CN100408835C - Reciprocating internal combustion engine and its operating method - Google Patents
Reciprocating internal combustion engine and its operating method Download PDFInfo
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- CN100408835C CN100408835C CNB018052142A CN01805214A CN100408835C CN 100408835 C CN100408835 C CN 100408835C CN B018052142 A CNB018052142 A CN B018052142A CN 01805214 A CN01805214 A CN 01805214A CN 100408835 C CN100408835 C CN 100408835C
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D45/00—Electrical control not provided for in groups F02D41/00 - F02D43/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D35/00—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for
- F02D35/0015—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for using exhaust gas sensors
- F02D35/0046—Controlling fuel supply
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D31/00—Use of speed-sensing governors to control combustion engines, not otherwise provided for
- F02D31/001—Electric control of rotation speed
- F02D31/007—Electric control of rotation speed controlling fuel supply
- F02D31/009—Electric control of rotation speed controlling fuel supply for maximum speed control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D37/00—Non-electrical conjoint control of two or more functions of engines, not otherwise provided for
- F02D37/02—Non-electrical conjoint control of two or more functions of engines, not otherwise provided for one of the functions being ignition
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/1497—With detection of the mechanical response of the engine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/20—Output circuits, e.g. for controlling currents in command coils
- F02D2041/202—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit
- F02D2041/2048—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit said control involving a limitation, e.g. applying current or voltage limits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2250/00—Engine control related to specific problems or objectives
- F02D2250/18—Control of the engine output torque
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
- Control Of Driving Devices And Active Controlling Of Vehicle (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
Abstract
An operating method of a reciprocating internal combustion engine in which a net fuel consumption rate is improved by reducing frictional loss power at an indicated power of substantially the same magnitude as a conventional one thereby increasing net output. A reciprocating internal combustion engine having output characteristics generating a maximum indicated power PM when the rotational speed of the engine is a first specified r.p.m. N1 is provided with an output lowering means (26). The output lowering means (26) lowers the engine output when the rotational speed exceeds a second specified r.p.m. N2 so that a required indicated power PS is obtained from the internal combustion engine (output characteristics thereof are shown by a solid line) at the second specified r.p.m. N2 lower than the first specified r.p.m. N1. Since the high rotational speed region out of the engine rotational speed region R where the internal combustion engine is operated is set at an r.p.m. lower than an r.p.m. N3 generated at the required indicated power PS (maximum indicated power Pm) by a prior art (output characteristics thereof are shown by a dashed line), frictional loss power PL at an indicated power of substantially the same magnitude as a conventional one is reduced as compared with a conventional one thus increasing a net output and a net fuel consumption rate.
Description
Technical field
The present invention relates to a kind of reciprocating internal combustion engine and operation method thereof, this reciprocating internal combustion engine has the output characteristics that produces maximum indication output when engine speed is the 1st regulation rotating speed, and can obtain necessary diagram (demonstration) output under the engine speed that is lower than above-mentioned the 1st regulation rotating speed.
Background technique
Past, in reciprocating internal combustion engine with regulation air displacement, the maximum indication output of maximum value of the indication output (indicated output) that the performance curve of when WOT (or) shows during by the full load of internal-combustion engine according to the diameter of the channel diameter of intake and exhaust system, inlet and exhaust valve, and each parameter of constituting the member of internal-combustion engines such as lifting capacity, compression ratio determine.The air displacement of the internal-combustion engine of the maximum of decision indication output is big more then big more like this.In addition, when the different a plurality of internal-combustion engine of contrast air displacement, the engine speed during the indication output that produces identical size is along with the air displacement of internal-combustion engine increases and reduces.In addition, the engine speed that produces maximum indication output is in the high rotary speed area in the engine speed region of operation of combustion engine, and this maximum indication output becomes the promptly necessary indication output of maximum value of the indication output of this internal-combustion engine requirement.
In addition, with in the internal-combustion engine, be provided with when reaching the engine speed of regulation the start clutch that crankshaft torque is delivered to the power transmitting deice that constitutes by speed changer etc. at vehicle.As this start clutch, but occasion at the centrifugal clutch that uses the clutch shoe that constitutes in the centrifugal weight of supporting axle by free swaying ground supporting, use leading (リ one デ ィ Application グ) formula centrifugal clutch, the center of gravity of the clutch shoe of the centrifugal clutch of this look ahead system is in the front side of supporting axle on the gyratory directions of bent axle.In the centrifugal clutch of this look ahead system, frictional force between clutch external member and the clutch shoe makes clutch swingingly act on (to call self-locking action in the following text) towards foreign side radially, is the advantage of clutch capacity so there is the transmission of torque performance that can improve clutch.
In addition, the flywheel of rotor and the revolution change that is used to suppress bent axle of alternator that is engaged in the bent axle of internal-combustion engine is integrally formed into.
, in reciprocating internal combustion engine, take place by the mechanical friction loss of each slide part such as bent axle, crank pin, piston, valve gear and the subsidiary engine that is used to drive various subsidiary engines such as oil pump, generator drives the frictional loss power that loss constitutes.Therefore, effective (just the distinguishing the flavor of) of this internal-combustion engine is output as the value that deducts frictional loss power from indication output.This frictional loss power is corresponding to the increase of engine speed and increase, so, even indication output increases along with the increase of engine speed, but because frictional loss power also increases, so, in the high rotary speed area that is comprising the engine speed that maximum indication output takes place, be difficult to improve significantly unit effectively output and the specific fuel consumption of unit time be effective specific fuel consumption, specific fuel consumption deterioration in the high internal-combustion engine of the operation frequency under above-mentioned high rotary speed area.
In addition, in the centrifugal clutch of look ahead system, when clutch is connected, the sharp increase that is concatenated to form the pushing force of the relative clutch external member of clutch shoe by self-locking action promptly acts on clutch shoe that the decline of the decline of the speed of crankshaft that the sharp increase of the load of bent axle produces and this rotating speed causes promptly acts on the rotating speed of the bent axle that the minimizing of the load of bent axle produces to the minimizing of the pushing force of clutch external member rising, the result makes that the vibration that is referred to as vibration is easy to take place, and this vibration is delivered to passenger by vehicle body.Making low rotation speed area is in the internal-combustion engine of its operation area, the engine speed that start clutch becomes coupled condition is step-down also, so, in order to ensure suitable clutch capacity, need to increase the weight of clutch shoe or clutch shoe is maximized, but this can increase add the shake power of vibration in the vehicle body effect, and the vibration of transmission produces unplessantness displeasure to passenger.
In addition, in order to adjust the degree of flywheel to the inhibition of crank up change, need change and this flywheel all-in-one-piece alternator with flywheel, so, the difficult point that existence can not simply be adjusted, in addition, be in the internal-combustion engine of its operation area making low rotation speed area, also need to suppress to turn round the flywheel of change, but in such occasion, need guarantee to be provided with the space of new flywheel, so, internal-combustion engine is maximized.
Summary of the invention
The present invention makes in view of such situation, its purpose is to provide a kind of operation method of reciprocating internal combustion engine, the operation method of this reciprocating internal combustion engine is set at the high rotary speed area in the internal-combustion engine rotational speed zone of internal combustion engine operation the low rotating speed of engine speed that takes place than maximum indication output, simultaneously, by obtain necessary indication output at this high rotary speed area, can make the frictional loss power of exporting with the indication of identical size of past than lacking in the past, increase effectively output, improve effective specific fuel consumption.
In addition, the object of the present invention is to provide a kind of reciprocating internal combustion engine of carrying out the operation method of above-mentioned reciprocating internal combustion engine, in addition, the objective of the invention is to obtain to reduce the vibration that produces when the start clutch that is made of centrifugal clutch in this reciprocating internal combustion engine connects, obtain the flywheel structure that does not make internal-combustion engine maximize and easily to carry out the adjustment of rotary inertial mass.
According to a form of the present invention, a kind of operation method of reciprocating internal combustion engine is provided, this reciprocating internal combustion engine has the output characteristics that maximum indication output takes place when engine speed is the 1st regulation rotating speed; Wherein, comprise that the output that speed probe with detection of engine rotating speed is provided and motor output is descended reduces the step of the reciprocating internal combustion engine of device, and when surpassing by the detected engine speed of speed probe, reduce the step that output that device makes this internal-combustion engine descends and exports with necessity indication that obtains internal-combustion engine at the 2nd regulation rotating speed by output than low the 2nd regulation rotating speed of the 1st regulation rotating speed.
According to this invention, reduce device by the output of start when surpassing the 2nd regulation rotating speed and export necessary indication of indication output that the 2nd regulation rotating speed lower than the 1st regulation rotating speed that obtains maximum indication output obtains the maximum that internal-combustion engine requires.In the existing reciprocating internal combustion engine, because maximum indication output becomes above-mentioned necessary indication output, so internal-combustion engine of the present invention has the output characteristics that the maximum indication output bigger than above-mentioned necessary indication output can take place, and becomes the big big internal-combustion engine of above-mentioned existing internal-combustion engine of air displacement.In addition, the engine speed low rotating speed of the 2nd regulation rotating speed that above-mentioned existing necessary indication output takes place for the time than the maximum indication output that in existing internal-combustion engine, takes place, the frictional loss power in the above-mentioned necessary indication output lacks than existing internal-combustion engine.Therefore, according to the present invention, even during the high rotary speed area operation of internal-combustion engine in its rotary speed area, the frictional loss power in the indication output also reduces than existing internal-combustion engine, effectively output increase.In addition, according to the present invention, internal-combustion engine has the engine speed region operation of the high rotary speed area lower than existing internal-combustion engine, so, with different by the above-mentioned existing internal-combustion engine that requires high rigidity, high-intensity component parts to constitute, can constitute internal-combustion engine by rigidity and the lower component parts of intensity for the operation that can bear the high rotary speed area of ratio engine rotary speed area.
Like this, above-mentioned necessary indication output obtains by the engine speed lower than existing internal-combustion engine, so, even by the high rotary speed area in the rotary speed area of operation of combustion engine of the present invention, also can reduce the frictional loss power in the indication output, increase effectively output, like this, can improve effective specific fuel consumption, the specific fuel consumption of the internal-combustion engine that the operation frequency of improvement under above-mentioned high rotary speed area is high.In addition, in the present invention, because internal-combustion engine has the engine speed region operation of the high rotary speed area lower than existing internal-combustion engine, so, can constitute internal-combustion engine by rigidity and the lower component parts of intensity, like this, the internal-combustion engine lightweight can be made, also specific fuel consumption can be improved thus.
In the operation method of above-mentioned reciprocating internal combustion engine, engine speed region in the time will being CLV ceiling limit value with the 1st regulation rotating speed is third-class be divided into low rotation speed area, medium speed zone, and the situation of high rotary speed area under, above-mentioned the 2nd regulation rotating speed can be the rotating speed that belongs to above-mentioned medium speed zone or low rotation speed area.
Like this, the much lower rotating speed of engine speed when engine speed becomes than the generation maximum indication output of existing internal-combustion engine, therefore, the frictional loss power that comprises in the indication output of high rotary speed area of the 2nd regulation rotating speed also reduces significantly than existing internal-combustion engine, and effectively output increases respective amount.In addition, internal-combustion engine moves under the engine speed with high rotary speed area more much lower than existing internal-combustion engine, so, can constitute internal-combustion engine by rigidity and the lower component parts of intensity.
Like this, above-mentioned internal-combustion engine is connected to the manual transmission with a plurality of gears, and the 2nd regulation rotating speed can be set corresponding to each gear of manual transmission.Like this, owing to set the 2nd regulation rotating speed corresponding to each gear of moving speed changer, so, can guarantee the driving force of each gear, and, by changing the 2nd regulation rotating speed of each gear, can at random change the driving force when quickening.As a result, the driving force when quickening is changed steadily, realize quickening stably operation.In addition, have different reduction speed ratio gear car type driving force guarantee and adjustment that the driving force when quickening changes is also carried out easily.
Output reduces device can be by stopping to reduce output to the fuel supply of internal-combustion engine.Like this, compare with the occasion that for example control ignition characteristic reduces motor output, fuel consumption reduces.Output reduces device and also can be undertaken by change or control ignition characteristic.The variation of firing characteristic or control comprise make time of ignition from the best time postpone in advance or light a fire stop or cancelling some igniting.
Internal-combustion engine have the detection of engine rotating speed speed probe, output that motor output is descended reduce device, and control gear, this control gear reduces device by above-mentioned output the motor output of above-mentioned internal-combustion engine is descended when being surpassed than low the 2nd regulation rotating speed of above-mentioned the 1st regulation rotating speed by the detected engine speed of above-mentioned speed probe.
Above-mentioned internal-combustion engine is as the vehicle internal-combustion engine, this internal-combustion engine has bent axle and is engaged in bent axle and has the start clutch of clutch external member, this start clutch can be and drags (イ レ one リ Application グ) formula centrifugal clutch, this drawing type centrifugal clutch has clutch shoe, and this clutch shoe is made of the centrifugal weight that freely swings that is contacted with clutch member when surpassing the engine speed of regulation.
In the drawing type centrifugal clutch, the center of gravity of clutch shoe is in the ratio supporting axle side backward on the gyratory directions of bent axle, so, when clutch shoe touches clutch outer and carries out clutch when connecting from the notconnect state of clutch, frictional force makes clutch shoe inwardly swingingly effect of side towards the footpath.Therefore, the size variation of the pushing force of the relative clutch external member of clutch shoe is littler than look ahead system, can reduce that the speed of crankshaft that occurs causing because of increase that its pushing force increase promptly acts on the load of bent axle repeatedly descends and the decline of its rotating speed causes clutch shoe the minimizing of the pushing force of clutch external member promptly to be acted on the rotating speed amplitude of fluctuation that rising produced of the speed of crankshaft that the minimizing of the load of bent axle causes.
Like this, can reduce vibration, make by the vibration that takes place lessly, alleviate the unplessantness displeasure of the passenger that the vibration of transmission causes the power of shaking that vehicle applies.Even the occasion that the engine speed when clutch connects is lower increases the weight of clutch shoe or clutch shoe is maximized, also can guarantee suitable clutch capacity, and can reduce vibration.
Reciprocating internal combustion engine have be connected in bent axle and also by the driven member of starter motor driving rotational and be in bent axle and above-mentioned driven member between and have an overrunning clutch of outer ring, the outer ring joins the joining portion with the rotor of the rotating alternator of above-mentioned bent axle one dismantledly to, and, can constitute the flywheel that to adjust rotary inertial mass thus from this radially foreign side's extension of joining portion court.
Like this, can under the state of the maximization of avoiding internal-combustion engine, append flywheel is set, can further suppress the revolution change of axle.And the outer ring that constitutes flywheel is detachable in the rotor of alternator, so the adjustment of the rotary inertial mass of flywheel can be carried out simply by only changing the outer ring, can easily adjust the inhibition degree of revolution change.
The outer ring has axial Extreme breadth in the outside of predetermined radius, has the recess of cooperation as the above-mentioned joining portion of an axial end of the rotor of above-mentioned alternator in the inboard of afore mentioned rules radius.Like this, can increase rotary inertial mass, and, be coupled to the recess of outer ring as the joining portion of the axial end of the rotor of alternator, so, can make the axial size when engaging outer ring and rotor reduce the suitable amount that is mated.
Like this, can avoid the maximization of internal-combustion engine, and can increase rotary inertial mass, formation can suppress to turn round the flywheel of change effectively.And, in the inboard of predetermined radius, be coupled to the recess of outer ring as the joining portion of the axial end of the rotor of alternator, so the axial dimension when engaging outer ring and rotor diminishes, and also can avoid the maximization of internal-combustion engine thus.
In the present invention, " axially " refers to the direction of the rotational axis of bent axle, and " radially " refers to that the rotational axis with bent axle is the radiation direction at center.
Description of drawings
Fig. 1 is the major component pie graph of the reciprocating internal combustion engine of the embodiment of the invention.
Fig. 2 is the plane cross section on plane of rotational axis of bent axle that comprises the internal-combustion engine of Fig. 1.
Fig. 3 is that the major component of Fig. 2 is amplified plane cross section.
The IV of Fig. 4 when pulling down the side plate of alternator and overrunning clutch in Fig. 3 is to view.
The V of Fig. 5 when pulling down driving plate in Fig. 2 is to view.
Fig. 6 is the figure of the performance curve of the performance curve of internal-combustion engine of comparison diagram 1 and existing internal-combustion engine.
Embodiment
Below with reference to Fig. 1-Fig. 6 embodiments of the invention are described.
As shown in Figure 1, be applicable to that internal-combustion engine 1 of the present invention is for being equipped on two-wheeled single cylinder overhead camshaft type 4 stroke reciprocating internal combustion engine, with reference to wanting Fig. 1 of portion's pie graph and Fig. 2 as can be seen as it, spark ignition type and water-cooled internal-combustion engine 1 install cylinder 3, cylinder head 4 successively in the upper end of crankcase 2, reach the cylinder head cover (not shown) and become one.But by 1 pair of main bearing 18,19 free rotaring ground supporting bent axle 5, the to-and-fro motion that can be coupled to the piston 6 in the cylinder 3 is transformed into the rotation motion of bent axle 5 with being free to slide by connecting rod 7 at crankcase 2.
As shown in Figure 2, the left shaft end that extends from main bearing 18 towards left of bent axle 5 set gradually from main bearing 18 sides towards left driving sprocket wheel 30, starter motor driven gear 62, and alternator 31. at bent axle 5 engages drive sprocket wheel 30 integratedly, in addition, but at free rotaring ground supporting in the camshaft 32 of cylinder head 4 engagement cam sprocket wheel 33 integratedly, set up timing chain 34 between driving sprocket wheel 30 and cam sprocket wheel 33, camshaft 32 is pressed 1/2 rotating speed driving rotational of bent axle 5.In addition, the left end setting at camshaft 5 drives the cooling waterpump 36 that joins camshaft 32 to by the magnetic joiner 35 that uses permanent magnet.
With reference to Fig. 3 and Fig. 4 as can be known, but as from a plurality of needle rollers 63 free rotaring ground supportings of the small gear 60a of the starter motor 60 starter motor driven gear 62 by the driven member of reduction gear 61 driving rotational by being disposed at this hub portion 62a inner peripheral surface and bent axle 5 outer circumferential faces in bent axle 5.Starter motor driven gear 62 joins bent axle 5 to by the overrunning clutch 64 of known cam type.That is, the outer ring described later 66 of overrunning clutch 64 be connected to alternator 31 by screwed joint to 3 bolt B of 3 screw hole H that are formed at outer ring 66 with the rotating rotor 31b of bent axle 5 one.
Cam retainers 68 (Fig. 4), the side plate 69,70 that limits axial 1 couple who moves of each cam 67 that overrunning clutch 64 comprises circular hub portion 62a as inner ring 65, is disposed at the cam 67 of a plurality of roller shapes with camming surface between the circular outer ring 66, cam 67 is kept mutually in accordance with regulations at interval, the spring 71 that is connected in each cam 67.
Like this, when starting, the revolution of starter motor 60 is delivered to starter motor driven gear 62 from small gear 60a by reduction gear 61, in addition, is delivered to bent axle 5 by overrunning clutch 64 and rotor 31b, and bent axle 5 is driven revolution.Then, internal-combustion engine 1 oneself begins revolution, and when the rotating speed of bent axle 5 surpassed the rotating speed of starter motor driven gear 62, the revolution transmission from bent axle 5 to starter motor driven gear 62 was cut off by overrunning clutch 64.
In addition, alternator 31 has the stator 31a that is fixed in engine hood 37 and surrounds the bowl-shape rotor 31b that this stator 31a foreign side is engaged in bent axle 5 integratedly.Rotor 31b has base portion 31c and bowl-shape magnet holding part 31d; The relative bent axle of this base portion 31c 5 is engaged towards gyratory directions by key, simultaneously, is connected by nut 38 in the axial direction; This magnet holding part 31d is joined to the base portion 31c of this base portion 31c by riveted way.Outer ring 66 is connected to lip part 31c1 as the joining portion of rotor 31b dismantledly by bolt B.
Like this, the external lateral portion 66c of outer ring 66 is positioned at the radially foreign side of lip part 31c1, simultaneously, utilizes the axial space that is present between overrunning clutch 64 and the rotor 31b, can increase axial width, can increase the quality of external lateral portion 66c thus.Therefore, outer ring 66 detachable to the rotor 31b of the rotating alternator 31 of bent axle 5 one, thereby can adjust rotary inertial mass by only changing outer ring 66, and, be configured for controlling the flywheel of the revolution change of bent axle 5.
On the other hand, bent axle 5 from main bearing 19 towards Fig. 2 the periphery of right shaft end of right-hand extension, but the cylindrical member 40 of free rotaring ground supporting in bent axle 5 is set coaxially with the rotational axis L of bent axle 5, main bearing 19 sides at this cylindrical member 40 form actuation gear 41, and the front end on the right side of cylindrical member 40 is provided with start clutch 50.
With reference to Fig. 2 and Fig. 5 as can be known, start clutch 50 is by having with the rotating driving plate 51 of bent axle 5 one and being positioned at driving plate 51 outsides and constituting with the centrifugal clutch of the rotating bowl-shape clutch external member 52 of cylindrical member 40 one.But 3 supporting axles 53 that are fixed in this driving plate 51 respectively free swaying ground supporting constitute by 3 centrifugal weights.At 3 supporting axles 53 that are fixed in this driving plate 51 clutch shoe 54 of constituting by 3 centrifugal weights of free swaying ground supporting respectively.Each clutch shoe 54 has the liner of being made by friction material 55 at its outer side surface, the center of gravity of clutch shoe 54 is in the last position side more backward than supporting axle 53 of gyratory directions A of bent axle 5, when connecting start clutch 50, frictional force makes clutch shoe 54 inwardly swingingly effect of side towards the footpath.Therefore, this centrifugal clutch becomes the centrifugal clutch of so-called dragging (ト レ one リ Application グ) formula.
Start clutch 50 connects when engine speed N surpasses the rotating speed of regulation.Promptly, when engine speed N surpasses the engine speed of regulation, the elastic force of clutch shoe 54 resistance clutch spring 56 under the centrifugal action that produces is with the radially foreign side's swing of supporting axle 53 centers court, be contacted with the inner peripheral surface of clutch external member 52 by liner 55, the connection of beginning start clutch 50, driving plate 51 and clutch external member 52 are turned round integratedly, and start clutch 50 becomes complete coupled condition.
Start clutch 50 forms the clutch shoe 54 that has big quality than the big clutch shoe 54 of existing internal-combustion engine or setting, also can guarantee the bigger centrifugal force of the clutch capacity of reliable transmission of torque when becoming the slow-speed of revolution with the engine speed N when internal-combustion engine 1 in clutch shoe 54 generations.
But with driven gear 43 free rotaring ground supportings of above-mentioned actuation gear 41 engagements as the main shaft 44 of the manual transmission M of engagement type gear-shift transmission often, this driven gear 43 by buffer drive be connected to be located at main shaft 44 protrude into the clutch external member of speed change clutch C of the right part of right-hand (when among Fig. 2, watching) from crankcase 2.Speed change clutch C has the friction type multi-plate clutch that releasing mechanism by driver's operation carries out frictional engagement or engages a plurality of clutch plates of removing.When carrying out frictional engagement under the effect of a plurality of clutch plates in elastic force, the torque of bent axle 5 is delivered to and main shaft 44 one oncoming clutch inner members by the clutch external member, speed change clutch C becomes coupled condition, on the other hand, when removing the frictional engagement of a plurality of clutch plates, the transmission of torque of cut-out from the clutch external member to the clutch inner member, speed change clutch C becomes notconnect state.
The above-mentioned manual transmission M that is configured to bent axle 5 rears at crankcase 2 has main shaft 44 that master gear group 45 is set and the countershaft 46 that pinion group 47 is set, when making speed-changing drum 48 revolutions by not shown speed changing operating mechanism, be engaged in speed-changing drum 48 peripheries cam path range fork on the supporting axle to left and right direction (in Fig. 2) suitably move, the gear that makes the master gear group 45 corresponding with variable speed operation suitably meshes with pinion group 47 gear and carries out speed change.
Axial side at driving plate 51 forms the centrifugal filter 81 that is formed by lid 80 mulched grounds, be blended into the impurity that supplies in the lubricant oil of centrifugal filter 81 through the oil circuit 82 that is communicated in the main passage (not shown) and separated by centrifugal force in centrifugal filter 81, clean lubricant oil supplies to the lubricant housings of crank pin 5a etc. via the oil circuit 83 that is formed at bent axle 5 inside.
In addition, the torque of bent axle 5 is delivered to actuation gear 41 with cylindrical member 40 one from start clutch 50, in addition, be delivered to manual transmission M by 1 grade of reducing gear and the speed change clutch C that is made of actuation gear 41 and driven gear 43, the torque after the speed change is delivered to trailing wheel W from countershaft 46 by 2 grades of reducing gear (not shown)s
R, drive trailing wheel W
RRevolution (with reference to Fig. 1).
Can find out referring again to Fig. 1 and Fig. 2, for internal-combustion engine 1, firing chamber 8 is formed at and piston 6 between cylinder head 4 inlet hole 9 and the exhaust port 10 that is communicated to firing chamber 8 respectively is set, in addition, be provided with firing chamber 8 sides that open and close inlet hole 9 opening intake valve 11 and open and close the exhaust valve 12 of opening of firing chamber 8 sides of exhaust port 10.Intake valve 11 and exhaust valve 12 by the switching in accordance with regulations of the valve gear that constitutes by camshaft 32 and rocking arm (not shown) etc. constantly and lifting capacity and bent axle 5 synchronously drive and drive valve.In addition, reach 8 ground, firing chamber in cylinder head 4 spark plug 13 that is used to make the ignition of mixed gas in the firing chamber 8 is installed.
Upstream side at inlet hole 9 is the opening connection suction tude 14 of cylinder head 4 sides, be provided with towards inlet hole 9 fuelings to form the Fuelinjection nozzle 16 of mixed gas in this suction tude 14, in addition, in the downstream side of exhaust port 10 be the opening connection outlet pipe 15 of cylinder head 4 sides.
At the speed probe 21 that is used for the detection of engine rotational speed N as electric control device (ECU) 20 inputs of the control gear of controlling fuel injection amount and time of ignition, detect the jaw opening sensor 22 of throttle opening, detect the pressure transducer 23 of the suction pressure in closure downstream, detect the temperature transducer 24 of coolant water temperature, and gear position switch 25 grades are as the testing signal of the above-mentioned various sensor 21-25 of the detection device of the running state that detects internal-combustion engine 1, according to these testing signals, press the emitted dose burner oil corresponding from Fuelinjection nozzle 16 with engine operating state, and the high-tension generation that is controlled at spark coil 17 constantly, lighted a fire by the time of ignition corresponding with engine operating state by spark plug 13.
Fig. 6 of the performance curve of (during WOT) as can be known when the full load of internal-combustion engine is shown, air displacement with setting for example the air displacement of 200cc internal-combustion engine 1 as by among Fig. 6 shown in 2 dot and dash line like that, have the output characteristics of output as the peaked maximum indication output PM of the indication output (indicated output) of internal-combustion engine 1 take place when engine speed N is the 6000rpm of the 1st regulation rotational speed N 1.This maximum indication output PM is according to each parameter (diameter and lifting capacity, the compression ratio etc. of channel diameter, intake valve 11 and the exhaust valve 12 of intake and exhaust system) decision of the member that constitutes internal-combustion engine 1.In Fig. 6, the curve PL of solid line illustrates the frictional loss dynamic curve of internal-combustion engine 1.
In the present invention, for having the internal-combustion engine 1 that produces the output characteristics of maximum indication output PM by the 1st regulation rotational speed N 1, less than the 2nd regulation rotational speed N 2 of the 1st regulation rotational speed N 1 for example 3500rpm can obtain the promptly necessary indication output of the maximum value PS of the indication output that internal-combustion engine 1 requires.For this reason, when surpassing the 2nd regulation rotational speed N 2 by the detected engine speed N of speed probe 21 (Fig. 1), from speed probe 21 to electric control device 20 input signals, carry out a series of calculation process corresponding to this signal, the signal that will stop the driving of Fuelinjection nozzle 16 from output reduction device 26 outputs to Fuelinjection nozzle 16, cut-out is from the fuel supply of Fuelinjection nozzle 16, the result, and the output of internal-combustion engine 1 descends.
Above-mentioned the 2nd regulation rotational speed N 2 considers that by being condition with the rotating speed that becomes necessity indication output PS that can obtain internal-combustion engine 1 air displacement and maximum indication output PM are determined.Internal-combustion engine 1 supposition when stopping (engine speed N is 0 (zero)) to stipulating that as the 1st of CLV ceiling limit value the rotary speed area of rotational speed N 1 moves, in addition, with this rotary speed area trisection, be divided into low rotation speed area, medium speed zone, reach high rotary speed area, in this embodiment, the 2nd regulation rotational speed N 2 is made as the engine speed in the medium speed zone that belongs to internal-combustion engine 1.This medium speed zone belongs to the high rotary speed area among the engine speed region R (Fig. 2) of operation of combustion engine 1.
Below, the embodiment's of formation effect and effect as described above are described.
With reference to Fig. 6 as can be known, generation shown by dashed lines respectively have internal-combustion engine 1 air displacement cardinal principle 1/2 air displacement and also produce the output characteristics and the maximum frictional loss dynamic curve of exporting among the Pm that comprises frictional loss power PLm of indicating of the existing reciprocating internal combustion engine of the maximum indication output Pm that equates with necessary indication output PS.Can learn from Fig. 6, rotational speed N 3 1/2 below of the engine speed that obtains necessary indication output PS of internal-combustion engine 1 when promptly the 2nd regulation rotational speed N 2 takes place for maximum indication output Pm in above-mentioned existing internal-combustion engine, in addition, the frictional loss power PLM among necessity of internal-combustion engine 1 indication output PS is below 1/2 of frictional loss power PLm among the maximum indication output Pm of above-mentioned existing internal-combustion engine shown by dashed lines.Compare internal-combustion engine 1 and above-mentioned existing internal-combustion engine as can be known, for the frictional loss power PL in the indication output of identical size, internal-combustion engine 1 lacks than existing internal-combustion engine.When the data of the frictional loss power PL that obtains Fig. 6, in internal-combustion engine 1 and above-mentioned existing internal-combustion engine, the slide part that produces mechanical friction loss is a same area, and in addition, producing subsidiary engine, to drive the subsidiary engine of loss identical.
Like this, for internal-combustion engine 1 with the output characteristics that when engine speed N is the 1st regulation rotational speed N 1, produces maximum indication output PM, when internal-combustion engine 1 is stipulated rotational speed N 1 less than the 1st, belong to the medium speed zone (thereby the engine speed region trisection when the 1st regulation rotational speed N 1 is made as CLV ceiling limit value is divided into low rotation speed area by surpassing, the medium speed zone, the output of start reduces device 26 during and medium speed regional during high rotary speed area) the 2nd regulation rotational speed N 2, can obtain to export PS as necessity indication of the maximum indication output of internal-combustion engine 1 requirements by being lower than the 1st regulation rotational speed N 1 the 2nd more regulation rotational speed N 2 that can obtain maximum indication output PM.In above-mentioned existing internal-combustion engine, maximum indication output Pm necessitates and indicates output PS, so internal-combustion engine 1 has can produce the output characteristics of exporting PM than the big maximum indication of necessity indication output PS, so, become air displacement than the big internal-combustion engine of above-mentioned existing internal-combustion engine.In addition, necessary the 2nd of the output PS that indicates of generation stipulates that rotational speed N 2 is the much lower rotating speed of engine speed N3 when indicating output Pm than generation in above-mentioned existing internal-combustion engine is maximum, and necessity indicates the frictional loss power PLM among the output PS to compare minimizing significantly with above-mentioned existing internal-combustion engine.Therefore, when the high rotary speed area operation of combustion engine 1 in this engine speed region R, the also comparable above-mentioned existing internal-combustion engine of frictional loss power PL in the indication output reduces significantly, effectively output increases corresponding amount, so, effectively specific fuel consumption is improved significantly, also can improve the specific fuel consumption of internal-combustion engine 1 when the operation frequency under the above-mentioned high rotary speed area is high.In addition, internal-combustion engine 1 has the engine speed region R operation of the high rotary speed area more much lower than above-mentioned existing internal-combustion engine, so, with for different by the above-mentioned existing internal-combustion engine that requires high rigidity, high-intensity component parts to constitute for also bearing in the operation of the high rotary speed area of ratio engine rotary speed area R, can constitute internal-combustion engine 1. results by rigidity and the lower component parts of intensity, internal-combustion engine 1 lightweight can be made, also specific fuel consumption can be improved in this point.
When engine speed surpassed the 2nd regulation rotational speed N 2, output reduced the fuel of device 26 sever supplies to internal-combustion engine 1, so, reducing the occasion of motor output with control ignition constantly and compare, fuel consumption reduces, and specific fuel consumption is further improved.
In addition, even internal-combustion engine 1 has the engine speed region R operation of the high rotary speed area more much lower than above-mentioned existing internal-combustion engine, start clutch 50 and the alternator 31 of being located at bent axle 5 work as the rotary inertial mass that appends to bent axle 5, so, can suppress the revolution change of slow-revving bent axle 5, can move reposefully.In addition, internal-combustion engine 1 is because in the rotary speed area operation lower than existing internal-combustion engine, so, start clutch 50 forms greatlyyer than existing internal-combustion engine, or be provided with centrifugal weight with quality bigger than existing internal-combustion engine, with also transmitting torque positively under the slow-speed of revolution, for this reason, can increase rotary inertial mass, further suppress above-mentioned revolution change.
In addition, because start clutch 50 is made of the centrifugal clutch of drawing type, so, the center of gravity of clutch shoe 54 is in ratio supporting axle 53 side backward on the gyratory directions A of bent axle 5, when the clutch that the engine speed that surpasses afore mentioned rules as engine speed N makes start clutch 50 become the liner 55 contact clutch external members 52 of clutch shoe 54 from notconnect state connected, frictional force made clutch shoe 54 inwardly swingingly effect of side towards the footpath.For this reason, the variation of the size of the pushing force of clutch shoe 54 relative clutch external members 52 is compared less with the look ahead system clutch, can reduce that the rotating speed that occurs the bent axle 5 that increase that its pushing force increase promptly acts on the load of bent axle 5 causes repeatedly descends and load that the minimizing of the pushing force of the relative clutch external member 52 of the clutch shoe 54 that the decline of its rotating speed causes promptly acts on bent axle 5 reduces the rotating speed amplitude of fluctuation that the rotating speed rising that causes bent axle 5 is produced, reduce vibration, make by add the shake power of the vibration that produces to diminish, alleviated the unplessantness displeasure of the vibration of transmission the passenger generation to vehicle.
The 2nd regulation rotational speed N 2 belongs to above-mentioned medium speed zone, and be that maximum rotating speed below 1/2 of indicating the engine speed N3 when exporting Pm takes place in above-mentioned existing internal-combustion engine, like this, even the occasion of operation of combustion engine 1 in belonging to the engine speed region R of the rotary speed area lower than the past, also can increase the weight of clutch shoe 54, or clutch shoe 54 is maximized, guarantee suitable clutch capacity, and can reduce vibration.
The outer ring 66 that starter motor driven gear 62 is joined to the overrunning clutch 64 of bent axle 5 utilizes and is present in the radially space of foreign side, existing unidirectional outer ring, join the lip part 31c1 of the rotor 31b of alternator 31 to, simultaneously, more be formed extended at both sides than lip part 31c1 towards foreign side radially, constitute flywheel by this outer ring 66, so, can when avoiding internal-combustion engine 1 to maximize, append flywheel, can further suppress the revolution change of bent axle 5.And the outer ring 66 that constitutes flywheel can be in the rotor 31b of alternator 31 mounting or dismounting, so the adjustment of the rotary inertial mass of flywheel only can realize simply by changing outer ring 66, can easily adjust the inhibition degree of revolution change.
The radially foreign side of the lip part 31c1 that utilizes at rotor 31b in the outer ring 66 of radially maximizing is present in axial space, has axial Extreme breadth at the external lateral portion 66c that is formed into the afore mentioned rules radius outside that forms stepped part 66b, so, the maximization of internal-combustion engine 1 can be avoided, and rotary inertial mass can be further increased.
In addition, the 2nd regulation rotational speed N 2 belongs to above-mentioned medium speed zone, and be in above-mentioned existing internal-combustion engine, to produce maximum rotating speed below 1/2 of indicating the engine speed N3 when exporting Pm, like this, even occasion at the engine speed region R operation of combustion engine that belongs to the rotary speed area lower than the past, also can utilize the outer ring 66 of overrunning clutch 64 to avoid the maximization of internal-combustion engine 1, and, can set up flywheel, increase rotary inertial mass, formation can suppress the flywheel of the revolution change of bent axle 5 effectively.
And, inboard at the afore mentioned rules radius, be coupled to the recess 72 of outer ring 66 as the lip part 31c1 of the axial end of the rotor 31b of alternator 31, so, amount (step amount) corresponding to this cooperation, axial size decreases when outer ring 66 is engaged with rotor 31b also can be avoided the maximization of internal-combustion engine 1 thus.
Below, the embodiment who constitutes for a part that has changed the foregoing description only illustrates about altered formation.
In the above-described embodiments, the 2nd regulation rotational speed N 2 is for belonging to the rotating speed in medium speed zone, but as long as the 2nd regulation rotational speed N 2 is less than the 1st regulation rotational speed N 1, its size determines according to the air displacement and the maximum indication output PM of internal-combustion engine 1 as described above, like this, compare with the foregoing description,, also can obtain the improvement of effective specific fuel consumption, the effects same as the previously described embodiments such as lightweight of internal-combustion engine 1 even the light-weighted degree of the degree of the improvement of specific fuel consumption and internal-combustion engine 1 reduces.
In addition, also can be as shown in Figure 1, the gear position switch 25 of the shift position that detects manual transmission M is set, set the 2nd regulation rotational speed N 2 corresponding to each gear of the manual transmission M of gear with the 1st speed to the 4 speed.At this moment, guarantee that at each gear necessary driving force ground sets each the 2nd regulation rotational speed N 2, the 2nd regulation rotational speed N 2 of the 1st speed that makes the reduction speed ratio maximum is for the highest, below, along with reduction speed ratio reduces, the 2nd regulation rotational speed N 2 that makes each gear is step-down successively.
Like this, set the 2nd regulation rotational speed N 2 corresponding to each gear of manual transmission M, so, can guarantee the driving force of each gear, and can at random change driving force when quickening by the 2nd regulation rotational speed N 2 that changes each gear, like this, the driving force when quickening is changed gently, realize quickening stably operation.In addition, can easily guarantee the driving force of the vehicle body of gear and the driving force of adjusting when quickening changes with different reduction speed ratio.
In the above-described embodiments, output reduces device 26 control Fuelinjection nozzles 16, fuel shutoff, but fuel injection amount is reduced, in addition, also can be by making time of ignition in advance or postpone from optimum igniting constantly, or light a fire and stop or cancelling some igniting, thereby the motor output of internal-combustion engine 1 reduced.Carrying out the minimizing of fuel injection amount, the occasion that shifts to an earlier date or postpone, cancel some igniting of time of ignition by output reduction device 26, the decline of the output when surpassing the 2nd regulation rotational speed N 2 as by shown in 1 pecked line of Fig. 6 like that, it is mild to compare when carrying out fuel cut-off, in addition, in these occasions, also can be by fuel cut-off or igniting stop to limit maximum speed.
Big and the less occasion of necessary indication output PS in the air displacement of internal-combustion engine 1 also can make the engine speed N of the 2nd regulation rotational speed N 2 for the low rotation speed area that belongs to the engine speed region when the 1st regulation rotational speed N 1 is made as CLV ceiling limit value.In addition, internal-combustion engine 1 also can be multi cylinder, and vehicle also can be two-wheeled vehicle in addition.
In the above-described embodiments, 66 form recesses 72 in the outer ring, but this recess 72 can not have yet, and in addition, the afore mentioned rules radius is set at the radius of lip part 31c1 of the base portion 31c of rotor 31b, but the radius of also comparable lip part 31c1 is big.
Claims (9)
1. the operation method of a reciprocating internal combustion engine, this reciprocating internal combustion engine have the output characteristics that maximum indication output takes place when engine speed is the 1st regulation rotating speed; It is characterized in that this method comprises:
The output that speed probe with detection of engine rotating speed is provided and motor output is descended reduces the step of the reciprocating internal combustion engine of device, and
Reducing output that device makes this internal-combustion engine by described output when being surpassed than low the 2nd regulation rotating speed of described the 1st regulation rotating speed by the detected engine speed of described speed probe descends with the step of necessity indication output of obtaining described internal-combustion engine at the 2nd regulation rotating speed.
2. the operation method of reciprocating internal combustion engine according to claim 1, it is characterized in that: the engine speed region in the time will being CLV ceiling limit value with described the 1st regulation rotating speed is third-class be divided into low rotation speed area, medium speed zone, and the situation of high rotary speed area under, described the 2nd regulation rotating speed is the rotating speed that belongs to described medium speed zone or low rotation speed area.
3. the operation method of reciprocating internal combustion engine according to claim 1 is characterized in that:
Described internal-combustion engine is connected to the manual transmission with a plurality of gears,
Described the 2nd regulation rotating speed can be set corresponding to each gear of described manual transmission.
4. the operation method of reciprocating internal combustion engine according to claim 1 is characterized in that: described output reduces device and stops fuel supply to internal-combustion engine.
5. the operation method of reciprocating internal combustion engine according to claim 1 is characterized in that: described output reduces the firing characteristic that device changes described internal-combustion engine.
6. reciprocating internal combustion engine, described reciprocating internal combustion engine has bent axle, and described reciprocating internal combustion engine has the output characteristics that produces maximum indication output when engine speed is the 1st regulation rotating speed; It is characterized in that this reciprocating internal combustion engine has:
The detection of engine rotating speed speed probe,
The output that motor output is descended reduces device, reaches
Control gear,
Described control gear reduces device by described output the motor output of described internal-combustion engine is descended when being surpassed than low the 2nd regulation rotating speed of described the 1st regulation rotating speed by the detected engine speed of described speed probe.
7. reciprocating internal combustion engine according to claim 6 is characterized in that:
Described internal-combustion engine is as the vehicle internal-combustion engine, and this internal-combustion engine has the start clutch that is engaged in described bent axle and has the clutch external member,
This start clutch is the drawing type centrifugal clutch, and this drawing type centrifugal clutch has clutch shoe, and this clutch shoe is made of the centrifugal weight that freely swings that is contacted with described clutch member when surpassing the engine speed of regulation.
8. reciprocating internal combustion engine according to claim 7 is characterized in that, this reciprocating internal combustion engine has:
Be connected in described bent axle and also by the driven member of starter motor driving rotational and
Be between described bent axle and the described driven member and have the overrunning clutch of outer ring,
Described outer ring joins the joining portion with the rotor of the rotating alternator of described bent axle one dismantledly to, and extends from this joining portion towards foreign side radially, constitutes the flywheel that can adjust rotary inertial mass thus.
9. reciprocating internal combustion engine according to claim 8, it is characterized in that: described outer ring has axial Extreme breadth in the outside of predetermined radius, has the recess of cooperation as the described joining portion of an axial end of the rotor of described alternator in the inboard of described predetermined radius.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP388296/00 | 2000-12-21 | ||
| JP388296/2000 | 2000-12-21 | ||
| JP2000388296 | 2000-12-21 | ||
| JP2001195348A JP3642418B2 (en) | 2000-12-21 | 2001-06-27 | Reciprocating internal combustion engine and method for operating the same |
| JP195348/01 | 2001-06-27 | ||
| JP195348/2001 | 2001-06-27 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1404549A CN1404549A (en) | 2003-03-19 |
| CN100408835C true CN100408835C (en) | 2008-08-06 |
Family
ID=26606237
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB018052142A Expired - Fee Related CN100408835C (en) | 2000-12-21 | 2001-11-20 | Reciprocating internal combustion engine and its operating method |
Country Status (10)
| Country | Link |
|---|---|
| EP (1) | EP1344925A4 (en) |
| JP (1) | JP3642418B2 (en) |
| KR (1) | KR100761188B1 (en) |
| CN (1) | CN100408835C (en) |
| AR (1) | AR032206A1 (en) |
| BR (1) | BR0108515B1 (en) |
| MY (1) | MY134561A (en) |
| TR (1) | TR200201967T1 (en) |
| TW (1) | TW536581B (en) |
| WO (1) | WO2002052140A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7309208B2 (en) * | 2005-02-22 | 2007-12-18 | General Electric Company | Turning gear drive system |
| JP4859042B2 (en) * | 2006-08-31 | 2012-01-18 | 本田技研工業株式会社 | Idle stop control device |
| WO2017127219A1 (en) | 2016-01-19 | 2017-07-27 | Eaton Corporation | Cylinder deactivation and engine braking for thermal management |
| EP3500745A1 (en) * | 2016-08-17 | 2019-06-26 | Eaton Intelligent Power Limited | Friction mitigation in cylinder deactivation |
| US11187162B2 (en) | 2016-08-17 | 2021-11-30 | Eaton Intelligent Power Limited | Extended coast and controlled deceleration using cylinder deactivation |
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| JPH0932602A (en) * | 1995-07-18 | 1997-02-04 | Nissan Motor Co Ltd | Engine output controller |
| JPH10159973A (en) * | 1996-11-27 | 1998-06-16 | Honda Motor Co Ltd | Vehicular power transmission |
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| EP1048845A1 (en) * | 1999-04-27 | 2000-11-02 | Honda Giken Kogyo Kabushiki Kaisha | Starter/generator for motor vehicles |
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| JPH05195849A (en) * | 1992-01-24 | 1993-08-03 | Toyota Motor Corp | Fuel cut controller for internal combustion engine |
| US5445121A (en) | 1992-11-24 | 1995-08-29 | Yamaha Hatsudoki Kabushiki Kaisha | Engine operational control unit |
| GB9312640D0 (en) * | 1993-06-18 | 1993-08-04 | Gen Motors Coropration | Traction controller |
| JPH07166906A (en) * | 1993-12-14 | 1995-06-27 | Nissan Motor Co Ltd | Acceleration slip controller by fuel cutting and ignition timing change |
| JPH11159371A (en) | 1997-11-25 | 1999-06-15 | Sanshin Ind Co Ltd | Direct cylinder injection type engine |
| JP4060517B2 (en) * | 2000-07-18 | 2008-03-12 | 本田技研工業株式会社 | Engine speed control device |
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2001
- 2001-06-27 JP JP2001195348A patent/JP3642418B2/en not_active Expired - Fee Related
- 2001-11-20 EP EP01982859A patent/EP1344925A4/en not_active Withdrawn
- 2001-11-20 WO PCT/JP2001/010113 patent/WO2002052140A1/en active Application Filing
- 2001-11-20 TR TR2002/01967T patent/TR200201967T1/en unknown
- 2001-11-20 BR BRPI0108515-8A patent/BR0108515B1/en not_active IP Right Cessation
- 2001-11-20 KR KR1020027010788A patent/KR100761188B1/en not_active IP Right Cessation
- 2001-11-20 CN CNB018052142A patent/CN100408835C/en not_active Expired - Fee Related
- 2001-11-30 TW TW090129711A patent/TW536581B/en not_active IP Right Cessation
- 2001-12-13 MY MYPI20015683A patent/MY134561A/en unknown
- 2001-12-20 AR ARP010105937A patent/AR032206A1/en active IP Right Grant
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0932602A (en) * | 1995-07-18 | 1997-02-04 | Nissan Motor Co Ltd | Engine output controller |
| JPH10159973A (en) * | 1996-11-27 | 1998-06-16 | Honda Motor Co Ltd | Vehicular power transmission |
| EP1010880A2 (en) * | 1998-12-17 | 2000-06-21 | Honda Giken Kogyo Kabushiki Kaisha | Apparatus for controlling internal combustion engine |
| EP1048845A1 (en) * | 1999-04-27 | 2000-11-02 | Honda Giken Kogyo Kabushiki Kaisha | Starter/generator for motor vehicles |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2002250245A (en) | 2002-09-06 |
| TW536581B (en) | 2003-06-11 |
| EP1344925A1 (en) | 2003-09-17 |
| JP3642418B2 (en) | 2005-04-27 |
| AR032206A1 (en) | 2003-10-29 |
| BR0108515B1 (en) | 2009-05-05 |
| KR20020081335A (en) | 2002-10-26 |
| TR200201967T1 (en) | 2003-05-21 |
| BR0108515A (en) | 2003-04-15 |
| EP1344925A4 (en) | 2010-09-15 |
| MY134561A (en) | 2007-12-31 |
| CN1404549A (en) | 2003-03-19 |
| KR100761188B1 (en) | 2007-09-21 |
| WO2002052140A1 (en) | 2002-07-04 |
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