Vehicle power transmission apparatus

Abstract: An object of this invention is to provide a vehicle power transmission apparatus (10) for keeping the shaft output constant when driving a vehicle regardless of the change in the frictional force of the belt in a belt type stepless speed change device. A vehicle power transmission apparatus embodying the invention comprises a belt type stepless speed change device and is used with a vehicle driving prime mover on board a vehicle. The apparatus provides a flat characteristic segment covering at least a part of the shaft output characteristic relative to the revolutions of the vehicle driving prime motor. The apparatus allows the vehicle to be driven by constant shaft output within the segment of the flat shaft output characteristic regardless of secular changes in the frictional force of the belt in the belt type stepless speed change device.

Description: The present invention relates to a vehicle power transmission apparatus according the preamble part of claim 1. Of the vehicles driven by internal combustion engine or by electric motor, some employ a belt type stepless speed change device as the automatic transmission for transmitting the torque of the driving source smoothly to the driven side. For example, Japanese Patent Laid-Open JP-A-3 128 789 (Hei 3-128789) discloses an electrically driven vehicle including a belt type stepless speed change device. This stepless speed change device has an endless belt with a trapezoid cross section engaged between the driving pulley mounted on the motor output shaft on the one hand, and the driven pulley furnished on the reduction gear input shaft on the other. The endless belt of the above cross-sectional shape transmit the torque when engaged frictionally across the driving pulley to the driven pulley. Over time, the coefficient of friction of the pulleys varies due primarily to secular change. In particular, the intermediate speed characteristic between high and low speeds is liable to change. The changed intermediate speed characteristic deteriorates the quality of the transmission apparatus or causes the performance thereof to become erratic. The irregularities often detract from the comfort of the passenger(s) on board the vehicle running on the transmission apparatus in question. EP 0 408 074 A1, of the same patent family as the above cited JP-A-3 128 789, discloses a vehicle power transmission apparatus according to the preamble part of claim 1. Such known vehicle power transmission apparatuses comprising a belt-type stepless speed change device suffer from insufficiencies related to the belt-type speed change device. As has already been indicated the problem is that the friction coefficient between the belt and the driving pulley and the driven pulley varies with time, in particular decreases with time. As a result of a decrease in the friction coefficient the slip between the belt and pulleys increases. Accordingly, in order to obtain a given vehicle speed the number of motor revolutions per time unit (rpm) has to increase to compensate for the increased slip. Since the power output at the output shaft of the electric motor changes with the rpm (cf. figure 17 of the EP 0 408 074 A1), the performance of a vehicle having said power transmission apparatus also changes. Particularly after a reduction in the friction coefficient between the belt and the pulleys, the speed change characteristic of the speed change device (speed reduction over vehicle speed) no longer matches the actual motor power output characteristic (motor shaft power output over motor revolutions or vehicle speed, respectively). As a consequence, the driving quality of the vehicle deteriorates or might even become erratic. An article by F.T. Thompson in the IEEE Transactions on Vehicular Technology, vol. VT-27, no. 3, August 1978, pp. 132-137, with the title "Advanced Electronic Control Systems for Electric Vehicles", discusses the characteristics and relative advantages of several types of electric vehicle control systems, namely so-called armature chopper systems, AC drive systems and field control systems. According to the discussion of armature chopper systems, it is known to provide substantially constant motor output power over a discrete range of motor revolutions per time unit. The article briefly mentions some objects the vehicle has to fulfill, e.g., that the vehicle has to overcome rolling resistances and wind resistance, has to provide acceleration, and has to climb grades. The article does not address problems encountered with vehicles having a belt-type stepless speed change device. In view of the foregoing, it is an object of the invention to provide a vehicle power transmission apparatus which is less sensitive to changes in the friction coefficient between the belt and the pulleys of the belt-type stepless speed change device. This object is achieved by the vehicle power transmission apparatus having she features of claim 1. By providing storage means for storing a predetermined characteristic table giving a desired shaft power output (kW) as a function of the motor revolutions per time unit (rpm), calculation means adapted to calculate the current shaft power output (kW) on the basis of the current flowing through the electric motor and the current motor revolutions per time unit (rpm) and comparing means for comparing said current shaft output (kW) with the desired shaft power output (kW) given for the current motor revolutions per time unit by said characteristic table, and by adapting said control circuit to control, on the basis of said comparison, the duty factor in such a manner that the shaft output is substantially constant over at least one discrete range of motor revolutions per time unit as given by the predetermined characteristic table, the shaft output power is kept constant if the rpm of the motor is changed within said at least one discrete range of motor revolutions per time unit to compensate for a change in the friction force between the belt and the pulleys. Said at least one discrete range of motor revolutions per time unit providing substantially constant shaft output power comprises the momentarily substantially constant revolutions-per-time-unit-value, which is provided over the variable speed characteristic region, and preferably also comprises the motor revolutions per time unit in a maximum vehicle speed region in which the speed change device provides the high gear ratio. By providing said at least one discrete range of motor revolutions per time unit (which can also be characterized as being a discrete substantially constant flat power characteristic segment, which covers at least a portion of the power output - also denoted as shaft ouput - relative to the revolutions of the motor) the power output of the motor is kept constant if the motor revolutions per time unit (rpm) are changed within said discrete range of motor revolutions per time unit (said substantially constant flat power characteristic segment) to compensate for a change in the frictional force between the belt and the pulleys. Accordingly, the driving quality of a vehicle equipped with the vehicle power transmission apparatus according to the invention does not - at least not within the respective discrete range of motor revolutions per time unit (flat characteristic segment) - deteriorate with the variation of the friction resistance between the belt and the pulleys caused by time-induced belt wear. Accordingly, when the frictional force of the belt in the belt-type stepless speed change device varies over time, the revolutions of the vehicle motor running in the stepless mode (variable speed characteristic region) can change correspondingly without variation of the power or shaft output of the motor, which safeguards, as explained, the high driving quality of the smoothly running vehicle. Preferred embodiments of the vehicle power transmission apparatus according to the invention will now be described in connection with an electrically driven motorcycle. Fig. 1 is a cross-sectional view of the first embodiment of the invention; Fig. 2 is a cross-sectional view of the second embodiment of the invention; Fig. 3 is a circuit diagram of a typical motor control system for use with the embodiments; Fig. 4 is a view illustrating a typical motor revolution vs. shaft output characteristic in connection with the invention; Fig. 5 is a view describing how a motor driving signal is constituted in connection with the invention; Fig. 6 is a set of views showing a typical vehicle speed vs. motor revolution characteristic, vehicle speed vs. entire vehicle output characteristic, and vehicle speed vs. efficiency characteristic in connection with the invention; and Fig. 7 is a view depicting a typical motor revolution vs. driving torque characteristic in connection with the invention. Figs. 1 and 2 are cross-sectional views of mechanical structures embodying the invention in conjunction with the electrically driven motorcycle. Fig. 1 is a cross-sectional view of a first embodiment wherein the clutch mechanism is provided on the driven side; Fig. 2 is a cross-sectional view of a second embodiment wherein the clutch mechanism is furnished on the driving side. In Fig. 1, reference numeral 10 is a driving section of the electrically driven motorcycle. A motor housing 12 is a casting made from a light metal. Inside the motor housing 12 is a motor 18 constituted by a stator 14 and a rotor 16. One axial end of the motor 18 is closed by a first lid member 20. The first lid member 20 supports rotatably a rotating shaft 24 of the motor 18 with bearings 22. The other end of the motor housing 12 supports the rotating shaft 24 with bearings 26. The motor housing 12 and the first lid member 20 are secured with bolts 28. The entire opening of the first lid member 20 is closed by a first cover member 30. Through the axial center of the first cover member 30 is a cooling hole 32. The cooling hole 32 is connected with the interior of the motor housing 12 via a hole 34 formed in the first lid member 20. One end of the rotating shaft 24 on which the rotor 14 is mounted is equipped with a centrifugal cooling fan 36 near the bearings 26. The cooling air generated by the centrifugal cooling fan 36 in operation is sent through a hole 38 to a chamber 39 formed by a second cover member 48, to be described later. The other end of the rotating shaft 24 is equipped axially with a first fixed pulley half 40 and a first moving pulley half 42, the two halves being secured in a fixed manner. When a centrifugal weight 44 is moved outward by its centrifugal force, the first moving pulley half 42 shifts its center of gravity in the radial and outward direction. A pulley belt 46 having a trapezoid shaped cross section is held taught across the first fixed pulley half 40 to the second moving pulley half 42 over their tapered surfaces. In this way, the pulley belt 46 is also engaged across a second fixed pulley half 62 and a second moving pulley half 58 held on the rear wheel side by the second cover member 48, to be described later. On the driven side, reference numeral 53 indicates a reduction gear. This reduction gear 53 has a gear train construction. A centrifugal clutch 56 is fixedly attached to the input shaft 54 of the reduction gear 53. The second moving pulley half 58 is attached to the centrifugal clutch 56 in an axial and displaceable manner. In this setup, a coil spring 60 is disposed interposingly between the moving pulley half 58 and the centrifugal clutch 56. The coil spring 60 keeps pushing the moving pulley half 58 toward the second fixed pulley half 62 engaged detachably with the input shaft 54. As illustrated, the centrifugal clutch 56 has a clutch inner 66 and a clutch outer 68. The clutch inner 66 and clutch outer 68 engage with each other reflecting the current revolutions to transmit the torque thereof to the input shaft 54. A second lid member 72 is fixedly attached to that section of the motor housing 12 in which the reduction gear 53 is contained. The input shaft 54 is rotatably supported by bearings 74 of the second lid member 72 and by bearings 76 held in the motor housing 12. Inside the motor housing 12, an input gear 78 is engaged with the input shaft 54. The input gear 78 is also engaged with an intermediate gear 80 of a large diameter. An intermediate gear 82 aligned axially with the intermediate gear 80 is engaged with an output gear 84. One end of the output gear 84 is fixedly engaged with an output shaft 88 that supports rotatably the rear wheel of the electrically driven motorcycle. In Fig. 1, reference characters WR indicate the rear tire secured to the rear wheel. Fig. 2 is a cross-sectional view of the second embodiment of the invention. with the second embodiment, those parts that are functionally identical to those already described in connection with the first embodiment are designated by the same reference characters, and any detailed descriptions thereof will be omitted. As shown in Fig. 2, what makes the second embodiment different from the first is that a centrifugal clutch 56a corresponding to the centrifugal clutch 56 is located on the driving side. In the second embodiment, the centrifugal clutch 56a is axially located outside the bearings 26. The centrifugal clutch 56a has a clutch inner 66a and a clutch outer 68a. The cooling air generated by the revolutions of the centrifugal cooling fan 36 is sent via a hole 38a to a chamber 39a accommodating the centrifugal clutch 56a. On the rear wheel side, a bearing member 90 is fixedly attached to the input shaft 54a of a reduction gear 53a. A moving pulley half 58a is attached to the bearing member 90 in an axial and displaceable manner. In this setup, a coil spring 60a is disposed interposingly between the moving pulley half 58a and the bearing member 90. The coil spring 60a keeps pushing the moving pulley half 58a toward a fixed pulley half 62a fixedly attached to the input shaft 54a. Thus one end of a pulley belt 46a is held taut across the moving pulley half 58a to the fixed pulley half 62a. In Fig. 2, the fixed pulley half 40, moving pulley half 42, centrifugal weight 44 and pulley belt 46 (46a) constitute a belt type stepless speed change device (hereinafter called the belt converter). The driving section 10 of the motorcycle in the first and the second embodiments described above operates as follows: Turning a throttle lever, not shown, rotates the motor 18. As the rotating shaft 24 rotates, the resulting torque rotates the first fixed pulley half 40 and the first moving pulley half 42. If the rotating speed is sufficiently high, the centrifugal weight 52 moves outward in the radial direction. This causes the moving pulley half 42 to shift in the direction shorn by two-dot chain line relative to the first fixed pulley half 40. On the side of the reduction gear 53 (53a), the moving pulley half 58 (58a) shifts in the direction indicated by two-dot chain line against the recoiling force of the coil spring 60 (60a). That is, on the side of the reduction gear 53 (53a), the moving pulley half 58 (58a) moves away from the second fixed pulley half 62 (62a). When the second fixed pulley half 62 (62a) and the moving pulley half 58 (58a) rotate while shifting axially under the torque of the pulley belt 46 (46a), the input shaft 54 (54a) rotates correspondingly. The revolutions are reduced as the gear ratio is changed through the input gear 78, intermediate gear 80, intermediate gear 82 and output gear 84, in that order. The resulting revolutions are transmitted by the output shaft 88 to the rear wheel WR. Thus the rear wheel rotates assuming the role of the driving wheel to move forward the electrically driven motorcycle in cooperation with the front wheel, not shown. Below is a description of how the motor 18 runs and how it is controlled when driven. The motor 18 is a DC brushless motor comprising a rotor 16, a stator 14, magnets 17, a rotor position detector 21 and a revolution detector 23. The rotor 16 has a total of four N and S permanent magnets 13N and 13S arranged alternately around the outer circumference of a rotor core secured to the rotating shaft 24 of the motor 18. The stator 14 has stator coils 15U, 15V and 15W arranged in Y-connection. The magnets 17 are N and S pole pieces which correspond respectively to the permanent magnets 13N and 13S and which are also secured alternately around the outer circumference of the rotating shaft 24. The rotor position detector 21 is composed of three Hall elements and is located opposite to the magnet assembly. The revolution detector 23, made of FG's for detecting the revolutions of the motor 18, is attached to the rotating shaft 24. Fig. 3 is a circuit diagram of a motor control system for use with the embodiments. For control over the motor 18, the invention provides a ROM 27 containing a motor revolution vs. shaft output characteristic table (the characteristic is plotted by solid line in Fig. 4) and a controller 25 having a microcomputer that works in cooperation with the ROM 27. The controller 25 receives four kinds of signals: the output signal from the rotor position detector 21 as it detects the permanent magnet position of the rotor 16 resulting from the rotation of the motor 18; the output from a potentiometer connected with an accelerator grip which in turn is coupled to a motorcycle handlebar, not shown; the output signal from the revolution detector 23; and the output from an A/D converter 41 that converts to digital data the voltage reductions across a resistor 43, to be described later, the reductions being attributed to the current flowing through the rotor coils of the motor 18. Between the controller 25 and the motor 18 is a switching circuit 29 that includes a driver 35 for amplifying the output of the controller 25. The switching circuit 29 also contains serially connected field effect transistors (FET's) 33a and 33b, 33c and 33d, and 33e and 33f. In turn, these FET's are connected in parallel between ground and the resistor 43 whose one end is connected to a battery 37. The connecting point between source of the FET 33a and drain of the FET 33b is connected to the stator coil 15U; the connecting point between source of the FET 33c and drain of the FET 33d is connected to the stator coil 15V; and the connecting point between source of the FET 33e and drain of the FET 33f is connected to the stator coil 15W. The output of the driver 35 drives the FET's 33a through 33f selectively to energize any one of the stator coils 15U, 15V and 15W. In the above setup, the current flowing from the battery 37 to the stator coils 15U, 15V and 15W is allowed to flow into the resistor 43 for conversion to voltages. Voltage reductions occurring across the resistor 43 are fed to the A/D converter 41 for conversion to digital data. The digital data are then sent to the controller 25. The FET's 33a through 33f are connected respectively with diodes 31a through 31f in parallel. The functions of she controller 25 include those of revolution control and shaft output control. In the motor control system of the above constitution, the controller 25 generates pulses for stitching the current to any one of the phases of the stator coils 15U, 15V and 15W in accordance with the output signal from the rotor position detector 21. The detector 21 detects the magnetic pole position of the rotor 16 driven by the motor 18. A deviation is calculated between the output of the potentiometer connected to the accelerator grip and the output signal from the revolution counter 23. On the basis of the deviation thus calculated, the duty ratio of a PWM signal is calculated. The PWM signal chops the pulses for switching the current to any one of the stator coils 15U, 15V and 15W. The chopped pulses are output by the controller 25 to the driver 35 for the respective stator coils. The period of the PWM signal is set to be very much shorter than the pulse width of the pulses for switching the current to the stator coils 15U, 15V and 15W. Fig. 5 is a schematic view showing one stator coil phase of the chopped pulses. In Fig. 5, reference character P indicates the pulses for switching the current to the stator coils, and the shaded portions represent regions in which the current is allowed to flow. The pulses chopped by the PWM signal are amplified for each phase by the driver 35. The amplified pulses turn on or off the corresponding FET's for control of the rotor revolutions of the motor 18 so that the deviation between the potentiometer output and the output signal from the revolution detector 23 will become zero. Meanwhile, the controller 25 calculates the shaft output of the motor 18 in accordance with the output of the revolution detector 23 as well as with the digital data converted by the A/D converter 41. The calculations are performed on the ground that the shaft output is based on the product of the current flowing through the motor 18 and the revolutions thereof. The motor revolution vs. shaft output characteristic table in the ROM 27 is referenced according to the rotor revolutions of the motor 18 detected by the revolution detector 23. This causes the shaft output corresponding to the rotor revolutions of the moor 18 to be read from the ROM 27. A comparison of the read-out shaft output with the calculated shaft output is followed by control of the duty ratio of the PWM signal in such a manner as to bring the deviation between the two kinds output to zero. The PWM signal with its duty ratio thus controlled chops the pulses P. The chopped pulses are amplified by the driver 35. The amplified output of the driver 35 turns on or off the FET's 33a through 33f selectively. Accordingly, the motor 18 is driven for shaft output based on the motor revolution vs. shaft output characteristic (at full load), the characteristic having segments a , b , c and a region beyond the three segments, as shown in Fig. 4. In the segment a , the output torque for increasing the shaft output in the low revolution region is constant; in the segment b , the shaft output remains constant past its peak; in the segment c , the shaft output further remains constant; and the region beyond the three segments is a high revolution region where the shaft output drops as the revolutions increase. In Fig. 4, the broken line represents a motor revolution vs. shaft output characteristic of the motor 18 in effect when the above-described chopping control is not provided. The rotor revolutions of the motor 18 are transmitted to a belt converter A (i.e., belt type stepless speed change device). In turn, the belt converter A drives the rear wheel WR via the reduction gear 53 (53a). The belt converter A is set to the characteristic of the broken line in Fig. 6(A), the characteristic being that of vehicle speeds vs. motor revolutions in the initial state where the frictional force of the pulley belt 46 (46a) has yet to be diminished. According to the characteristic thus established, the belt converter A works as follows: When the revolutions of the rotor 16 in the motor 18 reach a predetermined number of revolutions, the centrifugal clutch 56 (56a) is engaged. The vehicle speed increases in keeping with the rotor revolutions of the motor 18 based on the low reduction ratio of the belt converter A. The low reduction ratio is the ratio of the driving pulley to the driven pulley in terms of radius, the two pulleys being spanned with the pulley belt 46 (46a) wound thereon. Illustratively, speed change starts at a predetermined number of revolutions in the vicinity of the number of revolutions for yielding maximum efficiency. Speed change continues in a stepless manner with the established number of revolutions kept unchanged up to a vehicle speed that is commensurate with the high reduction ratio. Thereafter, the vehicle speed is raised along the high reduction ratio curve. It should be noted that the segment b of the motor revolution vs. shaft output characteristic in Fig. 4 is established so that the revolutions changed in stepless fashion by the belt converter A will fall within the segment b of the vehicle speed vs. motor revolution characteristic in Fig. 6. The segment b is called the variable speed characteristic region in which the variable speed characteristic occurs between the lowest and the highest ratios. Generally, where the belt converter A is utilized, the frictional force between the pulley belt 46 (46a) on the one hand and the first fixed pulley half 40 and the second moving pulley half 42 on the other, and the frictional force between the pulley belt 46 (46a) on the one hand and the fixed pulley half 62 (62a) and moving pulley half 58 (58a) on the other, deteriorate over time. Even with the rotor revolutions of the motor 18 held constant, the revolutions of the rear wheel WR decrease. This makes it impossible for the vehicle to run at a constant speed. On the other hand, raising the rotor revolutions of the motor 18 generally leads to a drop in the shaft output, with the result that the vehicle cannot run on the same output. By contrast, according to the invention as embodied above, there is provided a constant shaft output segment covering at least part of the whole span of rotor revolutions of the motor 18 (i.e., within variable speed characteristic region), the rotor revolutions being in effect when the vehicle illustratively travels up slopes. An example of the constant shaft output segment is the segment b of the motor revolution vs. shaft output characteristic shown in Fig. 4. When a drop occurs in the frictional force between the driving and driven pulleys on the one hand and the pulley belt 46 (46a) on the other in the belt converter A, a change takes place from the vehicle speed vs. motor revolution characteristic indicated by broken line in Fig. 6(A) to that indicated by solid line in the same figure. However, the rear wheel WR is driven by the constant shaft output within the segment b of the vehicle speed vs. motor revolution characteristic represented by solid line in Fig. 6(A). Because the vehicle in acceleration is driven by the constant shaft output within the segment b of the vehicle speed vs. motor revolution characteristic in Fig. 6(A), any reductions in the frictional force between the driving and driven pulleys on the one hand and the pulley belt 46 (46a) on the other from the initial value are minimized, the reductions being attributed to secular change and/or irregularities in mass production. That in turn minimizes any adverse effects on the power characteristic of the vehicle. Since the shaft output is kept constant within the segment b , drops in the frictional force between the driving and driven pulleys on the one hand and the pulley belt 46 (46a) on the other seldom affect the vehicle's capability to travel up slopes. In the preferred embodiments, the reduction ratio of the belt converter A rarely varies with the reduction in the frictional force between the driving and driven pulleys on the one hand and the pulley belt 46 (46a) on the other within a region of approximately maximum revolutions (e.g., segment c ) beyond the segment b of the motor revolution vs. shaft output characteristic shown in Fig. 4. As illustrated in Fig. 4, the segment c is the region where the shaft output remains constant with respect to the motor revolution vs. shaft output characteristic. This makes it possible to drive the vehicle at maximum speed despite reductions in the frictional force between the driving and driven pulleys on the one hand and the pulley belt 46 (46a) on the other. It is also possible to maintain the maximum speed regardless of power losses resulting from the wear of the gear elements constituting the reduction gear 53 (53a) between the driven pulley and the rear wheel WR. In that sense, the segment c is called the maximum vehicle speed region. It is the region where the maximum vehicle speed is achieved within the variable speed characteristic of the highest ratio. The segment c of the vehicle speed vs. motor revolution characteristic in Fig. 6(A) corresponds to the segment c of the motor revolution vs. shaft output characteristic in Fig. 4. Furthermore, where the segments b and c of constant shaft output are provided in the motor revolution vs. shaft output characteristic of Fig. 4, reductions in the frictional force between the driving and driven pulleys on the one hand and the pulley belt 46 (46a) on the other scarcely affect the vehicle speed vs. entire vehicle output characteristic, as depicted in Fig. 6(B). (In the figure, the broken line indicates the initial state in which no frictional force reduction has occurred, and the solid line stands for a state where the frictional force has dropped. The same applies to Fig. 7.) If no constant shaft output segment is provided in the motor revolution vs. shaft output characteristic, as in the case indicated by broken line in Fig. 4, reductions in the frictional force between the driving and driven pulleys on the one hand and the pulley belt 46 (46a) on the other significantly affect the vehicle speed vs. entire vehicle output characteristic, as shown in Fig. 6(C). When the segments b and c of constant shaft output are provided as illustrated in Fig. 4, reductions in the frictional force between the driving and driven pulleys on the one hand and the pulley belt 46 (46a) on the other seldom affect the vehicle speed vs. efficiency characteristic, as shown in Fig. 6(D). In the centrifugal clutch 56 (56a), secular change brings about reductions in the frictional force between clutch inner 66 (66a) and clutch outer 68 (68a). In turn, the reductions cause the clutch capacity to drop from a capacity g upon initial friction indicated by broken line down to a capacity f shown by solid line. However, within the region ranging from the clutch capacity g to the clutch capacity f , the torque of the motor 18 remains constant as shown by solid line e in the motor revolution vs. driving torque characteristic of Fig. 7, the constant torque region corresponding to the segment a of the motor revolution vs. shaft output characteristic in Fig. 4. This allows the centrifugal clutch 56 (56a) to be driven at a constant torque level irrespective of the frictional force being at its initial value or having degraded over time, whereby constant torque transmission is ensured by the centrifugal clutch 56 (56a). Thus the driving torque stays constant and the vehicle's capacity to move up slops is not adversely affected. The segment a of the motor revolution vs. driving torque characteristic in Fig. 7 corresponds to the segment a of the motor revolution vs. shaft output characteristic of Fig. 4. In a torque segment d of the motor revolution vs. shaft output characteristic in Fig. 4, the torque exceeds that in the constant torque segment a . This torque segment d is matched with the segment d provided in the motor revolution vs. driving torque characteristic of Fig. 7. As a result, the vehicle can start in a powerful manner at a torque level higher than that of the constant torque segment a . Conventionally, belt converters using an internal combustion engine as their driving source were incapable of keeping the output torque of the engine constant with respect to the output shaft revolutions thereof. More-over, this type of belt converters was liable to develop changes in revolutions. For these reasons, such conventional belt converters have incorporated a centrifugal clutch 56 (56a) wherein the clutch inner 66 (66a) and clutch outer 68 (68a) engage with each other typically at about 3,000 rpm. This means that power transmission is apt to be irregular under the 3,000 rpm threshold. In the second embodiment, by contrast, the output torque of the motor 18 is held constant relative to the revolutions thereof as in the segment a of the motor revolution vs. shaft output characteristic in Fig. 4. With little fluctuation in the number of revolutions, the centrifugal clutch 56 may be engaged illustratively at revolutions as low as 500 rpm. As described above, differences in clutch-engaging revolutions do no prevent the motor 18 from yielding constant torque at low revolutions. In the second embodiment, the centrifugal clutch 56a is located on the side of the motor 18 away from the belt converter A. This arrangement involves less loads connected to the motor 18 in idle state when the centrifugal clutch is disengaged than the setup wherein the relative positions of the centrifugal clutch 56a and belt converter A are reversed. Furthermore, the above arrangement lowers the number of revolutions at which to engage the centrifugal clutch 56a regardless of the reduction ratio adopted by the belt converter A. Because the driving pulley rotates faster than the driven pulley in the belt converter A, the centrifugal clutch 56a may be manufactured small in diameter. One benefit of this feature is a smaller and more lightweight centrifugal clutch 56a. Since the centrifugal clutch 56a is driven direct by the motor 18, the number of revolutions at which to engage the clutch is increased. This is another factor contributing to making the centrifugal clutch 56a smaller and lighter than before. As a result, the motor 18 as employed by the invention consumes less power than in prior art setups. As described, the vehicle power transmission apparatus according to the invention comprises a belt type stepless speed change device and is for use with a vehicle driving prime motor on board a vehicle. The apparatus provides a flat characteristic segment covering at least a part of the shaft output characteristic relative to the revolutions of the vehicle driving prime motor. The invention when embodied allows the vehicle to be driven by constant shaft output within the segment of the flat shaft output characteristic regardless of secular changes in the frictional force of the belt in the belt type stepless speed change device. This results in little adverse effect on the variable power transmission characteristic based on the frictional force of the belt in the belt type stepless speed change device. A major benefit of the invention is that little deterioration occurs over time in the power transmission characteristic of a used vehicle as compared with the initial state of the newly manufactured vehicle. Even if secular changes in the frictional force of the belt in the belt type stepless speed change device alter the number of revolutions of the vehicle driving prime motor whose speed is varied in stepless fashion, the vehicle is still driven by constant shaft output within the range of revolutions of the prime motor. By using an electric motor for the vehicle driving prime motor, it is easy to obtain a segment of the flat shaft output characteristic with respect to the number of revolutions.

Claims: A vehicle power transmission apparatus comprising: a belt type stepless speed change devive (A) for use with a vehicle for providing a driving force from an electric motor (18) to a driven wheel (WR) operatively connected to said vehicle, said speed change device (A) providing a high and a low gear ratio and having a variable speed characteristic such as to provide a momentarily substantially constant revolutions-per-time-unit-value over a variable speed characteristic region (b) between said high and said low gear ratios with respect to the speed (km/h) of said vehicle; a control circuit (25, 27) operatively connected to said electric motor (18), said control circuit including means (23) for detecting the current motor revolutions per time unit (rpm) via the rotational speed of an output shaft (24) of said electric motor; a switching circuit (29) for supplying current to the electric motor (18), said control circuit (25, 27) supplying pulses to said switching circuit (29) for controlling a duty factor of said current; characterized by said control circuit (25, 27) further including: storage means (27) for storing a predetermined characteristic table (Fig. 4) giving a desired shaft power output (kW) as a function of the motor revolutions per time unit (rpm), calculation means adapted to calculate the current shaft power output (kW) on basis of the current flowing through the electric motor (18) and the current motor revolutions per time unit (rpm) and comparing means (25) for comparing said current shaft output (kW) with the desired shaft power output (kW) given for the current motor revolutions per time unit by said characteristic table (Fig. 4); said control circuit (25, 27) controlling, on basis of said comparison, the duty factor in such a manner via said pulses that the shaft output power (kW) is substantially constant over at least one discrete range (b, c) of motor revolutions per time unit (rpm) as given by the predetermined characteristic table (Fig. 4), wherein one (b) of said at least one discrete range (b, c) of motor revolutions per time unit (rpm) providing substantially constant shaft output power (kW) comprises said momentarily substantially constant revolutions-per-time-unit-value (rpm). A vehicle power transmission apparatus, according to claim 1, wherein one (c) of said at least one discrete range (b, c) of motor revolutions per time unit (rpm) providing substantially constant shaft output power (kW) comprises the motor revolutions per time unit (rpm) in a maximum vehicle speed region (c), in which the speed change device (A) provides the high gear ratio.

Inventors: FUJII TAKAAKI, IWADATE TORU, KAWAGUCHI KENJI, MOHARA TOSHINARI, NISHIHARA SEIICHI, SUGIOKA KOUICHI, YAMAMOTO SADASHI, FUJII, TAKAAKI, IWADATE, TORU, KAWAGUCHI, KENJI, MOHARA, TOSHINARI, NISHIHARA, SEIICHI, SUGIOKA, KOUICHI, YAMAMOTO, SADASHI, FUJII, TAKAAKI KABUSHIKI KAISHA HONDA, IWADATE, TORU KABUSHIKI KAISHA HONDA, KAWAGUCHI, KENJI KABUSHIKI KAISHA HONDA, MOHARA, TOSHINARI KABUSHIKI KAISHA HONDA, NISHIHARA, SEIICHI KABUSHIKI KAISHA HONDA, SUGIOKA, KOUICHI KABUSHIKI KAISHA HONDA, YAMAMOTO, SADASHI KABUSHIKI KAISHA HONDA
Applicants: HONDA MOTOR CO LTD, HONDA GIKEN KOGYO KABUSHIKI KAISHA
Application year: 1993
Main classification: B62M9
IPC codes: B60L11, B62M7, B60K20, F16H9, B62M9, B62M23, B60L15