CN103291449A - Internal combustion engine - Google Patents
Internal combustion engine Download PDFInfo
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- CN103291449A CN103291449A CN2013100606619A CN201310060661A CN103291449A CN 103291449 A CN103291449 A CN 103291449A CN 2013100606619 A CN2013100606619 A CN 2013100606619A CN 201310060661 A CN201310060661 A CN 201310060661A CN 103291449 A CN103291449 A CN 103291449A
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Abstract
The invention discloses an internal combustion engine which comprises an engine consisting of a first air cylinder assembly and a second air cylinder assembly which are arranged in a contrapositive manner, wherein the first air cylinder assembly and the second air cylinder assembly are arranged in a housing; the first air cylinder assembly mainly comprises a first cylinder sleeve which comprises a first air cylinder cavity and is arranged in the first air cylinder cavity; the second air cylinder assembly mainly comprises a second cylinder sleeve which comprises a second air cylinder cavity and is arranged in the second air cylinder cavity; a crankshaft is arranged between the first air cylinder assembly and the second air cylinder assembly; and the first cylinder sleeve and the second cylinder sleeve are provided with air inlets and air outlets respectively. The internal combustion engine has the benefits that the internal combustion engine is light in weight, convenient to mount, simple in mechanical structure and low in cost; the efficiency is improved; the height of the complete internal combustion engine is low; and dynamic balance is reached wholly and basically.
Description
Technical field
The present invention relates to power equipment, be specifically related to a kind of internal-combustion engine.
Background technique
Automobile and light airplane industry are relatively advanced technical fields with design and the manufacturing of internal-combustion engine.For the coml feasibility; any new engine configurations must be under the prerequisite of not sacrificing performance, pollutes, guarantees that in the energy and conservation of raw material (the particularly improvement of fuel consumption), protection environment and control passenger's safety and comfortable, competitive design and the mode of production also must significantly improve to reduce aspects such as cost and weight.With sacrifice other side obtain wherein on the one hand improvement commercial be infeasible.
In occupation of leading position, the in-line four cylinder configuration is common type to present quartastroke engine in automobile-used market.Four cylinder engine is the demand that produces in order to reach the expansion stroke output-index that is consistent with it, has determined size and the profile of motor; Therefore also limited the Designer in the selection that motor is placed on the vehicle simultaneously.These cylinders are less, and are normally disadvantageous for the minimizing of efficient burning and original discharging.In addition, free inertial force exists because the in-line four cylinder machine has tangible imbalance, causes its noise and vibration bigger, thereby passenger comfort is also had adverse effect.
For a long time, engine designer has realized that two stroke engine has important potential advantages with respect to four stroke engine.On two stroke engine, bent axle whenever revolves and turns around, and each cylinder acting once.With respect to the four stroke engine of identical acting output-index, two stroke engine only needs the cylinder of half quantity to get final product.Number of cylinders still less makes that engine mechanical is simple in structure and volume is littler.Two stroke engine itself has more simple and mechanical structure with respect to four stroke engine, and reason is that the mechanical structure of opening and closing porting can be simpler.
Yet two stroke engine has been limited use because of several shortcomings that can perceive.There is weakness (for example, charging efficiency is lower) in two stroke engine with respect to four stroke engine aspect the mean effective pressure.Because the very big a part of pressure in each stroke must be used for clearing away products of combustion and the combustion air supply (scavenging) of an expansion stroke, so this part pressure will lose from expansion stroke.Itself also has problems scavenging, particularly when engine running is in a wide in range speed and load range.As everyone knows, two-stroke compression ignition internal combustion engine (diesel engine) also has other shortcoming, comprises relatively poor startability and higher particulate emission.
Modern supercharging technology can overcome a lot of previous narrow limitation relevant with two stroke engine with the fuel oil spraying technique, and making two cylinder two-stroke motors can substitute the four cylinder four-stroke motor becomes possibility.Two cylinder two-stroke motors have identical spark rate with the four cylinder four-stroke motor.If two stroke engine provides the mean effective pressure that is equivalent to four stroke engine 2/3, and bring up at the effective discharge of each cylinder of two stroke engine under 3/2 the situation of four stroke engine, two stroke engine will produce (with four-stroke) similarly power output so.The two stroke engine cylinder still less, but combustion volume is bigger, is favourable for improving combustion efficiency and reducing original discharging.Two stroke engine can also be exempted the valve on the four stroke engine, also has greater flexibility aspect its Combustion chamber design like this.
Now known the important root of the engine friction loss of current production; The efficient that improves motor can realize by reducing these frictional losses.Maximum friction on the engine for automobile of current production loss root is that the connecting rod of rotation is applied to lateral force on the piston and promotes piston and be adjacent to cylinder wall and produce, and accounts for about half of frictional loss total amount.The size of these losses is and the ratio of crank throw r divided by length of connecting rod l, is referred to as λ usually, and is relevant.By increasing the connecting rod effective length or reducing crank throw, all can reach the effect of the loss of significantly reducing friction.
Piston (piston ring of perhaps saying so more accurately) is relevant with respect to the average movement velocity of cylinder wall with piston with the frictional loss that the cylinder wall contact produces equally.When keeping equal-wattage output, if the speed of piston can slow down, frictional loss will reduce.
The important frictional loss root of on the motor of current production another is the bigger power that acts on the crankshaft main bearing.Typical four-in-line engine has five crankshaft main bearings.Because there is the firing pressure of tons of to act on the bent axle, these power must be transferred on the supporting structure of motor, so five main journals are necessary.The supporting structure of bent axle and motor must be designed to have enough big intensity, and (with corresponding weight) bears these loads.
Chinese patent CN1710254A discloses a kind of novel two stroke opposed type internal-combustion engines, its two-piston is contained in the two ends of a connecting rod respectively, the middle part is provided with the fuel feed pump plunger that is driven by connecting rod by internal combustion engine in the machine, the heat energy that fuel combustion produces can be converted into the hydraulic pressure energy during work, adopt the fluid motor-driven vehicle to exercise.Establish in its hydraulic system for oil cylinder and three gas holder of realizing that hydraulic pressure and air pressure can be changed; Be used for recovery section deceleration, braking energy, and the portion of energy in the internal-combustion engine combustion gas can be converted into useful work.Compare with traditional combustion engine during work and can reduce fuel consumption greatly, reduce exhaust emissions.There is tangible difference in the crankshaft structure that the fuel feed pump plunger of this patent and the present application have, does not also reach and improves the complete machine height, alleviates the technique effect of quality etc.
Chinese patent CN1555456A discloses a kind of motor, particularly, and internal-combustion engine.The objective of the invention is, improve efficient and the power of motor, simplify the structural design of motor, reduce the outside dimensions of motor, reduce load and the specific weight of movement conversion mechanism in essence, and improve the ecological characteristic of motor influence.This internal-combustion engine comprises at least one cylinder, and this cylinder has the piston of two opposed motions, and is placed in bent axle wherein.Described piston has connecting rod.Piston motion is converted to the mechanism that rotatablely moves of bent axle, the rocking bar that provides according to number of pistons is provided.The connecting rod of piston is connected to first rocker arm, and this connecting rod is pivotally connected to second rocker arm respectively.Two opposed connecting rods are arranged to two cross one another planes respectively, and described plane is perpendicular to the crankshaft rotating plane.This connecting rod is by following layout, and the piston that connects when one of them connecting rod is located thereon or during bottom dead center position, the piston that another connecting rod connects is not located thereon or bottom dead center position.There are obviously difference in suction port among this patent and the application and the structure of relief opening and location arrangements, and overall structure also is different from the application's integral structure.
Summary of the invention
The problems referred to above at existing internal-combustion engine exists the invention provides a kind of internal-combustion engine that can raise the efficiency and simplify mechanical structure.
The technological scheme that the present invention adopts for achieving the above object is:
A kind of internal-combustion engine, comprise the motor of being formed by first cylinder assembly and second cylinder assembly of opposed layout, described first cylinder assembly and described second cylinder assembly are located in the same housing, described first cylinder assembly mainly is made up of the first cylinder die cavity and first cylinder sleeve be located in the described first cylinder die cavity, described second cylinder assembly mainly is made up of the second cylinder die cavity and second cylinder sleeve be located in the described second cylinder die cavity, be furnished with bent axle between described first cylinder assembly and described second cylinder assembly, opposed first inner carrier and first outer piston of being laid with in described first cylinder sleeve, opposed second inner carrier and second outer piston of being laid with in described second cylinder sleeve, described first inner carrier and described second inner carrier are connected on the same axle journal of described bent axle by first push rod and second push rod respectively, described first outer piston is connected with described bent axle with second pull bar by first pull bar respectively with described second outer piston, and described first cylinder sleeve and described second cylinder sleeve are provided with suction port and relief opening respectively.
Above-mentioned internal-combustion engine, wherein, described relief opening is arranged in an end of described first cylinder sleeve and described second cylinder sleeve respectively, described suction port is arranged in the other end of described first cylinder sleeve and described second cylinder sleeve respectively, the layout of described axle journal makes in same cylinder, the described relief opening of motion opening and closing of another piston in the time of the described suction port of the motion opening and closing of a piston.
Above-mentioned internal-combustion engine, wherein, described first cylinder sleeve and described second cylinder sleeve are provided with drive unit, and described drive unit is in order to regulate moving axially of described first cylinder sleeve and described second cylinder sleeve.
Above-mentioned internal-combustion engine, wherein, the location arrangements of described first cylinder sleeve, described second cylinder sleeve, described suction port and described relief opening makes described first cylinder sleeve and described second cylinder sleeve be moved in the second place process by primary importance towards described bent axle, has shortened by opening time of the described suction port of described first inner carrier and second inner carrier control or described relief opening and has increased by described first outer piston and the described suction port of described second outer piston control or the opening time of described relief opening.
Above-mentioned internal-combustion engine, wherein, described drive unit comprises a hydraulic actuator, described hydraulic actuator makes hydrodynamic pressure be transferred to the part cylinder sleeve.
Above-mentioned internal-combustion engine, wherein, when described internal-combustion engine was in a predetermined speed, described first cylinder sleeve and described second cylinder sleeve were positioned at described primary importance, when described internal-combustion engine was in the speed that is lower than described predetermined speed, described first cylinder sleeve and described second cylinder sleeve were positioned at the described second place.
Owing to adopted said mechanism and method, the good effect that technique scheme compared with prior art has is: efficient improves, and the complete machine height is low, and is in light weight, is convenient to install, and integral body reaches transient equiliblium substantially and mechanical structure is simple, and cost is low.
Description of drawings
Fig. 1 is the part section normal axomometric drawing of a kind of internal-combustion engine of the present invention;
Fig. 2 is the vertical view cutaway drawing of first cylinder of internal-combustion engine shown in Fig. 1 when being positioned at top dead center;
Fig. 3 is the vertical view cutaway drawing of first cylinder of internal-combustion engine shown in Fig. 1 when being positioned at lower dead center;
Fig. 4 is the side view cutaway drawing of first cylinder of internal-combustion engine shown in Fig. 1;
Fig. 5 is first side view cutaway drawing of first cylinder sleeve of partial combustion chamber of first cylinder of internal-combustion engine shown in Fig. 1;
Fig. 6 is along the sectional view of 6A-6A line among Fig. 5;
Fig. 7 is along the sectional view of 6B-6B line among Fig. 5;
Fig. 8 is second side view cutaway drawing of first cylinder sleeve of partial combustion chamber of first cylinder of internal-combustion engine shown in Fig. 1;
Fig. 9 is along the sectional view of 7B-7B line among Fig. 8;
Figure 10 be internal-combustion engine shown in Fig. 1 symmetrical distribution suction port and exhaust open and when closing about the functional arrangement of crank angle;
Figure 11 be asymmetrically distributed suction port and the exhaust open of internal-combustion engine shown in Fig. 1 and when closing about the functional arrangement of crank angle;
Figure 12 is second embodiment's of internal-combustion engine shown in Fig. 1 the side view cutaway drawing when crank angle is 270 °;
Figure 13 is that the suction port of internal-combustion engine shown in Fig. 1 and exhaust open and the asymmetric timing of closing are about the functional arrangement of crank angle;
Figure 14 is the side view cutaway drawing in piston linear when motion of internal-combustion engine shown in Fig. 1;
Figure 15 is the side view cutaway drawing of first cylinder of internal-combustion engine shown in Fig. 1 when being positioned at top dead center;
When Figure 16 is first cylinder piston configuration Intermittent Contact formula ignition system of internal-combustion engine shown in Fig. 1 and the partial sectional view of this system when not working;
When Figure 17 is first cylinder piston configuration Intermittent Contact formula ignition system of internal-combustion engine shown in Fig. 1 and the partial sectional view during this system works;
Partial sectional view when Figure 18 is first cylinder piston configuration sliding contact formula ignition system of internal-combustion engine shown in Fig. 1;
Figure 19 is first embodiment's the side view cutaway drawing of the first outer piston head of internal-combustion engine shown in Fig. 1;
Figure 20 is second embodiment's the side view cutaway drawing of the first outer piston head of internal-combustion engine shown in Fig. 1;
Figure 21 is the 3rd embodiment's the side view cutaway drawing of the first outer piston head of internal-combustion engine shown in Fig. 1;
Figure 22 is the blast top plan view of bent axle, pull bar and the push rod of internal-combustion engine shown in Fig. 1;
Figure 23 is the assembling plan view of bent axle, pull bar and the push rod of internal-combustion engine shown in Fig. 1;
Figure 24 be internal-combustion engine shown in Fig. 1 push rod, crankshaft component and rolling bearing etc. axle survey the blast sectional view;
Figure 25 is the bent axle assembling normal axomometric drawing of internal-combustion engine shown in Fig. 1;
Figure 26 is the isometric cutaway views such as bent axle assembling of internal-combustion engine shown in Fig. 1;
Figure 27 is that the 3rd embodiment's of internal-combustion engine shown in Fig. 1 the axle that waits is surveyed partial sectional view;
Figure 28 is the partial sectional view of the balance sysmte of internal-combustion engine shown in Fig. 1;
Figure 29 is along the sectional view of 23-23 line among Fig. 3;
Figure 30 is the schematic diagram of overlooking of internal-combustion engine shown in Fig. 1;
Figure 31 is first embodiment's of internal-combustion engine shown in Fig. 1 forward sight schematic diagram;
Figure 32 is second embodiment's of internal-combustion engine shown in Fig. 1 forward sight schematic diagram.
Embodiment
The invention will be further described below in conjunction with the drawings and specific embodiments, but not as restriction of the present invention.
A kind of internal-combustion engine of the present invention as Figure 1-3, comprise the motor of being formed by first cylinder assembly 100 and second cylinder assembly 200 of opposed layout 10, first cylinder assembly 100 and second cylinder assembly 200 are located in the same housing 103, first cylinder assembly 100 mainly is made up of first cylinder sleeve 130 that contains the first cylinder die cavity 104 and be located in the first cylinder die cavity 104, second cylinder assembly 200 mainly is made up of second cylinder sleeve 230 that contains the second cylinder die cavity 204 and be located in the second cylinder die cavity 204, be furnished with bent axle 300 between first cylinder assembly 100 and second cylinder assembly 200, opposed first inner carrier 120 and first outer piston 110 of being laid with in first cylinder sleeve 130, opposed second inner carrier 220 and second outer piston 210 of being laid with in second cylinder sleeve 230, first inner carrier 120 and second inner carrier 220 are connected on the same axle journal of bent axle 300 by first push rod 412 and second push rod 422 respectively, first outer piston 110 is connected with bent axle 300 with second pull bar 421 by first pull bar 411 respectively with second outer piston 210, and first cylinder sleeve 130 and second cylinder sleeve 230 are provided with suction port 161 respectively, suction port 261 and relief opening 163, relief opening 263.
Further, first cylinder assembly 100 is made up of first cylinder sleeve, 130, the first outer pistons 110 and first inner carrier 120.First inner surface of cylinder liner 139 that first cylinder sleeve 130 comprises first liner backs 132 and defined by a hole.First cylinder sleeve 130 also comprises an air inlet port 136 and exhaust port 138, and air inlet port 136 comprises several left sides suction port 161, and exhaust port 138 comprises several relief openings 163.
Further, first outer piston 110 is made up of with first outer piston head, 116 relative slide blocks 118 first outer piston head 116.Piston combustion face 111 is the boundary beyond first outer piston head 116.First outer piston head 116 and first inner surface of cylinder liner 139 slide at air inlet port 136 places and closely cooperate.First inner carrier 120 comprises first piston head 126 and the slide block 124 relative with first piston head 126.First piston head 126 is the boundary with inner carrier combustion surface 121.First piston head 126 and first inner surface of cylinder liner 139 slide at exhaust port 138 places and closely cooperate.First outer piston 110, first inner carrier 120 and first cylinder sleeve 130 have defined first firing chamber 150 jointly.
Further, second cylinder assembly 200 is made up of second cylinder sleeve, 230, the second outer pistons 210 and second inner carrier 220.Second inner surface of cylinder liner 239 that second cylinder sleeve 230 comprises second liner backs 232 and defined by a hole.Second cylinder sleeve 230 also comprises an air inlet port 236 and exhaust port 238, and air inlet port 236 comprises several right sides suction port 261, and exhaust port 238 comprises several right sides relief opening 263.
Further, second outer piston 210 is made up of with second outer piston head, 216 relative slide blocks 218 second outer piston head 216.Piston combustion face 211 is the boundary beyond second outer piston head 216.Second outer piston head 216 and second inner surface of cylinder liner 239 slide at air inlet port 236 places and closely cooperate.It is the boundary with inner carrier combustion surface 221 that second inner carrier 220 comprises second piston head 226 slide block 224, the second piston head 226 relative with second piston head 226.Second piston head 226 and second inner surface of cylinder liner 239 slide at exhaust port 238 places and closely cooperate.Second outer piston 210, second inner carrier 220 and second cylinder sleeve 230 have defined second firing chamber 250 jointly.
Further, first outer piston 110 and second outer piston 210 are connected on the bent axle 300 on one group of public axle journal 311.First outer piston 110 links to each other with bent axle 300 by one group of first pull bar 411, links to each other with first cylinder sleeve 130 at the other end.Similarly, second outer piston 210 links to each other with bent axle 300 by two second pull bars 421.Because first pull bar 411 and second pull bar 421 be tension power effect usually in motor 10 operation process, and when starting, only bears by motor 10 a little compression force, therefore the following further explanation of picture is said, and their thickness can be thinner relatively, thereby realized lightweight.The length of first pull bar 411 and second pull bar 421 is long for radius of crankshaft.This helps to reduce the frictional loss of motor 10.
Further, first pull bar 411 is connected with second outer piston 210 with first outer piston 110 with the second bridge connection structure 270 by the first bridge connection structure 170 respectively with second pull bar 421.The first bridge connection structure 170 and the second bridge connection structure 270 comprise a concave arc surface 173, and the convex globoidal 172 on concave arc surface 173 and first outer piston 110 is slidingly matched.
Further, first inner carrier 120 and second inner carrier 220 are connected on the same axle journal 312.During motor 10 ran well, first push rod 412 and second push rod 422 were always located under pressure.First inner carrier 120 in first cylinder sleeve 130 relies on first push rod 412 to link to each other with bent axle 300.Second inner carrier 220 in second cylinder sleeve 230 relies on second push rod 422 to link to each other with bent axle 300.The first recessed end 413 and the second recessed end 423 are arranged respectively on first push rod 412 and second push rod 422.The first recessed end 413 and the second recessed end 423 are respectively on first crowning 125 and second crowning 225 of the first thrust end 124 of first inner carrier 120 and second inner carrier 220 and the second thrust end 224.The purpose of An Paiing is the effective length that increases push rod like this, reduces frictional loss, thereby helps the transient equiliblium of motor 10.
Further, on first outer piston 110, first inner carrier 120, second outer piston 210 and second inner carrier, 220 these four pistons the first outer piston ring 112, the first inner carrier ring 122, the second outer piston ring 212 and the second inner carrier ring 222 are arranged respectively.The position of these piston rings is respectively all outside after piston combustion face 111, inner carrier firing level 121, outer piston firing level 211 and the inner carrier firing level 221, be close to the first outer piston head 116, slide block 118, second outer piston head 216 and slide block 218 simultaneously respectively, leak to prevent the fluid between the first outer piston head 116, slide block 118, second outer piston head 216 and slide block 218 and the cylinder sleeve surface.Other piston ring also may use in addition.
Further, as top said, first cylinder sleeve 130 and second cylinder sleeve 230 respectively have several suction ports 161 and suction port 261 and relief opening 163 and relief opening 263.Give an example, on first cylinder assembly 100, first outer piston, 110 opening and closing suction ports 161, first inner carrier, 120 opening and closing relief openings 163 simultaneously.
Further, housing 103 is used for holding the first cylinder die cavity, 104, the second cylinder die cavities 204 and bent axle die cavity 304.These die cavities are used for holding first cylinder, second cylinder and bent axle 300 respectively.The first cylinder die cavity 104 has defined the first slide block slip surface 106 and has ended at first housing end plug 107. Slide block 118 and 106 slipper seals of the first slide block slip surface closely cooperate.Slide block 118, the first housing end plugs 107 and the first slide block slip surface 106 have defined first a scavenging chamber 105.
Further, the first cylinder die cavity 104 is divided into two chambeies by one group of first seal cartridge 123: a chamber has defined the part of bent axle die cavity 304, and another has defined the second scavenging chamber 109.First seal cartridge 123 is tubuloses; Each has an endoporus that diameter is moderate above the lining, so that a pull bar in first pull bar 411 can pass thus.Lining on first seal cartridge 123 terminal 169 and slide block 118 link together.When slide block 118 axial translations, it just drives first seal cartridge, 123 associated movements like this.
Further, the first cylinder die cavity 104, slide block 118, the first cylinder sleeves 130 and first seal cartridge 123 have defined the second scavenging chamber 109 jointly.The second scavenging chamber 109 links to each other with housing 103 by the seal with buss ring 128 on first seal cartridge 123 with bent axle die cavity 304, and fluid-encapsulated scurries into.Seal with buss ring 128 can adapt to the translation of first seal cartridge 123, in this process, prevents fluid communication between the second scavenging chamber 109 and the bent axle die cavity 304.The air inlet fluid circulates by the second scavenging chamber 109, simultaneously lubricated and or cooling fluid circulate by bent axle die cavity 304.
Further, carry out the fluid circulation by at least one 165, one scavenge line 166 of the first scavenging chamber mouth and second a scavenging chamber mouth 167 between the first scavenging chamber 105 and the second scavenging chamber 109.The first scavenging chamber 105 and scavenge line 166 are realized the fluid circulation by the first scavenging chamber mouth 165; The second scavenging chamber 109 and scavenge line 166 are realized the fluid circulation by the second scavenging chamber mouth 167.
Further, similarly, the second cylinder die cavity 204 has defined the second slide block slip surface 206, and stops at second housing end plug, 207 places.Slide block 218 and the second slide block slip surface 206 slide and fit tightly.Slide block 218, the second housing end plugs 207 and the second slide block slip surface 206 have defined the 3rd scavenging chamber 205 jointly.With the second cylinder similar arrangements, the second cylinder die cavity 204 is divided into two chambeies by one group of second seal cartridge 223: a chamber has defined the part of bent axle die cavity 304, and another has defined the 4th scavenging chamber 209.
Further, the mechanical part of forming the first scavenging chamber 105, the 3rd scavenging chamber 205, the second scavenging chamber 109 and the 4th scavenging chamber 209 is referred to as a scavenging pump.Next the running principle of scavenging pump will be described by example.As shown in Figure 2, suppose that first cylinder is in expansion stroke, wherein bent axle 300 is in 90 ° of positions of atdc.At expansion stroke, first outer piston 110 separates with the high-pressure liquid driving of scavenging chamber, left side generation in first inner carrier, the 120 burned processes.As shown in Figure 3, first outer piston 110 and slide block 118 move towards the direction near first housing end plug 107 thereupon, and then have reduced the volume of the first scavenging chamber 105, increase the pressure of the first scavenging chamber, 105 inner fluids simultaneously.
Further, under a predetermined pressure, adjoin an one-way cock 168 of the first scavenging chamber mouth 165 between other suitable position, discharge high-pressure liquid from the first scavenging chamber 105.High-pressure liquid enters in the second scavenging chamber 109 by left side scavenge line 166.Be released out a predetermined instant in 105 processes of the first scavenging chamber at high-pressure liquid, suction port 161 is unlocked, thereby makes the high-pressure liquids in the second scavenging chamber 109 enter first firing chamber 150.
Further, the air inlet fluid in the second scavenging chamber 109 is further compressed by the motion of first outer piston 110.In a scheme of the present invention, relief opening 163 is closed early than suction port 161.In this process, be accompanied by first outer piston 110 towards the direction motion away from bent axle 300, the air inlet hydrodynamic pressure further increases.
Further, in compression stroke, first outer piston 110 and first inner carrier 210 are respectively under first pull bar 411 and second push rod 412 drive, and be close to each other.First outer piston 110 and slide block 118 move towards the direction away from first housing end plug 107 thereupon, and then have increased the volume of the first scavenging chamber 105, have reduced the pressure of the first scavenging chamber, 105 inner fluids simultaneously.This one-way cock 168 that scavenging chamber mouth 165 of winning is adjoined is closed, and the breather cheek valve door 172 of the one or more air inlet fluid processes on first housing end plug 107 is opened simultaneously.
Be the side cutaway view of first cylinder of a kind of internal-combustion engine of the present invention as shown in Figure 4.First seal cartridge 123 comprises a suitable cross-sectional shape, as circular or oval, in order to adapt to the sphere of activities of first pull bar 411 between motor 10 on-stream periods.As shown in the figure, first pull bar 411 is in descending process, wherein shows among the bent axle 300(figure) in lower dead center moment position.
Be first side view cutaway drawing of firing chamber of first cylinder of internal-combustion engine of the present invention as shown in Figure 5, the side cutaway view of first cylinder sleeve 130 of definitional part first firing chamber 150.First cylinder sleeve 130 comprises an air inlet port 136.Air inlet port 136 is made up of at least one group of suction port 161 and at least one gas port 162 of advancing.First cylinder sleeve 130 also comprises an exhaust port 138.Exhaust port 138 comprises delegation's relief opening 163 at least.
The sectional view of suction port 161 of the present invention and suction port 162 shown in Fig. 6 and 7.Each suction port 161 comprises a radial flow path 164.Radial flow path 164 makes the air inlet fluid enter first firing chamber 150.The direction that enters is the radial direction of left side cylinder sleeve axis X-X, and with direction that exhaust port 138 points to first outer piston 110 of control air inlets a reverse angle α is arranged, as shown in Figure 3.Radial flow path 164 makes the air inlet fluid leave the first cylinder sleeve bore face 139, enters the zone line of first firing chamber 150.A suitable reflex angle α determines to depend on the air inlet hydrodynamic pressure that offers suction port 161, the pressure in first firing chamber 150, the temperature of air inlet fluid, the speed of air inlet fluid with become to grade.Suction port 161 has a path of non-eddy current on the whole.This feature has been determined the liquid form at center region air inlet fluid.
Further, each suction port 162 comprises a tangential runner 364.Tangential runner 364 makes the air inlet fluid enter first firing chamber 150 along tangential direction roughly.The direction that enters is the tangential direction of the first cylinder sleeve bore face 139, and with direction that exhaust port 138 points to first outer piston 110 of control air inlets a reverse angle β is arranged, as shown in Figure 3.Tangential runner 364 guiding air inlet fluids roughly move along the first cylinder sleeve bore face 139.Tangential runner 364 makes that adjoining the side regions that center region that the air inlet fluid enters and the air inlet fluids in the first cylinder sleeve bore face 139 enter sets up.A suitable reflex angle β determines, depends on the air inlet hydrodynamic pressure that offers suction port 162, the pressure in first firing chamber 150, the temperature of air inlet fluid, the speed of air inlet fluid with become to grade.Having one in first firing chamber 150 is the fluid path of eddy current substantially.This characteristics determined the liquid form of air inlet fluid.
Further, in motor 10 operation process, during first outer piston, 110 reversing motions (away from crankshaft direction), suction port 162 is opened.The unlatching of suction port 162 makes near exhaust (burning) fluid it form a backflow; Heavier and the cold air inlet fluid of centrifugal force pulls is away from axis X-directions X.Replaced near the first cylinder sleeve bore face 139 exhaust fluid so be the air inlet fluid of eddy current form subsequently.Along with the continuation reversing motion of first outer piston 110, suction port 161 and suction port 162 are opened together.The air inlet fluid of suction port 161 has replaced exhaust fluid at first firing chamber, 150 middle positions with center air inlet nowed forming.Because the backflow when suction port 162 is opened, this center air inlet are the fluid interference that can not be subjected to passing suction port 162 when being flowing in beginning.There is a more smooth fluid front end 177 between air inlet fluid 175 and exhaust fluid 176 side air inlet zone and the junction, center air inlet zone of adjoining air inlet zone, center and the first cylinder sleeve bore face 139.After fluid front end 177 arrived relief opening 163, air inlet fluid 175 was cleared away or alternative exhaust fluid 176. in first cylinder sleeve 130 from Fig. 5 substantially fully
One group of side view of first cylinder sleeve 130 of a scheme of the present invention and sectional drawing shown in Fig. 8 and 9.First cylinder sleeve 130 has defined part first firing chamber 150 and the terminal at least one row in 136 places of air inlet is combined into gas port 461.Each is combined into gas port 461 and comprises one and be combined into flow channel 464.Each is combined into flow channel 464 and comprises roughly tangential face 661 of a sagittal plane 561 and.Sagittal plane 561 and tangential face 661 make the air inlet fluid along radially entering first firing chamber 150 with tangential direction with respect to axis X-X.First outer piston, 110 directions that air inlet fluid approach axis and exhaust port 138 point to the control air inlet have a reverse angle γ, as shown in Figure 3.Be combined into the mini engine that gas port 461 is particularly suitable for being applied to arrange because of insufficient space the multirow suction port.The single file suction port is integrated with two functions: make the center region of direction of flow first firing chamber 150, necessary eddy current is provided simultaneously.
Further, good air inlet fluid front end 175 can be extended its width roughly to the width of first firing chamber 150, and effectively by first firing chamber 150 to relief opening 163 cleaning exhaust fluids 176.Intake duct geometric parameter (highly, width, length, radially with tangential etc.), interior outer piston arrangement of time, the combination of air inlet fluid pressure and temperature and other factors makes that almost all exhaust fluid 176 is cleared away in first firing chamber 150 at exhaust phase.Equally, above parameter also makes the air inlet fluid 175 that is rich in fuel oil do not overflowed by relief opening 163 places basically.The above-mentioned flow pattern that produces in first firing chamber 150 has improved engine performance, and has significantly reduced the discharging of rich oil pollutant.
Be that the symmetry timing of opening and closing porting is about a functional arrangement of crank angle as shown in figure 10.By suction port curve 22a as can be seen, the opening and closing of suction port are the curve about axis m symmetry constantly.By relief opening curve 20a as can be seen, the opening and closing of relief opening are the curve about axis m and suction port curve 22a symmetry constantly; The unlatching of relief opening is early than the unlatching of suction port, and exhaust close is later than inlet close.Because closing, the last pass of relief opening causes certain pressure loss, so this timing configuration is undesirable.
The asymmetric timing of opening and closing porting is about a functional arrangement of crank angle as shown in figure 11.By suction port curve 22b as can be seen, the opening and closing of suction port are the curves of symmetry center off-axis m.By relief opening curve 20b as can be seen, the opening and closing of relief opening are the curves about axis m symmetry; The unlatching of relief opening is early than the unlatching of suction port, and relief opening closes early than inlet close simultaneously.Because the relief opening earlier closing, there is not the pressure loss after the exhaust close, therefore this timing is disposed to be beneficial to and is kept or increase pressure in the firing chamber.
Further, outer piston connects axle journal 311 and is connected axle journal 312 is positioned at uniqueness with respect to crankshaft rotating axis 310 position with inner carrier.It is far away apart from the crankshaft rotating axis than outer piston connection axle journal 311 apart from the crankshaft rotating axis that inner carrier connects axle journal 312.This just causes the stroke of first inner carrier 120 and second inner carrier, 220 to the first outer pistons 110 and second outer piston 210 bigger.Further, first inner carrier 120 and second inner carrier, 220 opening and closing relief openings 163 and relief opening 263.Directly control axle journal 312 angular advances of first inner carrier 120 and 220 motions of second inner carrier.First outer piston 110 and second outer piston, 210 opening and closing suction ports 161 and suction port 162.Directly axle journal 311 angles of control first outer piston 110 and 210 motions of second outer piston lag.
Further, in the asymmetric timing that provides in the above, the unlatching of relief opening 161 is early than the unlatching of suction port 161 and suction port 162, and it closes closing early than suction port 161 and suction port 162.In this layout, there is not the air inlet fluid to be discharged from by relief opening 162, can clear away the waste gas in first firing chamber 150 simultaneously basically.
Further, first outer piston 110 is opening and closing suction port 261, suction port 262 and be combined into gas port 461 optionally, so that the air inlet fluid enters first firing chamber 150 constantly in expectation.A scheme of the present invention comprises asymmetric timing.Wherein finish in burning or expansion stroke, before the lower dead center, suction port 163 is opened when 75 ° of crank angles greatly, and suction port 162 is opened when 45 ° of crank angles greatly.On the contrary, for example finish in compression stroke, after the lower dead center, relief opening 163 is closed when 45 ° of crank angles greatly; And suction port 162 is closed when 55 ° of crank angles greatly.
The side cutaway view of another embodiment's of internal-combustion engine of the present invention motor 12 when its bent axle 1300 corners are 270 ° shown in Figure 12 and 14.When this angle, outer piston 1110 and 1120 condenses together in the left side in the left hand cylinder 1100; Left side porting 1161 and 1163 is closed thereupon.Air inlet fluid in the left side between the outer piston 1110 and 1120 is compressed.Right cylinder 1200 is finished its expansion stroke; The right side outer piston separates with 1220 with inner carrier 1210; Right side porting 1261 and 1263 is unlocked thereupon.
Further, in order to introduce air inlet fluid (pre-burning gas) and combustion gas fluid, suction port 1161, suction port 1261, relief opening 1163 and relief opening 1263 are opened separately.The time that they are opened is depended on a lot of fixing and variable factors.Fixed factor comprises left and right side outer piston and left and right side inner carrier 1110,1210,1120 and 1220 running length and the distance between suction port 1161, suction port 1261, relief opening 1163 and the relief opening 1263 etc.Variable factor comprises the pressure of engine speed and air inlet fluid etc.
Further, the opening and closing of suction port 1161, suction port 1261, relief opening 1163 and relief opening 1263 are regularly preferential, facilitate the use the air inlet fluid, and combustion gas is discharged from firing chamber, the left and right sides 1150 and 1250 substantially fully; Endurance can not be oversize simultaneously, in order to allow the air inlet fluid to leave relief opening 1163 and 1263.The waste gas fluid is discharged thoroughly can not reduce engine performance.The air inlet fluid can cause atmospheric pollution by the effusion of relief opening.
Further opening time and the engine speed of suction port 1161, suction port 1261, relief opening 1163 and relief opening 1263 have direct relation; Other is all fixed.When high rotating speed, suction port 1161, suction port 1261, relief opening 1163 and relief opening cycle opening time when 1263 opening times, the cycle was shorter than the slow-speed of revolution.Under a constant suction pressure, the displacement amount of intake and exhaust fluid and engine speed have direct relation.Under an engine speed, utilize the air inlet fluid that waste gas is implemented desirable cleaning completely and can realize.
Further, Figure 12 and Figure 14, what they showed is the motor that has the slip cylinder sleeve.In the drawings, the data of part thousand orders of magnitude are used for indicating some parts.In other place of this detailed description, same or similar parts indicate with hundred figure place data.In a scheme of the present invention, the variable air inlet timing is used for adjusting suction port 1161, suction port 1261, relief opening 1163 and relief opening 1263 with respect to the opening time of engine speed.Housing 1103 comprises 1104, one right cylinder die cavities 1204 of a left hand cylinder die cavity, and a bent axle die cavity 1304.These are used for holding left hand cylinder 1100, right cylinder 1200 and bent axle 1300 respectively.Left hand cylinder die cavity 1104 has defined left side sleeve port 1134, and it is closely contacted with left side cylinder sleeve 1130, is slidingly matched.Suitable slipper seal band (not shown) is applied between left side sleeve port 1134 and the left hand cylinder die cavity 1104.
Further, the axis of left side cylinder sleeve 1130 is preferentially controlled with respect to the position of left side sleeve port 1134.When the motor slow-speed of revolution moved, left side cylinder sleeve 1130 axially moved towards bent axle 1300.Left side cylinder sleeve 1130 has effectively shortened the opening time of left side relief opening 1163 towards the movement of bent axle 1300.Under opposite extreme situations, left side cylinder sleeve 1130 moves axially a sufficiently long distance towards bent axle 1300, and left hand piston 112 has just partly been opened left side relief opening 1163 like this, thereby has reduced the time that the waste gas fluid is discharged by left side relief opening 1163.
Further, similarly, the axis of right side cylinder sleeve 1230 is preferentially controlled with respect to the position of right side sleeve port 1234.When the motor slow-speed of revolution moved, right side cylinder sleeve 1230 axially moved towards bent axle 1300.Right side cylinder sleeve 1230 has effectively shortened the opening time of right side relief opening 1263 towards the movement of bent axle 1300.Under opposite extreme situations, right side cylinder sleeve 1230 moves axially a sufficiently long distance towards bent axle 1300, and right hand piston 1120 has just partly been opened right side relief opening 1263 like this, thereby has reduced the time that the waste gas fluid is discharged by right side relief opening 1263.
As shown in figure 13 in the scheme of the present invention the asymmetric timing of opening and closing porting about a functional arrangement of crank angle.As the symmetrical curve of expression suction port opening and closing, the symmetry center of the first suction port curve 22b departs from the symmetry axis of expression exhaust open and the first exhaust curve 20b that closes.Shown in the second suction port curve 22c and the second relief opening curve 20c, the movement of left side cylinder sleeve 1130 makes the timing curve of porting that movement take place.By mobile left side cylinder sleeve 1130, the porting timing corresponding and suitable with engine speed and load can realize.
Further, moving axially of left side cylinder sleeve 1130 and right side cylinder sleeve 1230 can be realized by many modes.In a scheme of the present invention, left side cylinder sleeve 1130 and right side cylinder sleeve 1230 are realized mobile by a drive system.This drive system is including but not limited to a motor, hydraulic unit driver etc.This drive system is controlled by a feedback control system; This feedback control system makes them arrive a preposition according to predetermined engine speed or other performance parameter control left side cylinder sleeve 1130 and right side cylinder sleeve 1230.In another scheme of the present invention, the hydrodynamic pressure that acts on the cylinder sleeve partial portion overcomes the restoring moment of location left side cylinder sleeve 1130 and right side cylinder sleeve 1230.
The side cutaway view of the motor 12 in the scheme of the present invention as shown in figure 15.As left hand cylinder 1200, and do not show among the left hand cylinder 1100(figure of similar arrangement); Housing 1103 comprises a fluid input 1264.This fluid input can provide the controlled hydraulic that acts on right side cylinder sleeve 1230 exhaust ends.Right side cylinder sleeve 1230 also comprises the one or more flanges 1237 that cooperate with biasing member 1259.
Further, in a scheme of the present invention, providing the fluid of hydraulic pressure at right side cylinder sleeve 1230 is the cooling liquid of cooling right side cylinder sleeve 1230.Coolant pressure is controlled by a feedback control system.This feedback control system makes them arrive preposition according to predetermined engine speed or other performance parameter control left side cylinder sleeve 1130 and right side cylinder sleeve 1230.
Further, the motor among the present invention program has the multiple internal combustion process that energy is provided, such as but not limited to those spark ignitions (SI), and diesel engine and even matter charge compression and combustion combustion processes such as (HCCI).
Further, in the spark ignition combustion process, uniformly gas mixture be pressed into cylinder and when compression stroke finishes by spark ignition.Spark causes a generation that can diffuse to flame kernel or the hot prewave of whole firing chamber.The oil gas flow that enters the firing chamber by control makes that the load (moment of torsion) of motor is controlled.Under all loads, it is invariable that air fuel ratio keeps substantially.
Further, the flame front temperature that flame kernel produces in the cylinder is above 1600 ℃.Under this temperature, can produce nitrogen oxide (NOx).Therefore, some measures that reduce NOx are essential.Such as but not limited to, by the NOx in the catalyzed conversion minimizing mixture.
Further, in a scheme of the present invention, volume of cylinder is divided into a firing chamber and a cylinder; Volume of cylinder also comprises radiating fin or a catalyst that reduces NOx between firing chamber and cylinder in addition.For the reason of dynamic response aspect, and in order to keep best scavenging configuration, transducer is attached on the exhaust pition; Fuel oil is injected into firing chamber by the direct injection mode.Such combustion system is not being sacrificed oil consumption, realizes under power output and the travelling comfort condition that utmost point low emissions combustion aspect provides breakthrough.
Further in diesel engine combustion, pure air is at first compressed in cylinder, causes air temperature to raise.When compression stroke finished, fuel oil was injected under hyperbaric environment in the pressurized air of heat.Fuel gasification and mix with pressurized air is local.When temperature is elevated to predetermined temperature, air and fuel oil mixture spontaneous combustion.Spray into amount of fuel in the cylinder by change, control engine load.
Further, in the bump combustion chamber process, gas mixture is compressed in cylinder uniformly.When the temperature of gas mixture raise because pressure raises, spontaneous combustion had just taken place.For guaranteeing spontaneous combustion, high compression ratio of bump combustion chamber process need.In order to reduce chemical reaction rate, thereby reduce rate of burning, very rare gas mixture is employed.Higher air fuel ratio or exhaust gas recirculatioon (EGR) can realize suitable gas mixture.By changing the amount of fuel in the gas mixture, engine load is controlled.
Further, it is fast that homogeneity compression-ignition engine has utilized higher compression ratio while rate of burning.Low with respect to the motor of spark ignition efficient when the sub load, homogeneity compression-ignition engine is the efficient height when low-load.A main advantage of homogeneous compression-ignition is that it produces a spot of nitrogen oxide (NOx).The formation of NOx depends on combustion temperature strongly.High temperature can produce more NOx.To produce a large amount of NOx different with spark ignition combustion process that the flame front that produces surpasses 1600 ℃ of high temperature, and the spontaneous combustion occurrence temperature in the bump combustion chamber process is lower than 1600 ℃ to a certain extent, about 875 ℃.
Further, because bump combustion chamber is uniformly, use very thin gas mixture simultaneously, combustion temperature becomes very low with respect to the spark ignition combustion process.Low temperature can produce very a spot of NOx.The air fuel ratio of stoichiometric mixture is 1.For the bump combustion chamber process, air fuel ratio is more near 1, and firing temperature is more high, simultaneously more near the generation temperature of NOx.The air fuel ratio scope is that 2 ~ 10 o'clock suitable generations are lower than the firing temperature that NOx produces temperature.Therefore, the air fuel ratio in the bump combustion chamber process can be up to about 10.
Further, the bump combustion chamber process does not produce the flue dust with the diesel engine combustion same degree.Because chemical reaction is very near the best and " constant volume combustion " that do not have the engine knock restriction faster in the firing chamber, therefore with respect to other combustion process, the bump combustion chamber process increases the thermal efficiency.Engine knock is also referred to as pinking, is a technical term.Its definition is, under unusual combustion case, a plurality of flames collisions in the firing chamber raise internal pressure of combustion chamber and it occurs in incorrect time in the burn cycle.The situation that engine knock is normally very inadvisable and harmful.
Further, though the present invention program can adopt the bump combustion chamber process, the control of this combustion process is than spark ignition or diesel engine combustion difficulty.The ignition timing that is different from the spark ignition combustion process, homogeneous compression-ignition are not the beginnings of controlling burning by direct mode.A plurality of factors are depended in the startup of this burning.Major parameter comprises compression ratio and inlet temperature etc.Control control burning to these major parameters takes place, and makes it reach the point that needs in good time a method is provided.
Further, in the present invention program, engine power derives from an auxiliary bump combustion chamber process.Gas mixture is compressed into a predetermined state that is lower than the autoignition conditions threshold value in cylinder in this process.Supplementary energy is as a thermal source that is produced by spark plug or heater plug etc., but is not limited thereto.This supplementary energy is used for initiating a burning that maintains a steady heat wave environment.Auxiliary bump combustion chamber process takes place being lower than under the threshold value environment, produces controlled and unified burning.This burning does not have out of season pinking (engine knock).
Further, starting the supplementary energy that burns can be provided by in many appropriate device.These devices comprise and are not limited to a spark plug or heater plug.Different with spark plug, the advantage of heater plug is that it can not produce flame front.Heater plug is the device that provides rapid heating to originate by parts that are exposed in the gas mixture.As everyone knows, heater plug is applied to the diesel engine cold start-up.As a rule, when diesel engine starting, the initial temperature of gas mixture is low excessively, is not enough to reach spontaneous combustion.Heater plug offers the necessary extra heat source of burning.When engine temperature raise and can heat gas mixture, heater plug was not in work.
Further, in the solution of the present invention, heater plug is installed in the cylinder and controls the firing time of gas mixture.In a scheme of the present invention, heating opportunity of heater plug is by the location triggered of piston (one of them piston).In another program, the heating of heater plug is triggered by the surge pressure of the gas mixture in the cylinder opportunity.
Further, in the solution of the present invention, heater plug is controlled by a feedback control system.In scheme, feedback control system is controlled heater plug based on predetermined performance standard therein.In scheme, when the top dead center position of maximum thermal efficiency can be provided, heater plug heated to start burning at bent axle therein.In another program, reach peak value at internal pressure of combustion chamber, namely passed through top dead center position at 5 ~ 10% o'clock afterwards, heater plug heats to start burning.
Further, in another scheme, the performance parameter of bent axle is depended in the heating of heater plug constantly, changes as change in torque and angle, but is not limited thereto.Still in another program, the heater plug heating regularly starts burning to optimize power output.When crankshaft speed constant, especially suitable when being applied to power generation application.
Further, in other scheme of the present invention, the temperature of heater plug is variable, and is controlled specially.Give an example, glow plug temperature based on or controlled according to the temperature of gas mixture, but be not limited thereto.In another scheme, glow plug temperature is controlled based on exhaust gas temperature.Still in the another one scheme, control glow plug temperature by measuring bent axle with respect to the fluctuation of desirable constant mean speed.
Further, as Figure 15 be the side cutaway view of first cylinder in the scheme of the present invention.This cylinder is included near left side outer piston firing level 111 and the left side inner carrier firing level 121 that forms a firing chamber 1150a top dead center.The left side outer piston firing level 111 of raised annular shape has been formed firing chamber 1150a with the inner carrier firing level 121 that has the complimentary profile.Outer inner carrier firing level 111 and 121 has formed a flat region; This flat band has been created a high strength eddy current near top dead center, improve toxic emission thereby provide, and fuel consume, the possibility of power output and travelling comfort.The outer piston firing level 111 and the inner carrier firing level 121 that are fit to other form of special intention also are expected.
The side cutaway view of first cylinder shown in Figure 16 and 17 in the scheme of the present invention includes the side cutaway view of first cylinder when ignition system is in non-contact and contact position of an Intermittent Contact spark ignition system 185.This first cylinder comprises first outer piston head 116.First outer piston head 116 comprises an outer piston firing level 111 and comprises conventional ignition plug, but is not limited thereto the spark lighter 180 of a class.Spark lighter 180 is disposed in first outer piston head, 116 inside.Like this spark gap 182 be correspondingly positioned at outer piston firing level 111 near, and be exposed in the air inlet fluid.Be understandable that spark lighter 180 can be arranged on other parts of first cylinder, be such as but not limited to inner carrier firing level 121 or be integrated in a side of first cylinder sleeve 130.
Further, Intermittent Contact spark ignition system 185 comprises the fixed touch plate 188 of being extended the mobile contact 186 of coming and one and axially-aligned opposed with mobile contact by first outer piston 110.When first outer piston head 116 roughly moved to top dead center position, mobile contact 186 contacted conduction with fixed touch plate 188, and discharged at spark gap 182 places.When first outer piston 110 was positioned at other all positions, mobile contact 188 separated with fixed touch plate 186 and opens circuit.In a scheme of the present invention, by regulating relevant fixed touch plate axial position, ignition mechanism is adjustable.In view of being blunt by mobile fixed touch plate away from the time of ignition that mobile contact obtains, previous time of ignition obtains to realize near mobile contact by mobile fixed touch plate.
The side cutaway view that comprises first cylinder of a sliding contact ignition system 285 as shown in figure 18 in the scheme of the present invention.As shown in above-mentioned scheme, the incendiary source of spark lighter 180 or spark plug 280 and so on is arranged in the inside of first outer piston head 116.Sliding contact ignition system 285 comprise one by heater plug 280 extend to slide block 118 accept that contact 286 and one are extended by first housing end plug 107 and with the slip contact 288 that receives contact 286 axially-aligned.When incendiary source was a spark lighter 180, spark lighter 180 was controlled in a conventional manner, and namely when first outer piston head 116 roughly moved to top dead center position, spark lighter 180 discharged an electrical spark at spark gap 182 places.When incendiary source was heater plug 280, the heating of heater plug 280 was all controlled in any time of piston cycle.Such as but not limited to, heater plug 280 can be controlled in scavenging process, makes its heating air inlet fluid to predetermined temperature; And when top dead center position, it is controlled to and produces a high temperature fluctuation.In other words, heater plug 180 can be come the heating air inlet fluid by continuous running; And spark plug 180 can only be used for igniting.
Further, in a scheme of the present invention, spark plug 180 shown in Figure 16 is preheated plug 280 and substitutes.Heater plug 280 provides a thermal source that can promote the air inlet fluid spontaneous combustion under the pressure.Because air inlet fluid pressure and temperature in the compression stroke process increases, heater plug 280 is activated, and provides thermal source to the air inlet fluid, to promote the air inlet fluid in the predetermined instant spontaneous combustion of this circulation.
Further, for air inlet fluid spontaneous combustion environment is provided, heater plug 280 needn't be worked under extreme temperature as electric plug.Give an example, when engine start, the air inlet fluid temperature (F.T.) is lower, and heater plug 280 can fully improve the air inlet fluid temperature (F.T.), adds the extra pressure of air inlet fluid when top dead center position, and the temperature of air inlet fluid is enough kept spontaneous combustion.Use heater plug 280 to provide a pressure source that is similar to very much piston for the igniting under the relative low temperature in addition.This pressure source compress inlet air fluid, and improve fluid temperature (F.T.) to spontaneous ignition temperature, firing chamber, left side 1150 interior all air inlet fluids are burnt together.
Further, ideally, for the consideration of aspects such as performance and discharging, the burning of air inlet fluids should be even in the firing chamber, left side 1150, and is spontaneous and intactly carry out.Heater plug igniting under common spark ignition and some situation has caused inhomogeneous burning.A flame front can spread forward in whole firing chamber, causes the inhomogeneous and partial combustion of air inlet fluid thereupon.In the solution of the present invention, the adverse effect of flame front is weakened; Wherein autoignition conditions is provided in the firing chamber, and simultaneously near under the autoignition conditions, the burning that is caused by spark plug or heater plug produces.Other scheme of the present invention is used to reduce or eliminate inhomogeneous and incomplete burning.These schemes including but not limited to, in a piston cavity or the igniting of piston chamber inner sealing.
It is the side cutaway view of first outer piston head 116 in the solution of the present invention shown in Figure 19-21.Heater plug 280 is arranged in by left side inner carrier firing level 121 and extends, in the chamber that forms in first outer piston head 116.Heater plug extends in the chamber, the air inlet fluid in the heating chamber.In this arranged, when outside the chamber spontaneous combustion taking place, the flame front that heater plug 280 produces all was accommodated in the chamber basically.Light the chamber external admission hydrodynamic pressure that causes because of air inlet fluid in the chamber and raise, make temperature and pressure evenly raise.This is conducive to realize in the firing chamber, left side 1150 uniformly, spontaneous and burning completely.
Further, as Figure 19, wherein, heater plug 180 extends in the spherical cavity.This spherical cavity is extended and is formed in first outer piston head 116 by inner carrier firing level 121.Spherical cavity 190 includes an import 191.This import can guide the air inlet fluid of introducing to enter spherical cavity 190.Spherical cavity 190 is enough little in order to fully hold any flame front.
Further, as Figure 20, wherein, heater plug 180 extends in the vortex-like chamber 192.This vortex-like chamber is extended by inner carrier firing level 121, and forms in first outer piston head 116.Vortex-like chamber 192 comprises one and can guide the air inlet fluid to flow along surface, vortex-like chamber 194 and make it be accommodated in import 193 in the vortex-like chamber 192 substantially.Heater plug extends in the vortex-like chamber 192 and is positioned in import 193 beyond the invisible.Deposit at such cloth, any flame front that heater plug 280 produces is directed to and vortex-like chamber surface 194 places of heater plug 280 to an anti-side, and it is flowed repeatedly, in order to postpone it greatly by vortex-like chamber 192 time of liberations.
Further, as Figure 21, wherein, heater plug 180 extends into 197 places, bottom of a rectangular cavity 196.This rectangular cavity 196 is extended by inner carrier firing level 121, and forms in first outer piston head 116.Rectangular cavity 196 comprises one and can guide the air inlet fluid to the entrance point 195 at 197 places, bottom, chamber.The degree of depth of rectangular cavity is predetermined, guaranteeing before the spontaneous combustion of rectangular cavity outside air inlet fluid, and the flame front that heater plug 280 the produces rectangular cavity of not overflowing.
Further, the chamber as rectangular cavity 196 grades of showing among Figure 21 and so on comprises the internal surface 198 that catalytic layer 199 is arranged at least part of position.In scheme, catalytic layer 199 contains the material of a kind of NOx of minimizing or other bad effulent content therein; These NOx or bad effulent may be to be formed by the flame front that produces in the rectangular cavity 196.In another program, catalytic layer 199 contains a kind of interior flame front of rectangular cavity that reduces and forms possible material.
Further, in other scheme of the present invention, the heating element of heater plug 280 also comprises a catalytic materials 299.Catalytic materials 299 comprises a kind of material that causes burning based on the chemical process of air inlet fluid.Along with the rising of air inlet hydrodynamic pressure, after fluid reaches predetermined concentration, cause igniting.Be understandable that above-mentioned is to exchange use as ignition system schemes such as spark lighter 180 and heater plugs 280.For example, the spark lighter among Figure 16 180 can be replaced by the heater plug 280 among Figure 18.
Further, in the solution of the present invention, fuel oil is provided for motor in many ways.In Figure 12, in a scheme of the present invention, a fuel injector 1183 is disposed in left and right side cylinder sleeve 1130 and 1230 adjacent places that end has a fuel injector mount inlet 1184, and sprays liquid fuel in left and right side firing chamber 1150 and 1250.The air inlet fluid passes left and right side suction port 1161 and 1261 with air form, enters left and right side firing chamber 1150 and 1250.When the air inlet fluid was in compressive state, fuel oil was injectedly gone into a left side/right firing chamber suitable time.
Further, in Figure 16 and 17, fuel injector 183 sprays liquid fuel in the second scavenging chamber 109.The air inlet fluid of air form is provided to the second scavenging chamber 109 by the first scavenging chamber 105 and mixes with the fuel oil of fuel injector ejection.Gas mixture is transported in first firing chamber 150 by suction port 161 by the second scavenging chamber 109.
Further, first crankshaft component 320 comprises columniform first main journal 325.First main journal 325 comprises first through hole 323 of a definition crankshaft rotating axis 310.First crankshaft component 320 also comprises one first nested 322.This nested face has first offset axis 321 that departs from crankshaft rotating axis 310.In Fig. 1, first main journal 325 provides support between bent axle 300 and housing 103.
Further, second crankshaft component 330 comprises second through hole 333.Second through hole 333 is coaxial and also defined crankshaft rotating axis 310 with first through hole 323.Second crankshaft component 330 also comprises one second nested 332 nested with the 3rd 336.Second offset axis 331 that departs from crankshaft rotating axis 310 is arranged for second nested 332.The 3rd offset axis 337 that departs from crankshaft rotating axis 310 and second offset axis 331 is arranged for the 3rd nested 336.Be slidingly matched into for first nested 322 in second nested 332.Second crankshaft component 330 also comprises one and has cylindrical cross-section and first journal surface 334 coaxial with second offset axis 331.First journal surface 334 cooperates with first collar bearing 361 on it.
Further, three-crankshaft parts 340 comprise one coaxial with first through hole 323, and can define the third through-hole 343 of crankshaft rotating axis 310 equally.Three-crankshaft parts 340 also comprise one the 4th nested 342.This nested 342 has one and departs from crankshaft rotating axis 310 and four offset axis 347 coaxial with the 3rd offset axis 337.Be slidingly matched into for the 3rd nested 336 in the 4th nested 342.Three-crankshaft parts 340 also comprise one in addition and have cylindrical cross-section and second journal surface 344 coaxial with the 4th offset axis 349.Second journal surface 344 cooperates with second collar bearing 362.
Further, three-crankshaft parts 340 also comprise one the 5th nested 346.This nested face has one to depart from crankshaft rotating axis 310 and five offset axis 341 coaxial with second offset axis 331.Three-crankshaft parts 340 also comprise the 3rd journal surface 348 that cylindrical cross-section is arranged.The 3rd journal surface 348 cooperates with the 3rd collar bearing 363.
Further, the 4th crankshaft component 350 comprises columniform second main journal 355.This main journal comprises the fourth hole 353 of an and definition crankshaft rotating axis 310 coaxial with first through hole 323.Other the 4th crankshaft component 350 also comprises one the 6th nested 352. this nested face has one to depart from crankshaft rotating axis 310 and six offset axis 351 coaxial with the 5th offset axis 341.The 5th offset axis 341 is simultaneously also coaxial with first and second offset axis 321 and 331.The 3rd journal surface 348 on the three-crankshaft parts is coaxial with the 6th offset axis 351.Be slidingly matched into for the 6th nested 352 in the 5th nested 346.In Fig. 1, second main journal 355 provides support between bent axle 300 and housing 103.In a scheme of the present invention, each nested allow to have enough fastness press-fit assembling guaranteeing axially and angular alignment, but also to allow dismounting.In another scheme, each nested face has key and guarantees axially and angular alignment in the mode that key cooperates.
Further, first push rod 412 and second push rod 422 are connected a public inner carrier axle journal 312 on the bent axle 300.Therefore inner carrier axle journal 312 also just is called as the push rod axle journal.In a scheme of the present invention, first push rod 412 and second push rod 422 are in same common plane.Scheme that allows left first push rod 412 and second push rod, 422 aligned coplanar to arrange comprises first push rod 412 that has a single hole axle journal end 414 relative with concave ends 413.Single hole axle journal end 414 has a single hole 415 that cooperates with the 362 tight rotations of second collar bearing.
Further, second push rod 422 comprises a diplopore axle journal end 424 relative with concave ends 423.Diplopore axle journal end 424 comprises one group of tang 426, perhaps is referred to as a handle fork.With the coaxial coaxial aperture 425 of tang 426 and second collar bearing 362 closely rotation cooperate.Tang 426 is separated intended distance in order to cooperate with the single hole axle journal end 414 of left side push rod 412.
Further, first push rod 412 and second push rod 422 are installed on the bent axle 300 by the single hole axle journal end 414 on first push rod 412 and the twoport axle journal end 424 on second push rod 422.Single hole axle journal end 414 is positioned at the centre of twoport axle journal end 424 and coaxial with a pair of coaxial aperture 425.Second collar bearing 362 is slidingly installed in the single hole 415 and coaxial aperture 425.The 4th nested 342 on the three-crankshaft parts 340 is installed in second collar bearing 362.In the 3rd nested 336 the 4th nested 342 of being installed on the three-crankshaft parts 340 on second crankshaft component 330, assembling is finished.First push rod 412 and second push rod 422 just share the public axle journal 312 on the bent axle 300.Above the scheme characteristics be to have saved other fastening pieces such as bolt, increased reliability and the performance of assembly.
Further, in a scheme of the present invention, the length of first push rod 412 and second push rod 422 is approximately 5 with the crank throw ratio.With respect to traditional motor, relatively large like this ratio can reduce lateral stress and the frictional loss between first inner carrier 120 and second inner carrier 220 and inner surface of cylinder liner 139 and 239.Typical and comparatively ideal ratio ranges is 3.2 to 3.8.
Further, first pull bar 411 and second pull bar 421 bear from first outer piston 110 shown in the prior figures 1 and the pulling force of second outer piston 210, and also therefore are referred to as pull bar.First pull bar 411 and second pull bar 421 are arranged on the bent axle a pair of public outer piston axle journal 311 on 300, namely on the so-called pull bar.
Further, in the solution of the present invention, first pull bar 411 and second pull bar 421 are in same common plane.Allow the scheme of first pull bar 411 and second pull bar, 421 co-planar arrangement equally also to allow their coaxial arrangement in the above.In a scheme, first pull bar 411 has a single hole axle journal end 416.Have above the single hole axle journal end 416 one with the first and the 3rd collar bearing 361 and 363 among a bearing rotating ring around, close-fitting single hole 417.
Further, a diplopore axle journal end 426 is arranged above second pull bar 421.Diplopore axle journal end 426 comprises a pair of tang 428.Have on each tang 428 one with the first and the 3rd collar bearing 361 and one of 363 rotating rings around, close-fitting coaxial aperture 427.Tang 428 is separated intended distance with the single hole axle journal end 416 of first pull bar 411 that is slidingly matched.The single hole axle journal end 416 of first pull bar 411 and second pull bar 421 and the diplopore axle journal end 426 on second pull bar 421 are connected on the bent axle 300.The single hole axle journal end 416 of first pull bar 411 is middle and coaxial with a pair of coaxial aperture 427 on the diplopore axle journal end 426 at the diplopore axle journal end 426 on second pull bar 421.The first and the 3rd collar bearing 361 and one of 363 is slidingly mounted in single hole 417 and the coaxial aperture 427.Second nested 332 on second crankshaft component 330 is installed in first collar bearing 361.In first nested 322 second nested 332 of being installed on second crankshaft component 330 on first crankshaft component 320, assembling is so far finished.One group of first pull bar 411 in the pull bar of the left and right sides and second pull bar 421 are connected on the public axle journal on the bent axle 300 jointly.
Further, similarly, the 5th nested 346 on the three-crankshaft parts 340 is installed in the 3rd collar bearing 363.In the 6th nested 352 the 5th nested 346 of being installed on the three-crankshaft parts 340 on the 4th crankshaft component 350, assembling is so far finished.In the pull bar of the left and right sides another organized first pull bar 411 and second pull bar 421 and is connected jointly on the public axle journal 311 on the bent axle 300.Above the scheme characteristics be to have saved other fastening pieces such as bolt, increased reliability and the performance of assembly.
Further, the solution of the present invention provides quite long first pull bar 411 and second pull bar 421.The length of first pull bar 411 and second pull bar 421 and the ratio between the crank throw are greater than 10.Such configuration more is conducive to reduce lateral stress and frictional loss between first outer piston 110 and second outer piston 120 and inner surface of cylinder liner 139 and 239 with respect to the configuration under the prior art.
The installation normal axomometric drawing of bent axle 300 in the scheme of the present invention as shown in figure 25.The above-described the first, the second and the 3rd collar bearing 361,362 and 363 helps to reduce the axle journal end 416,426 of first pull bar 411, second pull bar 421 and first push rod 412, second push rod 422,414,424 with bent axle 300 on corresponding bearing surface 334,344, the frictional force between 348.The the first, the second and the 3rd collar bearing 361,362 and 363 is demonstrated by way of example, is not limited to this.What can estimate is that the parts of the resistance of reducing friction of other type or method also are operable.Such as but not limited to needle bearing, roller bearing, lubricious and circulating lubrication liquid.
Further, vuilt-up crankshaft 300 makes as the connected element of first pull bar 411, second pull bar 421 and first push rod 412, second push rod 422 and so on along mounted relevant journal motion in advance.So just avoided split connecting rod and the split bearing on the traditional approach.The split connecting rod needs supporting structure and fastening piece just can be assembled to form integral shaft.These parts have all been saved in the present invention.
Further, in the solution of the present invention, vuilt-up crankshaft 300 is made of several subassemblies of assembling subsequently.Usually less subassembly has superiority in manufacture process, as forging machining, fine finishing and other back work.Vuilt-up crankshaft 300 also has superiority aspect weight reduction.Because connecting element does not need fastening piece, can be employed than the simple components of low weight.In addition, for example insert in the process of housing 103 at bent axle 300, the assembling of several subassemblies can be finished.
Further, another characteristics of this programme are: because the power that bent axle 300 need bear reduces, so assembling bent axle 300 can be employed.The elimination of the balance of reciprocating member and uneven combustion force makes on the motor does not almost have force action on the main journal 325 and 355 that supports bent axle 300.Unbalanced force with respect to the conventional engines tons of acts on the bent axle, and this programme does not almost have unbalanced force.Comprise in the minimizing aspect the power and to act on crankshaft main journal 325 and 355 and the minimizing of motor 10 overall fit on power.
Further, on known conventional array or W row motor, unbalanced force on main journal and the bent axle causes moment of torsion by acting on.In this programme, these power almost are eliminated and do not have a central main journal.Having only two main journals 325 and 355 is that bent axle 300 necessity in housing 103 supports.Because numerous parts are by careful arrangement in this programme, crank throw may only be equivalent to about half of crank throw in the conventional design of similar piston stroke.To a certain extent, have benefited from the split movement of all piston strokes, the crank throw that is defined by the crankcase perpendicular to crankshaft center line is reduced.
The positive isometric cutaway view of assembling of the bent axle 300 of a scheme of the present invention as shown in figure 26.The first, the third and fourth crankshaft component 320,340 and 350 also comprises the first, the second and the 3rd fluid passage 329,339 and 359 respectively.The the first, the second and the 3rd fluid passage 329,339 and 359 provides Lubricants and cooling liquid and so on but the fluid that is not limited thereto, makes them promptly by the bent axle die cavity 304 among Fig. 1.Also include axle journal lubrication channel 335,345 and 349 on the bent axle 300.These axle journal lubrication channels 335,345 and 349 are directly carried Lubricants and cooling liquid and so on respectively but the fluid to the first that is not limited thereto, the second and the 3rd journal surface 334,344 and 348.
Further, the main effect of bent axle is the conduction by push rod and pull bar, the to-and-fro motion of piston is converted into rotatablely move.The unbalanced force that acts on the bent axle makes the frictional force between bent axle and its bearing of support increase.Because unbalanced force must mechanically be transferred on the supporting structure of motor in some way, and mechanical structure is must be enough firm in adapting to these active forces, so the existence of unbalanced force also makes engine design complicated.In-line four cylinder motor with a standard is example, from the power of whole four pistons with identical directive effect on bent axle, the pressure of tons of must pass to engine body by crankshaft main journal simultaneously.The in-line four cylinder motor of a standard has five main journals to support bent axle.
Further, because the active force of outer piston is eliminated substantially in every cylinder, so the motor scheme among the present invention can be considered simple crankshaft designs.As first cylinder assembly 100 among Fig. 1, as can be seen, since act on pressure on first inner carrier 120 and first outer piston 110 and combustion power substantially quite and direction opposite, first pull bar 411 of first outer piston, 110 correspondences will produce pulling force at bent axle 300, simultaneously first push rod 412 of first inner carrier, 120 correspondences with roughly the same thrust on bent axle 300.Zuo Yong result produces a very small side direction that rotatablely moves and caused by minute angle difference and the asymmetric timing of piston of first pull bar 411 and first push rod 412 and the unbalanced force of vertical direction at bent axle like this.Therefore the load that acts on crankshaft main journal 325 and 355 is very little.This is also just without any need for central main journal, and makes and compare with the in-line four cylinder machine of similar performance, and frictional loss reduces greatly.
The axle that waits of the motor 14 of the third embodiment of the present invention is surveyed partial sectional view as shown in figure 27.Motor 14 comprises a housing 1103.1100, one of left hand cylinders and left hand cylinder 1100 axial opposed right cylinder 1200 are arranged in this housing and be positioned between the two bent axle 1300.The terminal 1306 and second bent axle end 1307 of first bent axle is arranged on the bent axle 1300.
Further, motor 14 comprises a housing 1103.Housing 1103 comprises 1100, one of left hand cylinders and left hand cylinder 1100 axial opposed right cylinder 1200, and the bent axle 1300 of between layout.What Figure 27 described is that left hand cylinder arrives after the top dead center, during through 270 ° of crank angles, and the situation of motor 14.
Further, left hand cylinder 1100 comprises left side cylinder sleeve 1130, one left sides outer piston 1110 and left side inner carrier 1120.Left side cylinder sleeve 1130 comprises the hole of a left side liner backs 1132 and a definition left side inner surface of cylinder liner 1139.Left side cylinder sleeve 1130 also comprises a left side cylinder sleeve inlet end 1136 and a left side cylinder sleeve exhaust end 1138.Left side cylinder sleeve inlet end 1136 comprises a row left side suction port 1161, and left side relief opening 1138 comprises a row left side relief opening 1163 simultaneously.
Further, left side outer piston 1110 comprises an outer piston head 1116 and a left side outer piston slide block 1118 relative with outer piston head 1116.Outer piston head 1116 ends at left side outer piston firing level 1111.Left side outer piston head 1116 and left side inner surface of cylinder liner 1139 closely cooperate in left side cylinder sleeve inlet end 1136 places sliding contact.
Further, left side inner carrier 1120 comprises a left side piston head 1126 and a left side inner carrier promote-side 1124 relative with left side piston head 1126.Left side piston head 1126 ends at left side inner carrier firing level 1121.Left side piston head 1126 and left side inner surface of cylinder liner 1139 closely cooperate in left side cylinder sleeve exhaust end 1138 places sliding contact.Left side outer piston 1110, left side inner carrier 1120 and left side cylinder sleeve 1130 have defined firing chamber 1150, left side jointly.
Further, right cylinder 1200 comprises 1230, one right side outer pistons 1210 of a right side cylinder sleeve and right side inner carrier 1220.Right side cylinder sleeve 1230 comprises the hole of a right side liner backs 1232 and a definition right side inner surface of cylinder liner 1239.Right side cylinder sleeve 1230 also comprises a right side cylinder sleeve inlet end 1236 and a right side cylinder sleeve exhaust end 1238.Right side cylinder sleeve inlet end 1236 comprises a row right side suction port 1261, and right side relief opening 1238 comprises a row right side relief opening 1263 simultaneously.
Further, right side outer piston 1210 comprises an outer piston head 1216 and a right side outer piston slide block 1218 relative with outer piston head 1216.Outer piston head 1216 ends at right side outer piston firing level 1211.Right side outer piston head 1216 and right side inner surface of cylinder liner 1239 closely cooperate in right side cylinder sleeve inlet end 1236 places sliding contact.
Further, right side inner carrier 1220 comprises a right side piston head 1226 and a right side inner carrier promote-side 1224 relative with right side piston head 1226.Right side piston head 1126 ends at right side inner carrier firing level 1221.Right side piston head 1226 and right side inner surface of cylinder liner 1239 closely cooperate in right side cylinder sleeve exhaust end 1238 places sliding contact.Right side outer piston 1210, right side inner carrier 1220 and right side cylinder sleeve 1230 have defined firing chamber, right side 1250 jointly.
Further, left side outer piston 1110 and right side inner carrier 1210 are connected a pair of public axle journal on the bent axle 1300, namely on the outer piston axle journal 1311.It is on the inner carrier axle journal 1312 that left side inner carrier 1120 and right side inner carrier 1220 are connected a public axle journal.
Further, the left side outer piston 1110 in the left hand cylinder 1100 is connected on the bent axle 1300 by a pair of left side pull bar 1411 of left hand cylinder one side.Similarly, the right side outer piston 1210 in the right cylinder 1200 is connected on the bent axle 1300 by a pair of right side pull bar 1421.Left and right sides pull bar 1411 and 1421 is connected on left and right sides outer piston 1110 and 1210 by bridge shape structure 1170 and 1270 respectively.Bridge shape structure 1170 and 1270 relies on respectively on the convex surface of left and right sides outer piston 1110 and 1210 on 1172 and 1272.
Further, the left side inner carrier 1120 in the left hand cylinder 1100 is connected on the bent axle 1300 by a left side push rod 1412; Similarly, the right side inner carrier 1220 in the right cylinder 1200 is connected on the bent axle 1300 by a right side push rod 1422.Left and right sides push rod 1412 and 1422 has a left and right sides concave surface terminal 1413 and 1423 respectively.Left and right sides concave surface terminal 1413 and 1423 relies on respectively on the left and right sides convex surface 1125 and 1225 on the promote- side 1124 and 1224 of left and right sides inner carrier 1120 and 1220.
Further, left side outer piston 1110, left side inner carrier 1120 has several left sides outer piston ring 1112 respectively on right side outer piston 1210 and the right side inner carrier 1220, left side inner carrier ring 1122, right side outer piston ring 1212 and right side inner carrier ring 1222.In order to prevent that fluid is by piston head 1116,1118,1216 and 1218 and cylinder sleeve 1115 and 1215 between leak left side outer piston ring 1112, left side inner carrier ring 1122, right side outer piston ring 1212 and right side inner carrier ring 1222 are arranged in firing level 1111 respectively, after 1121,1211 and 1221, and be close to piston head 1116,1118,1216 and 1218.
Further, housing 1103 is used for holding left hand cylinder 1100, right cylinder 1200 and bent axle 1300.Housing 1103 comprises and is used for holding left hand cylinder 1100 respectively, 1104, one right cylinder die cavities 1204 of a left hand cylinder die cavity and a bent axle die cavity 1304 of right cylinder 1200 and bent axle 1300.Left hand cylinder die cavity 1104 has defined a left slider slidingsurface 1106 and has ended at left side housing end plug 1107. Left slider 1118 and 1106 sliding contacts of left slider slidingsurface closely cooperate.Left slider 1118, left side housing end plug and left slider slidingsurface 1106 have defined the first scavenging chamber 1105, left side.
Further, left hand cylinder die cavity 1104, left slider 1118, left side cylinder sleeve 1130 and bent axle 1300 have defined scavenging chamber, second left side 1109 jointly.The second scavenging chamber 1109, left side is open communication with bent axle die cavity 1304, allows fluid freely to pass through thus.
Further, right cylinder die cavity 1204 has defined a right side slide block slidingsurface 1206 and has ended at right side housing end plug 1207.Right side slide block 1218 and right side slide block slidingsurface 1206 sliding contacts closely cooperate.Right side slide block 1218, right side housing end plug 1207 and right side slide block slidingsurface 1206 have defined the first scavenging chamber 1205, right side.
Further, right cylinder die cavity 1204, right side slide block 1218, right side cylinder sleeve 1230 and bent axle 1300 have defined the second scavenging chamber 1109, right side jointly.The second scavenging chamber 1209, right side is open communication with bent axle die cavity 1304, allows fluid freely to pass through thus.Therefore the second scavenging chamber 1109, left side, bent axle die cavity 1304, and the second scavenging chamber 1209, right side is open comes round, fluid can free flow between them.
Further, fluid is the second scavenging chamber 1109 in the left side, bent axle die cavity 1304, and free flow provides a fluid dynamic effect between the second scavenging chamber 1209, right side.In the suitable moment in left and right side suction port opening process, fluid dynamic effect can effectively increase the pressure of scavenging fluid.Description about the motor circulation will be illustrated more clearly in this effect.
Further, suppose that left hand cylinder 1100 is in expansion stroke, wherein bent axle is positioned at lower dead center.In expansion stroke, left side outer piston 1110 promotes to separate with the high-pressure liquid that left side inner carrier 1210 is produced in the 1150 inherent combustion processes of firing chamber, left side.Left side outer piston 1110 and corresponding left side outer piston slide block 1118 are driven towards left side housing end plug direction.This reduces with regard to the volume that causes scavenging chamber, left side 1105, and pressure increases.Under a predetermined pressure, an one-way cock 168(in the left side outer piston slide block 1118 sees Fig. 3) the first scavenging chamber 1105 discharges high-pressure liquid to the second scavenging chamber 1109, left side from the left side.By a predetermined instant in 1105 releasing courses of the first scavenging chamber, left side, left side suction port 1161 is opened at high-pressure liquid, and high-pressure liquid is entered in the firing chamber 1150, left side.
Further, when left hand cylinder 1100 expansion strokes began, right cylinder 1200 was in the beginning of compression stroke.In compression stroke, the direction of left hand cylinder 1100 is driven in other words towards bent axle for right side outer piston 1210 and right side outer piston slide block 1218.This makes that the fluid in the second scavenging chamber 1209, right side is compressed, make fluid pass through the right side suction port when right side suction port 1261 is opened, the while also makes fluid enter the second scavenging chamber 1109, left side by bent axle die cavity 1304 and its second scavenging chamber, left side, 1109 internal pressures is raise.
Further, when left side outer piston 1110 in compression stroke during towards bent axle 1300 motion, the hydrodynamic pressure ripple that the momentum forward that is had by the second scavenging chamber, right side, 1209 inner fluids produces arrives the second scavenging chamber 1109, left side.When left side suction port 1161 was opened, right side outer piston 1210 just in time began to have closed left side relief opening 163 towards the direction motion away from bent axle 1300 thereupon, has also compressed the air inlet fluid in the firing chamber, left side 150 simultaneously simultaneously.The hydrodynamic pressure ripple arrives the left side suction port of opening 1161, has effectively increased the pressure that is used for the air inlet fluid of scavenging.
The partial sectional view of the balance sysmte 500 in the scheme of the present invention as shown in figure 28.Balance sysmte 500 comprises 514, one balancer weights 508 of a balance sysmte housing and a planetary gear set 506.By fastening piece 512 is installed, balance sysmte housing 514 is coupled on the motor body 1103.
Further, planetary gear set 506 comprises a crankshaft gear 518 and a counterrotating gear 519.Balancer weight 508 comprise one coaxial with bent axle 1300, and the axis hole 516 that can rotate freely around crankshaft center line 310.Crankshaft gear 518 is not only coaxial with bent axle 1300, and is bound up on above the bent axle 1300 and by its driving.Crankshaft gear 518 also contacts cooperation with counterrotating gear 519 simultaneously.Counterrotating gear 519 is bound up with balancer weight 508.Give an example, bent axle 1300 drives crankshaft gear 518 motion counterclockwise.Crankshaft gear 518 then drives counterrotating gear 519 and moves clockwise, and counterrotating gear 519 driven equilibriums weigh 508 motions clockwise.
Further, balance sysmte 500 is applicable to the sinusoidal unbalanced force of single order small on abundant counteracting side direction and the vertical direction.This unbalanced force is to be caused by the minute angle difference of first pull bar 411 and first push rod 412 and the asymmetric timing of piston.Balancer weight 508 is installed on the bent axle 1300 with a predetermined angle, with this unbalanced force of abundant counteracting.
Further, the loss of about 50% engine friction is to be caused by the lateral force that first pull bar 411 and 412 motions of first push rod produce.First pull bar 411 and first push rod 412 act on the piston around crankshaft journal rotation separately, in other words, promote piston and make it impact inner surface of cylinder liner 1139 and 1239.The connecting rod of a weak point can produce bigger lateral force, and simultaneously long connecting rod can produce less lateral force (connecting rod of an endless may not can produce lateral force, but at that rate, and its may be infinitely great and have a freight weight limit).Therefore need be under the prerequisite that does not increase connecting rod size and weight, thus the loss of reducing friction of these lateral forces reduced.
Further, therefore push rod 1412 and 1422 load effects that are stressed do not need wrist pin.Wrist pin is also just large-sized by one, and replaces at convex arc fitting surface 1125 and 1225 concave arcs that slide terminal 1413 and 1423.
Be the sectional view that obtains along line of cut 23-23 among Fig. 3 as shown in figure 29.In a scheme of this motor, as seen from the figure, the first bridge shape structure 170 comprise one with second outer piston 210 on convex globoidal 172 be slidingly matched the tight bridge shape concave arc surface 173 of contact.Bridge supports 372 and is used as a needle bearing, to reduce the frictional loss between bridge shape concave arc surface 173 and the convex globoidal 172.
The forward sight schematic diagram of the motor 16 in the scheme of the present invention as shown in figure 31.Motor 16 comprises several and quantity is the opposed pistons opposed cylinder engine cylinder 15 of odd number.Motor 16 among the figure has three cylinders 15; They all are connected on the common crankshaft 300 with radially equally distributed position relation.The characteristics of the motor 16 of this configuration are simply to add extra cylinder 15 and be connected on the common crankshaft 300, to obtain extra power output.Similar with Figure 24, in other scheme, the extra motor 16 that adds is connected on the common crankshaft 300 with parallel relation.
The forward sight schematic diagram of the motor 18 in the scheme of the present invention shown in figure 32.Motor 18 comprises several opposed pistons opposed cylinder engines 11.As seen from the figure, two motors 11 are connected on the common crankshaft 300 with the form of radial equipartition.The motor characteristics of this configuration are simply to add extra cylinder 11 and be connected on the common crankshaft 300, to obtain extra power output.Similar with Figure 24, in other scheme, the extra motor 18 that adds is connected on the common crankshaft 300 with parallel relation.
Further, by removing one or more motors from bent axle, can realize increasing of power decrement.Parallel engine as shown above can provide excess power neatly.
The above is only for preferred embodiment of the present invention, is not so limits claim of the present invention, so the equivalent structure that all utilizations specification of the present invention and diagramatic content are made changes, all is included in protection scope of the present invention.
Claims (6)
1. internal-combustion engine, it is characterized in that, comprise the motor of being formed by first cylinder assembly and second cylinder assembly of opposed layout, described first cylinder assembly and described second cylinder assembly are located in the same housing, described first cylinder assembly mainly is made up of the first cylinder die cavity and first cylinder sleeve be located in the described first cylinder die cavity, described second cylinder assembly mainly is made up of the second cylinder die cavity and second cylinder sleeve be located in the described second cylinder die cavity, be furnished with bent axle between described first cylinder assembly and described second cylinder assembly, opposed first inner carrier and first outer piston of being laid with in described first cylinder sleeve, opposed second inner carrier and second outer piston of being laid with in described second cylinder sleeve, described first inner carrier and described second inner carrier are connected on the same axle journal of described bent axle by first push rod and second push rod respectively, described first outer piston is connected with described bent axle with second pull bar by first pull bar respectively with described second outer piston, and described first cylinder sleeve and described second cylinder sleeve are provided with suction port and relief opening respectively.
2. internal-combustion engine according to claim 1, it is characterized in that, described relief opening is arranged in an end of described first cylinder sleeve and described second cylinder sleeve respectively, described suction port is arranged in the other end of described first cylinder sleeve and described second cylinder sleeve respectively, the layout of described axle journal makes in same cylinder, the described relief opening of motion opening and closing of another piston in the time of the described suction port of the motion opening and closing of a piston.
3. internal-combustion engine according to claim 1 is characterized in that described first cylinder sleeve and described second cylinder sleeve are provided with drive unit, and described drive unit is in order to regulate moving axially of described first cylinder sleeve and described second cylinder sleeve.
4. as internal-combustion engine as described in the claim 2, it is characterized in that, the location arrangements of described first cylinder sleeve, described second cylinder sleeve, described suction port and described relief opening makes described first cylinder sleeve and described second cylinder sleeve be moved in the second place process by primary importance towards described bent axle, has shortened by opening time of the described suction port of described first inner carrier and second inner carrier control or described relief opening and has increased by described first outer piston and the described suction port of described second outer piston control or the opening time of described relief opening.
5. as internal-combustion engine as described in the claim 3, it is characterized in that described drive unit comprises a hydraulic actuator, described hydraulic actuator makes hydrodynamic pressure be transferred to the part cylinder sleeve.
6. as internal-combustion engine as described in the claim 4, it is characterized in that, when described internal-combustion engine is in a predetermined speed, described first cylinder sleeve and described second cylinder sleeve are positioned at described primary importance, when described internal-combustion engine was in the speed that is lower than described predetermined speed, described first cylinder sleeve and described second cylinder sleeve were positioned at the described second place.
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN118030269A (en) * | 2024-02-28 | 2024-05-14 | 佛山仙湖实验室 | Homogeneous charge compression ignition prechamber structure, internal combustion engine and operation method |
| CN118030269B (en) * | 2024-02-28 | 2024-10-29 | 佛山仙湖实验室 | Homogeneous charge compression ignition prechamber structure, internal combustion engine and operation method |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4977864A (en) * | 1979-06-04 | 1990-12-18 | Grant Lloyd L | Diesel engine |
| CN100590305C (en) * | 2003-06-25 | 2010-02-17 | 先进动力科技公司 | Internal combustion engine |
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- 2013-02-26 CN CN2013100606619A patent/CN103291449A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4977864A (en) * | 1979-06-04 | 1990-12-18 | Grant Lloyd L | Diesel engine |
| CN100590305C (en) * | 2003-06-25 | 2010-02-17 | 先进动力科技公司 | Internal combustion engine |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN118030269A (en) * | 2024-02-28 | 2024-05-14 | 佛山仙湖实验室 | Homogeneous charge compression ignition prechamber structure, internal combustion engine and operation method |
| CN118030269B (en) * | 2024-02-28 | 2024-10-29 | 佛山仙湖实验室 | Homogeneous charge compression ignition prechamber structure, internal combustion engine and operation method |
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Application publication date: 20130911 |