed cycle system (not shown) or discharge motor fully from auxilliary power house E discharge by power piston 4b.
Again referring to Figure 28, when two compression pistons 03 and power piston 04 during all at their tdc positions, the available space minimum in the chamber B of cylinder 01.At TDC, cylinder 02a and 02b also have chamber C that their correspondences comprise and the minimum volume among the E.In one embodiment, power crank axle 08 turns clockwise and drives connecting rod 09 motion and compression crankshaft 07 is turned clockwise.Crankshaft 07 and 08 rotary-actuated two- piston 03 and 04 to be to carry out symmetry to-and-fro motion synchronously, and wherein compression piston 03 and power piston 04 inwardly and outwards move in mode uniformly-spaced symmetrically.In alternate embodiment according to the present invention, phase lag or the phase place that can introduce between compression piston 03 and internal motivation piston 04a or external impetus piston 04b or both relative positions shift to an earlier date.
In according to one embodiment of the invention, when compression piston is opened through its TDC and Aspirating valves 10, the SE-DPCE beginning that circulates.Ambient air flows into compression cylinder 01 Room B.07 rotation of compression crankshaft and compression piston 03 motion arrive BDC up to it, close at this Aspirating valves 10.Compression piston 03 its to-and-fro motion of execution is returned to TDC then, causes that air pressure and the temperature in the B of chamber rises.At each predetermined point, interstage valve 12 be connected valve 16 in one or two open.Connection valve 16 makes pressurized air can push the firing chamber C that pressure was lower at that time from the high relatively B of pressure chamber and enters annular air/water/vaporium E.In one embodiment, when compression piston 03 and power piston 04 arrived their TDC, pressurized air was transferred to actuating cylinder 02 basically.At this moment, finish the transfer of pressurized air to actuating cylinder 02, interstage valve 12 and compressed air valve 16 are closed.Fuel oil sprays into chamber C and controlled temperature system by fuel nozzle 20 water sprays into and/or injects chamber E (Figure 29) by bilge injection valve 21.The water of controlled temperature system can valve 12 and 16 finished close before, among or add the E that enters the room afterwards.Burning takes place in spark plug 22 (Figure 29) igniting, and it effectively pushes internal motivation piston 04a to its BDC.Simultaneously, water-spraying in the E of chamber and pressurized air expand and flash to steam, and it increases the pressure in the E of chamber again significantly.The pressure that increases is effectively pushed external impetus piston 04b to BDC.At water during steam-reforming (phase transformation), but the motor superfluous heat that during the C internal combustion of chamber, produces efficiently and the grown place move on to chamber E.
When power piston 04 begins when TDC retracts the SE-DPCE loop termination.Simultaneously, outlet valve 11 is opened, and high-temperature combustion product imports port one 9 from outlet valve 11 and also advancing in the pipeline of outer cylinder 02b coiling and discharging by region D then, and heating cylinder 02 thus.At this moment or near at this moment, outlet valve 11 is opened, steam outlet valve 13 is opened and product (steam, water, the air) recirculation of the previous extraction of chamber E enters the water supply closed cycle system.In one embodiment, steam outlet valve 13 open and the product (steam, water, air) of the previous extraction of chamber E discharge and flow out motor and not with any water or steam recirculation with further energy regeneration.In another embodiment, for conserve energy, the recycled liquid in water and/or steam recirculation and the chamber E can be used for the water-spraying that preheating enters.Before power piston 04 arrived TDC, outlet valve 11 and steam drain 13 were closed once more.When compression piston 03 when its BDC recalls, new circulation begins, and Aspirating valves 10 is opened again.In one embodiment, external impetus cylinder 02 outer perimeter is covered by insulation material layer 15, so that SE-DPCE heat-energy losses minimum.
In one embodiment, as shown in figure 30, piston 04 comprises hot part 30, and it is adjacent with the casing surface of products of combustion and Geng Re and/or directly contact.Hot part 30 is by making as the temperature-resistant material of carbon or pottery.This piston portion only carries longitudinal force.Auxilliary sliding plate 36 is admitted most of slip side-friction force.Part 30 is heating parts of piston 04, and it cools off and lubricate with a spot of water and steam leakage.Part 32 is colder parts and known further coolings and lubricated of piston engine lubricating method of its use of piston 04.Dish 38 separates the colder part 32 of oil lubrication with hot piston steam lubrication part 30.Power connecting rod 06 is connected to power crank axle 08 with piston ear 34.
Figure 31 shows the structure of power piston 04 according to an aspect of the present invention and lubricates.In one embodiment, actuating cylinder 02 and piston 04,04a and the 04b surface that directly cooperates with combustion process is covered with pottery.The ceramic surface of actuating cylinder 02 and piston 04,04a and 04b is water/steam cooling and lubricated.As external impetus piston 04b during near BDC, steam is discharged into zone between power piston 04 and inside and external impetus piston 04a and the 04b by nozzle in a small amount.The power of hot piston portion side is absorbed by additional piston sliding plate 36, and this sliding plate carries most piston side stress and uses known method to carry out oil lubrication.Piston sliding plate 36 will separate around all the other zones in the zone of crankshaft 08 and the actuating cylinder 02 and with its sealing.Therefore, novel cooling of the application of the invention and lubricated aspect, SE-DPCE can move under higher temperature.
Oil content separation disc 36 is accepted most of piston 04 sideslip kinetic force of friction, during the engine crankshaft rotation, makes machine oil can flow to casing surface 48 (between cylinder 02 and the piston 04).In one embodiment, the general seal ring 42 of motor can be installed around the circumference of dish 36.Piston and cylinder slidingsurface 46 and 50 make water and steam as cooling and lubricating fluid, and these materials are discharged cylinder 02 by drain opening 44 then.
Figure 32 shows according to another embodiment of the present invention, and wherein SE-DPCE comprises split type compression piston 03.Compression piston 03 is divided into internal compression piston 03a and external compression piston 03b.Internal compression piston 03a absorbs the ambient air that contains or do not have gasified fuel by Aspirating valves 54, and by interstage valve 12 its compression is entered firing chamber C.External compression piston 03b enters air vapor chamber E by Aspirating valves 10 absorbing environmental air and by connecting Aspirating valves 16 with its compression.In one embodiment, also water is added air-breathing air chamber F and, perhaps alternatively, can water directly be sprayed into chamber E (Figure 29) by water spray 21 then by connecting Aspirating valves 16 with its compression inlet chamber E.The compression piston structure of division makes motor can utilize the gasified fuel of suction chamber G.In addition, the compression piston of division and chamber structure makes SE-DPCE can be designed so that total air divided and can independently determine each chamber F and G by volume between chamber F and G volume that enters.
Figure 33 shows according to another embodiment of the present invention, and wherein SE-DPCE comprises two dynamic force generating units that separate, and wherein main combusting system uses the Fuel Air combustion process, and auxilliary water-steam-air system is used superfluous motor heat energy.In this embodiment, main combusting system comprises compression piston 03a, power piston 04a, Aspirating valves 54, outlet valve 11, interstage valve 12 and output shaft 08.In one embodiment, the waste gas input cylinder from outlet valve 11 heats port 19 with heating cylinder 02b, as mentioned above.Auxilliary water-steam-air system comprises compression piston 03b, power piston 04b, Aspirating valves 10, interstage valve 16, steam/air outlet valve 13 and auxilliary pto 60.Main combusting system changes into the motor merit with fuel oil and air, as mentioned above.Auxilliary water-steam in one embodiment-air system is used identical with main combusting system basically reciprocating motion of the pistons, connecting rod motion and crankshaft rotation.But in auxilliary water-steam-air system, the air of heating, water and/or steam can be used for producing the motor merit.Each power generation systems activates the operating valve of himself.In one embodiment, main combusting system activated valve 54,12 and 11 and optional fuel injection system.In this embodiment, auxilliary system activation valve 16 and 13 and activate alternatively hydroecium E direct injection system (nozzle 24, Figure 29).Based on the above discussion, in certain embodiments, main compression piston 03a is configured to make them arrive their tdc position at different time with different phase difference operations with active force piston 04a.Similarly, auxilliary compression piston 03b and auxilliary power piston 04b also can be configured to relative to each other move with a phase difference.
In one embodiment, SE-DPCE uses following power unit, and they are used for auxilliary power output (compression and power piston motion, they use engine thermal to produce extra engine power output).Auxilliary power output comprises two pistons, two compression connecting rods 70, compression crankshaft 68, power crank axle 60, power crank axle connecting rod 64 and crankshaft connecting rod 66, and wherein two pistons comprise ring compression piston 03b and ring output piston 04b.Connecting rod is connected to respective pistons on their corresponding crankshafts.Compression crankshaft 68 will rotatablely move and convert the to-and-fro motion of compression ring piston 03b to.Outputting power crankshaft 60 converts outputting power ring piston 04b to-and-fro motion to auxilliary output 60 and rotatablely moves.Crankshaft connecting rod 66 will use the outputting power crankshaft 60 of crankshaft 62 to convert 68 rotations of compression crankshaft to.
In one embodiment, between main shaft 08 and auxilliary axle 60, there is not engine interior to cooperate.In this embodiment, each system is independently, and power of each and speed depend on engine behavior and motor input parameter.In another embodiment, SE-DPCE can accept gasified fuel/air feed and carry out the fuel-injecting method that burns.And, in another other embodiment, the air that SE-DPCE can accept empty G﹠W and enter along with the water-spraying that directly sprays in the E of chamber.In according to another embodiment of the present invention, SE-DPCE uses electronic optimization supervisory computer (not shown), its monitoring engine temperature, RPM, engine torque, fuel consume, water-spraying temperature and the water yield.These motor physical parameters miscellaneous of Computer Analysis are correspondingly regulated the injection water yield, temperature and the injected fuel amount that is used for optimum performance.
In various other embodiments according to the present invention, SE-DPCE can have any several in several supplementary features.In one embodiment, water-vaporium E water and/or steam replace pressurized air to operate.When piston arrives TDC, water and/or steam are injected chamber E.Burning piston 03 is only transferred to pressurized air in the C of chamber by interstage valve 12.The function of above-mentioned water cooling and generation merit is carried out with the phase transformation that becomes steam that sprays into the water in the E of chamber and follow.During piston-retraction, when piston was shifted to TDC, chamber E steam and/or water were discharged by steam/air expulsion valve 13.In another embodiment, can be with steam heating to higher temperature to obtain better engine performance.
In another alternate embodiment, water and/or steam can be with another kind of liquid or gas instead, such as ammoniacal liquor, freon, ethanol or any other suitable inflatable liquid (comprising gaseous state).
In another embodiment, only pressurized air rather than water or steam are sprayed into chamber E.
In another embodiment, ebullator layer 71 comprises and is used for fluid and/or gas are remained on wherein a plurality of passages 71 that wherein ebullator layer 71 is around at least a portion coiling of burning chamber shell 02.As shown in figure 34, in one embodiment, ebullator layer/passage 71 is centered on by the passage 14 of the outlet pipe 14 of coiling, and the both is centered on by heat insulation layer/thermal-protective coating 15.Only should be appreciated that for purpose of illustration passage 71 and 14 sectional view are shown as square and circular.In reality is implemented, can use the shape of any requirement to these passages.In another embodiment, passage 71 and/or passage 14 can respectively be configured to fluid and/or gas are remained on wherein single than major path or raceway groove around the burning chamber shell coiling.In one embodiment, pressurized water or other the suitable fluid from the external source (not shown) can be pressed into ebullator passage 71 via entry end 72 by the oil hydraulic pump (not shown).Since firing chamber C, cylinder 02 and inner disk around exhaust level 14 temperature very high, any water (or any other liquid) that flows into or spray into entry end 72 can be transformed into high pressure steam rapidly.In one embodiment, then high pressure steam is guided to outside steam piston motor (not shown) or steam turbine (not shown) from steam outlet 74, it can convert steam to extra useful mechanical work, such as rotating generator or mechanically cooperate SE-DPCE main output shaft 08.Heat insulation layer 15 remains on most of SE-DPCE heat energy in the engine structure.When its exhaust stroke of power piston 04 beginning, hot combustion gas flows into inlet exhausts coiling mouthfuls 19 by outlet valve 11, heat thus inner disk around exhaust level 14.After the part of their heat energy was transferred to water/steam coil pipe 14, waste gas was discharged from motor by delivery outlet D.
By implementing said method and device, SE-DPCE embodiment produces and utilizes the steam energy by using previous untapped heat energy.The steam of Chan Shenging can be used to produce extra mechanical work then.In one embodiment, steam can be used by auxiliary steam motor or steam turbine, and it can change into extra power with steam then.
Also have the air-breathing and compression piston of motor wherein with burning with discharge other embodiment that temperatures involved physics separates, as when reading this specification to those skilled in the art conspicuous.Although illustrated and described various embodiment of the present invention, those skilled in the art will appreciate that each embodiment's above explanation only is exemplary and the present invention can and change form with the change of said apparatus and technology and puts into practice.Those skilled in the art can up to, or only be to use routine test just can determine the multiple equivalent form of value of the specific embodiment of invention described herein.This change, change and coordinate have been considered in the spirit and scope of the present invention of in following claims, setting forth.
Claims (26)
1. double-piston device that is used for internal-combustion engine comprises:
First cylinder accommodates first piston therein, and wherein said first piston is only carried out air-breathing and compression stroke;
Second cylinder accommodates second piston therein, and wherein said second piston is only carried out power and exhaust stroke;
The 3rd piston also is contained in described second cylinder and with described second piston and connects, and wherein said the 3rd piston utilization is carried out extra power stroke by the heat energy that described second piston produces.
2. device as claimed in claim 1 is characterized in that:
Described second piston comprises dish type internal-combustion piston, and described dish type internal-combustion piston comprises lateral cylindrical side and forms the first interior interior chamber of described second cylinder; And
Described the 3rd piston comprises the annular, outer power piston, and described power piston centers on the lateral cylindrical side of described second piston and forms the second interior interior chamber of described second cylinder, and wherein said second interior chamber is to small part around described first interior chamber.
3. device as claimed in claim 1 is characterized in that, described first cylinder is relative second cylinder adiabatic, and described first cylinder remains on than the lower temperature of described second cylinder when operation.
4. device as claimed in claim 1 is characterized in that, also comprises:
Aspirating valves is connected to described first cylinder so that fuel oil mixture enters described first cylinder;
The burning and gas-exhausting valve is connected to described first interior chamber of described second cylinder so that waste gas can be discharged described second cylinder; And
Interstage valve is connected to the interior chamber of described first cylinder described first interior chamber of described second cylinder.
5. device as claimed in claim 1 is characterized in that, also comprises:
Aspirating valves is connected to described first cylinder so that fuel oil mixture can enter described first cylinder;
Connect valve, the interior chamber of described first cylinder is connected to described second interior chamber of described second cylinder, described second interior chamber of described second cylinder transferred to pressurized air, liquid or gas by wherein said connection valve; And
Outlet valve is connected to described second interior chamber of described second cylinder, so that the air of certain volume, liquid or gas can be discharged described second interior chamber of described second cylinder.
6. device as claimed in claim 5 is characterized in that, comprises that also described second interior chamber that is connected to described second cylinder is to spray into liquid or gas at the nozzle of described second interior chamber of described second cylinder.
7. device as claimed in claim 1 is characterized in that, also comprises:
Aspirating valves is connected to described first cylinder so that fuel oil mixture can enter described first cylinder;
Nozzle is connected to described second interior chamber of described second cylinder, liquid or gas are sprayed into described second interior chamber of described second cylinder; And
Outlet valve is connected to described second interior chamber of described second cylinder, so that liquid or gas can be discharged described second interior chamber of described second cylinder.
8. device as claimed in claim 7 is characterized in that described liquid or gas comprise water or steam respectively.
9. device as claimed in claim 8 is characterized in that, the liquid of described injection or gas comprise at least a in water, steam, ammoniacal liquor, freon or the ethanol.
10. device as claimed in claim 1 is characterized in that, also comprises the outside exit casing on the described outer surface that is arranged on described second cylinder casing, and wherein said outside exit casing is configured to described second cylinder is remained on the temperature of rising.
11. device as claimed in claim 10 is characterized in that, described outside exit casing comprises:
Heat insulation layer; And
The outlet pipe of coiling, the outlet pipe of wherein said coiling is around the described outer surface coiling of described second cylinder casing, and also comprises and be used to utilize further a plurality of waste heating passages of described second cylinder of heating of heat that the waste gas of being discharged by described second piston provides.
12. device as claimed in claim 11 is characterized in that, also comprises:
The ebullator layer, the described outer surface around described second cylinder casing below the outlet pipe of described coiling coils; And
Entry end is connected to described ebullator layer, so that fluid can enter the ebullator layer, wherein said fluid is owing to the temperature that raises changes into gas.
13. device as claimed in claim 1 is characterized in that, also comprises the ebullator layer of the housing that is connected to described second cylinder, is used for owing to the temperature of described second cylinder casing rising fluid being changed into gas.
14. a double-piston device that is used for internal-combustion engine comprises:
First cylinder accommodates first piston therein, and wherein said first piston is only carried out air-breathing and compression stroke, and wherein said first piston comprises:
Dish type internal compression piston forms the inboard interior chamber of described first cylinder;
The annular, outer compression piston is connected to and around described dish type internal compression piston, wherein said external compression piston forms the outside interior chamber of described first cylinder; And
Second cylinder accommodates second piston therein, and wherein said second piston is only carried out power and exhaust stroke.
15. device as claimed in claim 14 is characterized in that, described second piston comprises:
Dish type internal-combustion piston forms the inboard interior chamber of described second cylinder; And
The annular, outer power piston is connected to and around described dish type internal-combustion piston, wherein said external impetus piston forms the outside interior chamber of described second cylinder.
16. device as claimed in claim 15 is characterized in that, also comprises:
Aspirating valves is connected to described first cylinder so that fuel oil mixture can enter described first cylinder;
The burning and gas-exhausting valve is connected to the described inboard interior chamber of described second cylinder, so that waste gas can be discharged described second cylinder; And
Interstage valve is connected to the described inboard interior chamber of described first cylinder described inboard interior chamber of described second cylinder.
17. device as claimed in claim 15 is characterized in that, also comprises:
Aspirating valves is connected to described first cylinder, so that fuel oil mixture can enter described first cylinder;
Connect valve, the described outside interior chamber of described first cylinder is connected to the described outside interior chamber of described second cylinder, wherein said connection valve will comprise that a constant volume at least a in gas or the liquid transfers to the described outside interior chamber of described second cylinder; And
Outlet valve is connected to the described outside interior chamber of described second cylinder, so that the gas of a constant volume can be discharged the outside interior chamber of described second cylinder.
18. device as claimed in claim 15 is characterized in that, the volume of the outside of the described outside interior chamber of described first cylinder is different with the volume of the described inboard interior chamber of described first cylinder.
19. device as claimed in claim 14 is characterized in that, also comprises the ebullator layer, is connected to described second cylinder casing, is used for owing to the temperature of described second cylinder casing rising fluid being changed into gas.
20. a double-piston device that is used for internal-combustion engine comprises:
First cylinder, hold dish type internal compression piston and annular, outer compression piston, wherein said inside and outside compression piston is only carried out air-breathing and compression stroke, and wherein said internal compression piston forms the inboard interior chamber of described first cylinder, and described external compression piston forms the outside interior chamber of described first cylinder; And
Second cylinder, hold dish type internal-combustion piston and annular, outer power piston, wherein said internal-combustion piston and external impetus piston are only carried out power and exhaust stroke, and wherein said internal-combustion piston forms first interior chamber of described second cylinder, and described external impetus piston forms second interior chamber of described second cylinder.
21. device as claimed in claim 20 is characterized in that, also comprises:
The first main crank axle is connected to described internal compression piston;
The second main crank axle is connected to described internal-combustion piston; And
The main crank shaft connection mechanism is connected on the described first and second main crank axles and is configured to transmitting movement between the described first and second main crank axles.
22. device as claimed in claim 21 is characterized in that, also comprises:
The first auxilliary crankshaft is connected to described external compression piston;
The second auxilliary crankshaft is connected to described external impetus piston; And
Auxilliary crankshaft coupling mechanism, the transmitting movement that is connected on the described first and second auxilliary crankshafts and is configured to assist between the crankshafts described first and second.
23. device as claimed in claim 22 is characterized in that, the described second auxilliary crankshaft is with the speed motion different with the described second main crank axle.
24. device as claimed in claim 22 is characterized in that, the described first and second auxilliary crankshafts are configured to provide the phase difference between described external compression piston and the described external impetus piston.
25. device as claimed in claim 21 is characterized in that, the described first and second main crank reel structures become to provide the phase difference between described internal compression piston and the described internal-combustion piston.
26. device as claimed in claim 20 is characterized in that, also comprises the ebullator layer, this ebullator layer is connected to described second cylinder casing, is used for owing to the temperature of described second cylinder casing rising fluid being changed into gas.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US67242105P | 2005-04-18 | 2005-04-18 | |
| US60/672,421 | 2005-04-18 | ||
| US11/371,827 | 2006-03-09 |
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| CN101253316A true CN101253316A (en) | 2008-08-27 |
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| CNA2006800184102A Pending CN101253316A (en) | 2005-04-18 | 2006-04-18 | Steam enhanced double piston cycle engine |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104302886A (en) * | 2011-11-30 | 2015-01-21 | 托尔发动机股份有限公司 | Crossover valve in double piston cycle engine |
| CN110966091A (en) * | 2019-02-02 | 2020-04-07 | 烟台小米机械技术有限公司 | Engine capable of realizing constant volume combustion and working method thereof |
| CN111601962A (en) * | 2018-02-05 | 2020-08-28 | 宝马股份公司 | Otto internal combustion engine with urea supply and method for operating such an internal combustion engine |
| CN113389611A (en) * | 2020-03-12 | 2021-09-14 | 赵天安 | Air inlet adjusting mechanism, engine and pneumatic motor |
-
2006
- 2006-04-18 CN CNA2006800184102A patent/CN101253316A/en active Pending
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104302886A (en) * | 2011-11-30 | 2015-01-21 | 托尔发动机股份有限公司 | Crossover valve in double piston cycle engine |
| US9689307B2 (en) | 2011-11-30 | 2017-06-27 | Tour Engine, Inc. | Crossover valve in double piston cycle engine |
| CN111601962A (en) * | 2018-02-05 | 2020-08-28 | 宝马股份公司 | Otto internal combustion engine with urea supply and method for operating such an internal combustion engine |
| US11111884B2 (en) | 2018-02-05 | 2021-09-07 | Bayerische Motoren Werke Aktiengesellschaft | Spark-ignition internal combustion engine having urea introduction device and method for operating an internal combustion engine of this type |
| CN111601962B (en) * | 2018-02-05 | 2022-06-21 | 宝马股份公司 | Otto internal combustion engine with urea supply and method for operating such an internal combustion engine |
| CN110966091A (en) * | 2019-02-02 | 2020-04-07 | 烟台小米机械技术有限公司 | Engine capable of realizing constant volume combustion and working method thereof |
| CN113389611A (en) * | 2020-03-12 | 2021-09-14 | 赵天安 | Air inlet adjusting mechanism, engine and pneumatic motor |
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