TW575716B - Engine starting apparatus - Google Patents

Description

D / D / W V. Description of the invention (1) Man Yimeng's dry street This invention relates to the inertial force and starter motor that start the engine by starting the engine starting device, especially Θ = horse f to make the crankshaft move ：: f is an engine starting device which can also have good engine & torque even when using a turning system including crankshaft, even a low torque starting motor. When the engine is started, the crank is from _ (the maximum value before TDO (the maximum that the piston can reach the compression top dead center just after it reaches the maximum). In order to overcome this TDC, in the past, a larger torque than the torque, that is, the stop torque It is the largest crankshaft _ starter motor mentioned above. The startability of the engine is to start this, the starter motor is straight, 4 =: drive = the larger the moment, the more the moment is increased. As part of the inertia mass + + ^, when the starter motor rotates the motor Special: Acceleration: Dynamic; To adopt a large starting torque with large driving torque, for example, the driveability of a boat / speed i moving 4 has to be reduced. Its maximum crankshaft 'moment reaches: 4 strokes below 100cc used by m The engine starts at 1.3kgfm. However, the maximum inertia when the motor is directly connected to the crankshaft, the inertia is far greater than the optimal inertial mass:! · Sangbury is 40kgcm, and the driveability is $ py kgcm. That is, The engine startability of the present invention is difficult to get the best of both worlds. The engine starting device is based on the problems of the conventional technology of the rabbit and provides a kind of starter motor that can start the engine. Starting and driving can be the best of both worlds. Page 5 C: \ 2D-00DE \ 9] -07 \ 9] 10759] .ptd ^ / 5716 5. Description of the invention (2) Reversing to the stated position in order to achieve the above purpose ' It is provided with the maximum torque of the starting horse after the stoppage is required. In addition to the large crankshaft torsion compression stroke based on the above-mentioned special speed 'to obtain a relatively large torque combined force, as long as the maximum torsional compression stroke can be achieved. Invention of f This is a necessary sign that the crankshaft is up to the reverse to make the moment of the engine large, in which the moment of inertia reaches the lowest moment than the lowest engine, and even the engine is automatically opened, and then the body frame is placed in the car body. Refer to the figure of the moving device with the engine stopped and the start operation started. The front and the body frame of the car (both are not shown in the figure, the front part of the body is extended ^ Ming eight features: after the engine stops, the crank The engine starting rotation of the engine starts = and the starting motor of the reverse rotation, and the reverse rotation control mechanism of the engine stop. When the aforementioned starting motor starts, its piston must cross the compression stroke below about 60%, and when the piston is cranking the crankshaft, The piston can be fully applied until the compression stroke is reached. 'This inertial force and the driving torque of the starter motor increase the crankshaft torque. Even if the crankshaft torque of the starter motor is small, the piston can leapfrog the invention in detail. Figure 1 In order to apply the present invention to the entire side view of a speed Keda type two-wheeled vehicle, the vehicle automatically stops, the engine can be triggered when the vehicle stops, 'σ if the throttle handle is opened, or the start switch is operated, the The starter motor is automatically driven so that the rear part of the body is connected via a low floor portion 4, and the frame is composed of a bottom pipe 6 and a main pipe 7. The fuel tank is supported by the main pipe 7, and a seat cushion 8 is arranged above it. It is supported by the shaft of the steering head 5 and a handlebar front fork 12 is provided above it. The lower end shaft supports the front wheel FW. C: \ 2D-C0DE \ 91-07 \ 91107591.ptd Page 6 575716 V. Description of the invention (3) The upper part is covered with the handle of the instrument panel. The lower end of the standing part of the supervisor 7 = the support stand 15, and the support stand 15 is free via the link member 16. Shake while the connection is supported. The suspension bracket 18 of the swinging device 2. In the swing Pei set 2, the front Pei contains a single-cylinder 50cc 4-stroke engine E. This engine E constitutes a belt-type stepless speed changer to the rear, and its rear part supports the rear wheel M through a reduction mechanism 9 provided by a centrifugal clutch. The upper end of the speed reduction mechanism 9 and the upper curved portion of the main pipe 7 "Jian Chang Yan Shi has a back cushion 3". In the front part of the swing device 2, a suction from the engine: 19: a connected carburetor 17 and an air filter state 14 connected to the same carburetor 17 are provided. FIG. 2 is a cross-sectional view of the aforementioned swinging device 2 cut along the crankshaft 201, and FIG. 3 is an enlarged view of a part thereof, showing the same component number as the same or the same as the above. The swinging device 2 is covered by a crankcase 202 composed of left and right crankcases 202L and 202R, and a crankshaft 201 is rotatably supported by a vehicle 280, 209 fixed to the crankcase 2021 ?. The crankshaft 200 is connected to a connecting rod (not shown) via a crankpin 213. The left crankcase 202L also serves as a belt-type stepless gearbox. A crankshaft 201 extending to the left curve 2202L is provided with a rotatable belt drive wheel m. The belt driving wheel 210 is composed of a fixed-side pulley half 21L and a movable-side pulley half 21 0R. The left-side end of the fixed-side pulley half 21 is fixed via the hub 2 η, and on its left side is a movable-side pulley half 2i. The r slot is fitted on the crankshaft 201 'and can approach or leave the fixed side pulley half 21. A ¥ -shaped belt 212 is hung between the two pulley halves 210L and 210R. Page 7 c- \ 2D-CODE \ 91-07 \ 91107591.ptd 575716 V. Description of the invention (4) The right side of the movable side pulley half 21 〇R, the cam plate 215 is fixed to the crankshaft 201, and the outer peripheral end is provided with The slider 215 is freely slidably coupled to a cam plate slider 210Ra formed at the outer peripheral end of the movable side pulley half 2 1 0R and formed in the axial direction. The cam plate 2 1 5 of the movable side pulley 2 1 5 has a tapered surface 4 inclined toward the movable side pulley half 2 near the outer periphery. The space between the inclined surface and the half of the movable side pulley 2 1 0R accommodates a dry clock. Ball 2 1 6. When the rotation speed of the crankshaft 201 increases, the aforementioned dry hammer ball 216, which is located between the movable side pulley half 21 0R and the cam plate 215 and rotates together, moves in the centrifugal direction due to centrifugal force, and the movable side pulley half 21 〇R moved to the left by the dry hammer ball 216 and approached the fixed-side pulley half 210L. As a result, the v-belt 212 sandwiched between the two pulley halves 21oL and 2ior moved toward the centrifugal direction, and it hung The upper diameter becomes larger. A passive leather = wheel (not shown) corresponding to the aforementioned belt drive wheel 2 丨 0 is provided in the rear part of the vehicle, and the v-belt 212 is hung on this passive pulley. It is driven by two leather τ The power of the mechanism 'engine ^; is automatically adjusted and transmitted to the centrifugal separator 5, and the rear wheel RW is driven through the aforementioned reduction mechanism 9. etc. ::: Shaft phase 2 0 2R' g has a starter motor and AC generator combination Motive and generator (from ACG starter M eACG As for the motive, the outer rotor 6 is fixed with the thread 2 53 at the sloping cone of the crankshaft 201. The stator 5 () provided on the inner peripheral side of the outer rotor 60 is bolted at 279 to the worm feather and has a heat of 282, The radiator 282 is covered with a fan cover 281. As shown in the enlarged view in FIG. 3, the sensor box 28 is intended to be inserted into the sensor box 28 in the inner periphery.

575716 V. Description of the invention (5) In the sensor box 28, a rotor angle sensor (magnetic pole sensor) 2 9 and a pulse sensor (ignition) are provided at equal intervals along the outer periphery of the hub 60a of the outer rotor 60. Pulser) 30. The rotor angle sensor 29 is a user for energizing the stator coil of the ACG starter 1, and is provided corresponding to each of the U-phase and W-phase of the ACG starter 1. The ignition pulsator 3 is used as the engine and fire control, but only one. Both the rotor angle sensor 29 and the ignition pulser 30 may be composed of a Hall IC or a magnetic resistance (MR) element. The wires of the rotor angle sensor 29 and the ignition pulser 30 are connected to the substrate 31, and even the substrate 31 is combined with the wiring conductor 32. In the outer periphery of the hub 6 o a of the outer rotor 60, a two-stage magnetic ring 33 for imparting magnetism to each of the rotor angle sensor 29 and the ignition pulser 30 is embedded. One of the magnetic bands corresponding to one of the magnetic rings 33 of the rotor angle sensor 29 corresponds to the magnetic pole of the stator 50 and is 30 ° in the circumferential direction. The N and S poles which are alternately arranged for the interval form, and among the magnetic strips corresponding to the other side of the magnetic ring 33 of the ignition pulser 30, one of them is at 15 in the circumferential direction. To 40. The range forms a magnetic portion. The aforementioned ACG starter i is the function of a starter motor (synchronous motor) when the engine is started. It uses the current supplied from the battery to drive the crankshaft 2 (Π) to start the engine; after the engine starts, it has the function of a synchronous generator. The electric current after power generation charges the battery and supplies the electric current of each electric part. Returning to FIG. 2 'in the crankshaft 201', a sprocket 231 is fixed between the aforementioned ACG starter j and the bearing 209, and this sprocket 231 +, It is attached to drive the convex = shaft (not shown) from the crankshaft 201. Moreover, the aforementioned key wheel 231 and the gear m form a body. The gear 232 is used to transmit power to the circulating lubricant system C: \ 2D-mDE \ 91 -07 \ 91107591 .ptd Page 9 575716 V. Description of the invention (6) PU 0 Figure 4 is a block diagram of an electrical equipment system containing ACG starter 1. ECU3 contains ACG starter 1. The generated three-phase AC full-wave rectification is a three-phase full-wave rectifier bridge circuit 300, and the output of the full-wave rectifier bridge circuit 300 is limited to a predetermined adjustment voltage (adjusting operating voltage: for example: 1 4 · 5 V) Adjuster 1 0 0. Even 'ECU3 of this embodiment' has Immediately after the engine stops, the crankshaft can be reversed to a predetermined position to improve the startability of the next engine. The turning control unit 7 0 0 ′ and the starting control unit that reduces the crankshaft torque at the start of the engine 5 0 0,

The engine control unit 400 for increasing the power generation amount in a predetermined low rotation range and the number of engine revolutions connects the ignition coil 21 to ^ 1 ^ 3 ', and connects the star base 22 to the secondary side of the ignition coil 21. In addition, the ECU 3 is connected to an influenza sensor 23, a fuel sensor 24, a seat switch 25, an idle switch 26, a cooling water temperature sensor 27, a rotor angle sensor 29, and an ignition pulser. 3 〇, the detection signal from each unit is input to ECU3. Furthermore, ECU3, ϋ τ are reversely connected to start relay 3 4, start switch 3 5, 2 off 36, 37, standby indicator 38, fuel indicator 39, speed sense °°, and headlight 42. A timing switch 43 is provided in the headlight 42.

^ Ϊ 4 each through the main fuse 44 and the main switch 45 by the battery 2 " Another ^ t still the battery 2, directly connected to the ECU through the start relay 34 =, the surface of the electricity also has no way through the main switch 45, Only through the main reading, next to the above-mentioned ECU3, < the swing control unit 700, the start control name

575716 V. Description of Invention (7) 500 and the structure and block diagram of the power generation control unit 400 are described. In the swing control unit 700, the output signal of the stage discriminating unit 73 and 29 will stab the crankshaft 201 according to the rotor angle, and the ignition pulser 3 will be ignited. Happened ... is the baseline phase_. ) To determine the detection timing. The phase passing time detection unit 74 determines the time from the new phase to the time when the next phase is determined based on the previous phase. The reversing control unit 75 generates a reversing drive command based on the previous stage: = another = and the pass detected by the time detecting unit 74 at the aforementioned stage = time Δ t η. The duty ratio setting unit 72 controls the duty ratio of the idle voltage of each power fet supplied to the full-wave rectifier bridge circuit 300 based on the discriminated name of the aforementioned stage discrimination unit 73. The driver 80 drives each of the power FETs of the full-wave rectifier bridge circuit 300 with the previously set load ratio. ... It is explained that the operation of the swing-back control unit 700 will be described with reference to the flow of Fig. 6 and the operation explanatory diagram of Fig. 7. α Figure 7 (a) shows the crankshaft torque required for the reverse rotation of crankshaft 201 (the relationship between the negative reversal and the crankshaft angle. The crankshaft torque rises sharply just before the compression top dead center (reverse time). The same figure (b) shows the crankshaft angle. The relationship with the stage, the graph (C) shows the change in the angular velocity of the crankshaft when the reversal is not shown. When the engine is stopped at step S61, the current stage that has been identified and learned is referred to in steps S62, S63, and the stage discrimination unit 73. This If the stage is any of stages # 0 to # 11, step S64 is performed. If it is ^

C: \ 2D-CODE \ 91-07 \ 91107591.ptd Page 11 575716 V. Description of the invention (8) Any one of paragraphs # 12 ~ # 32, then proceed to step mail (other than paragraphs # 33 ~ # 35), then proceed to step ⑽. In step s64, ⑽ sets the load S65 of the driving pulse in the load ratio setting section 72 to 80%. The dynamic control of such a load ratio is described in detail below. The angular velocity of the crankshaft at 200 rpm during reverse rotation is reduced sufficiently before the crankshaft torque compresses the upper dead center to a considerable angle (when turning). At the same time, the angular control is performed so that Fast reversal drive from other angles becomes possible. :: In step 67, the driver 80 controls each power FET of the full-wave positive bridge circuit 300 according to the previously set load ratio, and starts to be turned on. At + ^ ^ ^ ^ ^ ^ ^ Δΐη ^ ^ ^ ^ ^ The time detection unit 74 detects. In step S69, the reversal control unit 75 determines that the crankshaft 201 has passed the stage, that is, near the top dead center. If there is no passing stage ㈣, then the ratio of the passing time Atn of the aforementioned stage #n to the preceding passing stage, and the passing time △ tnq of # (n_l) [8 ratio / eight 饨 '] and the reference value just passed in step S7i. Rref (4/3 in this embodiment) is compared. If the aforementioned passing time ratio [△ "/ △ tn_1] is increased incomparably with the reference value Rref, the process returns to the foregoing step S62] The shovel drive is similar to the above-mentioned processes repeatedly. Here, the engine stop position, that is, the reverse start position is as shown in the figure. 7 (〇 curve A does not compare with the middle position of the compression top dead point of the previous and second times, = compression top dead point, in other words, the process from passing through the exhaust top dead point (when forward rotation) to the compression top dead point At this time, although the ACG starter 1 is driven in reverse with a load ratio of 70%, the crankshaft can still pass through the phase # 0 (exhaust top dead center). Therefore,

Page 12 575716 V. Description of the invention (9) ----- Step S7 is performed in step S69 as measured in step S69. # 3 2 〇 Carry am w 千 υ i 疋 arrived; because the Bech crankshaft 201 has arrived At the stage # 32, in step S72, the energization has been stopped due to the other-mentioned rotation, and thereafter, the crankshaft is stopped due to reverse rotation. 〖Beijing force advancement On the other hand, the start position of the reversal is shown in Figure 7 (c), curve B, and the middle of the compression top dead point t of time f is set closer to the compression top dead point 'in other words, from the compression through From the top dead center (for forward rotation) to the exhaust top dead center, during the process, the load ratio of the ACG starter is reversely driven. The reverse load is shown in Figure 7 (a), just before stage # 〇 (when reversed) When it is rising, the angular velocity of the crankshaft 201 decreases rapidly. In step S71, when it is determined that the passing time ratio [Δΐ: η / Λι: η-1] is 4/3 or more of the reference value, the process stops in step S72. In the aforementioned reverse rotation, the crankshaft reverses and stops at the same time. Thus, in the swing control of this embodiment, during the reverse drive after the engine is stopped, it is monitored whether the crankshaft passes through a top dead center equivalent angle and whether the angular speed of the crankshaft decreases When the crankshaft reverses, the reverse energization is stopped immediately after passing through the top dead center, and when the angular speed of the crankshaft is reduced due to the increase of the reverse load, the reverse energization is also stopped. Therefore, regardless of the start position of the reverse, the crankshaft can be compressed in the previous return Before the top dead point (when reversing), return to the position where the compression reaction force is low. Even in the swing-back control of this embodiment, based on the detected rotor angle sensor 29 to detect the angular velocity of the crankshaft 201, which is Based on the output of the rotor angle sensor that can detect the rotor angle (ie stage) of the ACG starter, the above-mentioned detection can be achieved, so there is no need to set up a special detection crankshaft

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575716 V. Description of the invention (11) In step S58, the pressure relief coil 63 becomes 0FF, and in step S59, ACG 刼 1 is OFF. & Motivation

In this way, in this embodiment, the exhaust valve is forcibly opened when the engine is started, the internal pressure of the cylinder controlled in the compression stroke is increased, and the maximum crankshaft torque P is reduced.

Tmax ’Therefore, it is possible to ensure good startability even with a small start with a small maximum torque. As shown in FIG. 5, the power generation control unit 400 normally has a delay angle from the battery 2 to the static sub-lines of each phase of the ACG starter 1 in addition to the moon dagger that controls the power generation amount (voltage). In order to increase the power generation (the function of the "ACG energization control".% Is here, the so-called delayed angle energization refers to the magnetic detection of the magnetic ring 33 based on the aforementioned rotor angle sense 29, the delay is equivalent. Pre-determined thunder £ ^ / 1,] ^ y Q The electric current angle of the electric circuit is energized in the stator coil. Guest 3 3 S S Ϊ Swiveling encirclement is to prevent the entry of The rapid change caused by the rapid change of the engine causes the engine to turn unstable. ^ Ϊ: The output voltage of the bridge circuit 3 °° (the battery voltage is within the predetermined voltage range below the adjusted voltage.) Tethered to the power generation control unit In 4 〇〇, the phonation ρ miscellaneous rr 5 cry 117 rotation number discriminating unit 48, for example, based on the detection signal of the point pulse state 30 detection bow 丨 engine 丨 enough to within the predetermined power generation control range, the number of J 'This cited rotation number

St .; Hoop driver 80 is read from the delay angle amount setting section 49: the delay angle is turned on in advance by 6 and the delay angle is preliminarily supplied to the driver from the load ratio setting section 47. § 〇. The ratio is driven to 80. The magnetic pole detected by the rotor angle sensor ° is detected.

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575716 V. Description of the invention (12) Bluff, that is, the tape formed by the magnetic pole of the outer rotor 60, each time it is detected by the sensor 2 9 ^% makes it longer than the above幵 The second delay angle, which is equivalent to the energization delay angle, is applied to the full-wave rectifier bridge electric PWM control signal. Each of the FET output battery voltage discriminating units 46 assigns the maximum control voltage VMax of the battery voltage to the factory, regulates the & control target, and controls the minimum value of the control voltage. ^ Comparison of the minimum control voltage, ^ ^ Second, Ό, increase or decrease the current-carrying load set by the load ratio setting unit to 47, so that the animal battery voltage is within the aforementioned control range Θ. That is, if the power storage person, ^ vb reaches the maximum control voltage VMax, the energized load will be reduced by only ^ 仞! (For example, 1%), and when the battery voltage Vb drops to the minimum control voltage VMim, the energized load will only increase by the same small value. Fig. 10 is a flowchart showing the operation of the power generation control unit 400, and the power generation control unit is started after the engine start control by the start control unit 500 is completed. In step S41, it is determined whether or not the number of engine revolutions is within the power generation control range. The gross power control range is set to, for example, 1 000 r p m or more and 3 50 0 r p m or less. If the number of engine revolutions is in the power generation control range, step S42 is performed to determine that the flag indicating that the number of engine revolutions is in the power generation control range is yes (= 1). If the signal flag is not set, step S43 is performed: the flag FACG is again set. In step S44, the energization delay amount acgagl is set to a predetermined value ACGAGL. The predetermined value ACGAGL can be appropriately set in advance, but in this embodiment, it is set to, for example, an electrical angle of 6 Q. .

Continue to step 45. Set the initial value ACDUTY C: \ 2D-C0DE \ 91-07 \ 91107591.ptd in the power-on load acduty. Page 16 575716 5. Description of the invention (13) The initial value ACDUTY can be set appropriately beforehand. However, in this embodiment, it is set to 40%, for example. After steps s 4 3 to S 4 5 are completed, step S47 is performed. If the result in step S4 is YES, skip steps S43 to S45 and proceed to step S47. When the number of engine revolutions does not exist in the aforementioned power generation control range ', after the signal flag facg is reset (= 0) in step S 4 6, step s 4 7 is performed. In step S47, it is determined whether the signal flag Fagg is set. If the signal flag ^^ is set, it is judged at step S48 whether the battery voltage vb is greater than the maximum control voltage amount VMax. The maximum control voltage \ ^ ax is set to a lower value than the adjustment voltage, such as 13.5Volt. If the battery voltage Vb is not greater than the maximum control voltage value VMax, step S49 is performed to determine whether the battery voltage Vb is less than the minimum control voltage value VMin. The minimum control voltage VMin is set to, for example, 13 · OVolt. In step S49, if the battery voltage Vb is not below the minimum control voltage VMin, it is determined whether Vb falls within the ACG energization voltage range set to a value lower than the regulator's adjustment voltage, then step 50 is performed according to the above-mentioned energization delay angle. ACG is controlled by measuring the amount of acgagl and the load acduty. When it is judged at step S48 that the battery voltage Vb is greater than the maximum control voltage VMax ', step S5 1' is performed to reduce the energized load a c d u t y by only a small value D D U T Y. The minute value D D U T Y is, for example, 1%. When it is determined in step s 4 9 that the battery voltage V b is below the minimum control voltage V M i η, step s 5 2 is performed to increase the energized load acduty by only a small value DDUTY. Steps S51 and S52 are followed by step S50. Moreover, the aforementioned small value DDUTY when the energizing load acduty increases or decreases may not necessarily be the same, depending on the maximum control voltage VMax or the control voltage

C: \ 2D-C0DE \ 91-07 \ 91107591.ptd page 17 575716 V. Description of the invention (14) The difference between the minimum value VM i η and the current value, and the small value DDUTY may be changed proportionally. On the other hand, if the signal flag facg is not set in step S47, that is, it is known that the signal flag is not in the power generation control range, then step S53 is performed to stop the ACG power-on control. Fig. 11 is a timing chart showing the current (phase current) flowing through each phase of the stator coil and the output of the rotor angle sensor 29 during the AC C G energization control. No delay angle energization control is performed. In normal conditions, in response to changes in the positive and negative (NS) of the detection output of the rotor angle sensor 29, current is supplied to the phases of the stator coil, V, and W. On the other hand, when the delay angle energization control is performed, the current is delayed by a predetermined delay angle amount d (= 60 °) from the change of the positive and negative (NS) detection output of the rotor angle sensor 29. u, V, W phases. In FIG. 11, the conduction angle T due to load interruption is 180. By applying the energized load supplied from the load ratio setting unit 47 to the driver 80, the load can be reduced to 180. Within decision. Fig. 12 is a graph of the energized load set with the number of revolutions of the engine Ne, that is, the number of revolutions of the ACG starter 1 as a parameter. The number of engine revolutions is detected, and the energized load is determined in response to the number of engine revolutions. In this way, according to the power generation control of this embodiment, it is not necessary to activate a normal voltage regulator in a low rotation range, and it is possible to stably increase the power generation amount. Therefore, the variation in engine load can be reduced during "core speed operation", and the variation in engine rotation can be minimized to stabilize the idle operation. Next, in the present embodiment, the specifications of the ACG starter 1 described above, particularly the maximum generated torque related to the specifications, will be described.

C: \ 2D-C0DE \ 91-07 \ 91107591.ptd Page 18 575716 V. Description of the Invention (15), which previously showed that == :: plug = ^ generates the torque above the maximum crankshaft torque Tmax. Qu_ The starting and driving characteristics of the engine must be shown in the two states, as shown in the ACG starter 1 "^ This is like a starter!" Due to the inertia structure of the crankshaft, the large starting gas with large moment # \ At first use, when the bismuth is used to drive the motor, its acceleration performance will decrease. Position 詈 2 y As shown in this embodiment, after the engine is stopped, the crankshaft reverses to a predetermined position, and the engine starting device needs to go to the desired stroke to increase the travel time plus *, J = compression can be further increased, so it includes The number of revolutions of the crankshaft is proportional to sexual force. , U turn 糸 also serve the relatively large habit. Figure 13 shows the engine rotation number Ne (actual

Tdrv (solid line), which includes the time chart of the crankshaft's rotating torque itself and the aforementioned driving torque Tdrv and inertia torque e Tlnej chain line). The torque δ of e (point moment T: η! ί t: I 'as shown in Figure 1 3' is displayed at the time tmax crankshaft torque > H / 仏 ❿, in order to make the piston across the compression top dead center, to the evening A driving torque of 1 · 3kgfm or more is required. Therefore, 芏 1 needs to have a maximum torque of!. 3kgcm or more of a large ACG starter that has been reached. In this embodiment, after the engine is stopped, the crankshaft is reversed. As shown in Figure 13, when the next engine starts, it will reach the compressed line: C: \ 2D-00DE \ 91-07 \ 9110759l.ptd Page 19 575716 V. Description of the invention (16) '—— 4 engine revolutions It can reach 7000 to 900 rpm. Therefore, as shown in Figure 丨 4, the inertia torque Tine of the turning system including the crankshaft 201 becomes larger. Therefore, even if only the driving torque τ drv occurs in the starting stack 1, and It is far lower than the maximum crankshaft torque Tmax, but the combined torque Tadd of inertia torque Tine and driving torque TdrV2 can exceed the aforementioned maximum crankshaft torque Tmax (1.3 kgfm in this embodiment). That is, the ACG starter 1 can be reduced in size and weight. However, in the ACG starter 1, the piston is further advanced beyond the compression stroke. It is necessary to generate the necessary crankshaft torque 1 (31 ^), which is confirmed to be approximately 20% of the maximum crankshaft torque Tmax necessary when the piston spans the compression stroke according to the results of the inventors and others. Therefore, in this embodiment, It is desirable that the maximum torque of the ACG starter 1 is at least approximately 20% of the maximum crankshaft torque Tmax. Furthermore, as shown in this embodiment, if the ACG starter! Is made of a straight structure with the crankshaft 201, its ACG is relative to the engine. The starter i functions as an inertial mass. From the viewpoint of the driveability during acceleration, the value of the inertial mass, as shown by the Bebesch shape, 'the engine with a maximum crankshaft torque of about 13 kgfm, empirically believes that the inertial mass is 28 ~ 33kgfm is an appropriate value. Figure 15 shows the relationship between the inertia mass of ACG starter 1 and the maximum generated torque. ACG starter with specifications of 28 ~ 33kgcm inertia mass} its maximum generated torque is 0.5 · 0 · 8kgfm. This is equivalent to about 40 ~ 60% of the maximum crankshaft torque, and the ac G starter 1 with inertia mass above this has good engine startability, but its drive when accelerating Is reduced. From the above viewpoint, the present embodiment 1 ACG starter generator system using the maximum torque Tmax as the maximum torque of the crankshaft to 6〇 2〇% of small starter motor.

C: \ 2D-00DE \ 91-07 \ 91107591.ptd Page 20 575716 V. Description of the invention (17) In other words, A C G starts the selection of the maximum torque generated directly by the starter 1 and makes the selection. The effect of the inertia mass of the shaft 20 in its most suitable invention is according to the present invention, which is & & speed, which can be relatively large;! ;; to; before the reduction stroke 'the resultant force of its dynamic torque is reachable, so to this'丨 Bearing force and the maximum occurrence torque ratio is larger than the crankshaft torque, even if the maximum crankshaft torque from M m kr ^ ^ m is taken as a small case, the more thin the light. Because of the parallel eclipse, the starting motor can be smaller than the previous one, so that it can be used to improve the driving performance without causing undue damage. According to the upper limit of the range, the drive motor itself has been fully driven. The piston itself can also be straddled, so it is formed as a real component number. 1 Starter and generator (ACG 2 swing device 2, battery 3 Rear bumper 3, ECU 4 Base plate part 5 Steering head 6 Bottom pipe 7 Main pipe 8 Seat cushion 9 Reduction mechanism 10 Belt-type stepless speed changer

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V. Description of the invention (18) 11 Handlebar 12 Front fork 13 Handlebar cover 14 Air filter 15 Support frame 16 Connecting rod member 17 Carburetor 18 Suspension bracket 19 Suction pipe 21 V-belt, Ignition coil 22 Mars plug 23 Section Flu sensor 24 Fuel sensor 25 Valve seat switch 26 Idle speed switch 27 Cooling water temperature sensor 28 Sensor box 29 Rotor angle sensor (magnetic pole sensor) 30 Ignition pulsator 31 Substrate 32 Wiring lead 33 Magnetic Ring 34 Start relay 35 Start switch C: \ 2D-CODE \ 91-07 \ 91107591.ptd Page 22 575716

36 Stop switch 37 Stop switch 38 Standby indicator 39 Oil indicator 40 Speed sensor 42 Headlight 43 Timing switch 44 Main fuse 45 Main switch 46 Battery voltage determination section 47 Load ratio setting section 48 Engine rotation number determination section 49 Delay angle Volume setting section 50 Static child 51 Decompression drive section 52 Engine revolution number discriminating section 60 Outer rotor 6 0a Outer rotor hub 63 Decompression coil 72 Load ratio setting section 73 Phase discriminating section 74 Phase transit time detecting section 75 Reverse control section 80 Horse Zone actuator page 23 C: \ 2D-CODE \ 91-07 \ 91107591.ptd 575716 V. Description of the invention (20) 100 Adjuster 201 crankshaft 202 crankcase 20 2L left crankcase 2 0 2R right crankcase 208 bearing 209 Bearing 210 Belt drive wheel 210L Half fixed side pulley 210R Half movable side pulley 210Ra Cam plate sliding hub 211 Hub 212 V-belt 213 Crank pin 215 Cam plate 215a sliding Pieces 216 dry hammer ball 231 sprocket 232 gear 246 bolt 253 screw 279 bolt 280 fan 281 fan cover

1111

C: \ 2D-00DE \ 91-07 \ 91107591.ptd Page 24 575716 V. Description of the invention (21) 282 Radiator 300 Full-wave rectifier bridge circuit 400 Power generation control unit 500 Start control unit 700 Swing control unit E Engine FW front wheel RW rear wheel

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3 / J / lO Brief description of the whole side view of the moving wheel Figure 1 is a diagram of a speed keda to which the present invention is applied. FIG. 2 is a curve of the swinging device along the figure. FIG. 3 is an enlarged view of a part of FIG. 2. Figure of 4 faces. Fig. 4 is a starter-generator control. Fig. 5 is a block diagram showing the main part I of the ECU of Fig. 4. Fig. 6 is a flowchart of swing-back control. Block diagram. Figures 7 (a) to (c) are diagrams showing the relationship between the crank angle and the degree of rotation. Shaft Torque, Phase, Angular Speed Figure 8 shows the change in crankshaft torque for engine start control. FIG. 9 is an operation flowchart of the pressure relief driving unit. FIG. 10 is a flowchart of ACG power generation control processing. Fig. 11 is a timing chart showing the ACG thunder control accusation, the phase current of the stator coil and the output of the rotor angle sensor. Figure 12 is a graph of the energized load with the number of engine revolutions as a parameter. Fig. 13 is a graph showing changes over time of the number of revolutions Ne of the engine and the torque Tcnk of the crankshaft. / FIG. 14 is a graph showing the time variation of the driving torque Tdrv of the starter motor, the inertia torque Tine of the slewing system including the crankshaft, and the combined torque Tadd of the driving torque Mrv and the inertia torque Tine. Fig. 15 is a graph showing the relationship between the inertial mass of the ACG starter i and the maximum generated torque.

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Claims (1)

575716 VI. The scope of the patent application is transferred to the institute, and after it is made, the maximum occurrence of the major accident is beyond the limit. 2 · If the motor is directly connected to the 3 · If the motor is on. 4 · If it has a more fixed base force, the starting position of the engine is equipped with the crankshaft torque required for cranking the crankshaft torque. The largest crankshaft customary patent application. The largest patent application with a machine. · If the patent application piston is about to 900rpm, the patent application will be compressed. Among them, it is at 700 rpm 6 · If it is about to reach 900 rpm, the device is characterized by: the engine is stopped for the next MAN crankshaft reverse rotation and reverse rotation Starting the reversing control mechanism of the engine starting device 3, as described above: f In order to make the piston span pressure less than about 60% at the start of the engine, the crankshaft torque required is higher than that required. For the starting of the engine to the compression line ^, the engine starting device of item 1 has a torque-generating stream, Chi Gu; *, Jiayue "The edge quality has become the highest in the basin. Ϊ The basis for making the range of the starting motor suitable for the wheel. The upper limit is selected. The engine starting torque of item 1 of the yoke is approximately 20% of the maximum crankshaft torque mentioned above. The compression stroke will be set within the period below the start of the engine of any of the items ΞΐΓ / 3. Zhongqi range 1 to 3 Zhong 乜 —K t The engine starting device of J, before reaching the compression stroke.仃 ％ 之 则 ’bow 丨 engine rotation number is from the engine of the item to the private, the engine rotation"