JP5471202B2 - Hybrid drive mechanism, vehicle and control method thereof - Google Patents

Description

  The present invention relates to a hybrid drive mechanism including an internal combustion engine, a motor generator, and a continuously variable transmission, a vehicle, and a control method thereof.

  The configuration of a hybrid vehicle provided with an internal combustion engine and a motor generator as an existing power source is roughly as shown in FIGS. In the configuration of FIG. 5, a motor generator (generator / motor) 4 is attached between a clutch 2 connected to an internal combustion engine (engine) 1 and a continuously variable transmission (CVT) 3. That is, the internal combustion engine 1, the clutch 2, the motor generator 4, and the continuously variable transmission 3 are connected in this order, and a driving force is output from the continuously variable transmission 3 to the wheels.

  6 has a motor generator 4 attached between the internal combustion engine 1 and the clutch 2. In this configuration, the internal combustion engine 1, the motor generator 4, the clutch 2, and the continuously variable transmission 3 are used. Are connected in this order, and driving force is output from the continuously variable transmission 3 to the wheels. In the configuration of FIG. 7, the motor generator 4 is attached to the rear of the continuously variable transmission 3. In this configuration, the internal combustion engine 1, the clutch 2, the continuously variable transmission 3, and the motor generator 4 are connected in this order. Then, driving force is output from the continuously variable transmission 3 to the wheels. On the other hand, in the configuration of FIG. 8, a planetary gear 5 is provided behind the internal combustion engine 1, and a driving motor (motor) 6 and a generator (generator) 7 are attached to the planetary gear 5.

  When the configuration shown in FIGS. 5, 7, and 8 is adopted, as shown in FIG. 9, the power generation amount of the motor generator 4 or the generator 7 indicated by the vertical axis is the vehicle speed indicated by the horizontal axis. Although it rapidly increases and changes, there is a problem that power cannot be generated when the vehicle speed is 0 (km / h), that is, when the vehicle is stopped.

  Further, when the configuration as shown in FIG. 6 is adopted, power generation is possible even when the vehicle is stopped, but as shown in FIG. 10, the amount of power generation changes as the engine speed of the internal combustion engine 1 changes. Therefore, there is a problem that it is difficult to perform a power generation operation at the highest efficiency point of the motor generator 4 during traveling.

  As a vehicle drive device in this hybrid vehicle, for example, in a hybrid vehicle including an engine and a motor as drive sources with the aim of improving fuel efficiency, a planetary gear mechanism disposed between the engine and the motor and the front wheel of the vehicle; There has been proposed a drive device for a hybrid vehicle including a speed change mechanism disposed between a rear wheel of the vehicle and an engine (see, for example, Patent Document 1).

  On the other hand, a continuously variable transmission using a conical planetary gear mechanism has been proposed. For example, in a planetary gear mechanism, a carrier that rotates together with an input shaft that is rotatably supported by a case, and is rotatably supported by the carrier. A conical (tapered) planetary gear, a planetary gear that rotates integrally with the planetary gear, an output gear that meshes with the planetary gear, a gear that rotates integrally with the output gear, and that is rotatably supported by the case The transmission ring is configured to include an output shaft and a transmission ring that is provided so as not to rotate with respect to the case and that is movable to change the frictional contact position with the planetary gear by a transmission operation mechanism. With this movement, a planetary friction wheel type continuously variable transmission has been proposed in which the output shaft rotates forward, stops, and reverses with respect to the rotation of the input shaft (see, for example, Patent Document 2).

JP 2008-290613 A JP-A-10-115356

  The present invention has been made in view of the above situation, and its object is to generate power even when the vehicle is stopped in view of the problem that the power generation amount of the generator of the hybrid vehicle depends on the vehicle speed or the engine speed. In addition, an object of the present invention is to provide a hybrid drive mechanism, a vehicle, and a control method therefor that can perform a power generation operation of a motor generator at the highest efficiency point during traveling.

Hybrid drive mechanism for achieving the above object, the hybrid drive system having an internal combustion engine and the transmission and the motor generator, as well as constructed by connecting the transmission to the internal combustion engine, the transmission, The planetary friction wheel type continuously variable transmission is configured to be connected to the rotation shaft of the internal combustion engine, and is rotatable in a case of the planetary friction wheel type continuously variable transmission. A supported input shaft, a carrier that rotates together with the input shaft, a planetary friction wheel rotatably supported by the carrier, a tapered roller that is a part of the planetary friction wheel, and a part of the planetary friction wheel. A second roller that rotates integrally with the taper roller, a ring roller that rotates in contact with the second roller, an output shaft that rotates integrally with the ring roller and is rotatably supported by the case And said A transmission ring that is non-rotatable with respect to the input shaft and that is movable only in the axial direction of the input shaft, and the transmission ring is moved in the axial direction of the input shaft, A speed change operation mechanism that changes a contact position with the taper roller ; and a sun roller that rotates in contact with a second roller that is a part of the planetary friction wheel; and the rotation of the input shaft rotates the output shaft and the sun roller. The output shaft is forwardly rotated, stopped, and reversely rotated with respect to the rotation of the input shaft by changing the contact position between the speed change ring and the taper roller by the speed change operation mechanism. further wherein connecting the motor generator, configured to generate power by rotating the motor generator by the rotation of the input shaft to the end of the rotating shaft of the sun roller of the planetary friction wheel continuously variable transmission .

  According to this configuration, even when the rotation of the internal combustion engine is transmitted to the input shaft and the internal combustion engine rotates at a certain engine speed, the contact position between the transmission ring and the taper roller is at a specific position (neutral point). In some cases, the rotation of the output shaft stops. Utilizing this fact, when the rotation of the output shaft is stopped, that is, when the vehicle is stopped, the rotation of the internal combustion engine is continuously transmitted to the input shaft, and the sun roller of the planetary friction vehicle continuously variable transmission is rotated. Therefore, it is possible to generate electric power by rotating the motor generator connected to the end of the rotating shaft of the sun roller by the rotation of the internal combustion engine. As a result, power generation is possible even when the vehicle is stopped.

  In addition, even during traveling, the output shaft can be rotated at a continuously variable speed relative to the rotation of the input shaft by changing the contact position between the speed change ring and the taper roller in the planetary friction wheel type continuously variable transmission. Since the vehicle speed can be changed while maintaining the rotation speed or maintaining the rotation speed of the sun roller, the rotation of the internal combustion engine is transmitted to the motor generator via the sun roller to generate power at the highest efficiency point. Is possible.

  In other words, regardless of the rotational speed of the internal combustion engine, the vehicle can be stopped with the output shaft rotating at zero, and the rotational speed of the output shaft during travel can be changed by changing the contact position between the transmission ring and the taper roller. Therefore, it is possible to generate power at the highest efficiency point of the motor generator by changing the vehicle speed and engine speed so that the motor generator speed is optimal for the power generation efficiency even during travel. .

  Further, during driving, the output of the internal combustion engine can be supplemented by driving the motor generator with power supplied from a battery or the like.

  In the above hybrid drive mechanism, two planetary friction wheel type continuously variable transmissions are arranged such that the ring roller side faces each other across an output ring that transmits rotation to an output shaft. When the output ring is configured to rotate, the contact pressure of each roller is reduced, or the planetary friction wheel type continuously variable transmission is downsized, the motor generator is downsized, or the number of motor generators is increased. The effect of increasing the output can be achieved.

  Further, in the above hybrid drive mechanism, the rotation shaft of the sun roller of one planetary friction type continuously variable transmission can be connected to the rotation shaft of the sun roller of the other planetary friction type continuously variable transmission, and It is configured to be able to be disconnected, and when connected, the rotation is transmitted from one sun roller to the other sun roller, and when disconnected, the rotation is not transmitted to each other, and the motor generator is connected to one planetary friction vehicle. It is configured to be provided only on the rotating shaft of the sun roller of the type continuously variable transmission.

  In other words, the shaft of one sun roller and the shaft of the other sun roller are coupled by, for example, a spline shaft that is movable in the axial direction so that the other sun roller can be driven with respect to each other. A single motor generator is attached to and configured.

  According to this structure, the effect of reducing the surface pressure of the contact part of each roller, or downsizing the planetary friction wheel type continuously variable transmission and unifying the motor generator can be achieved.

  In the hybrid drive mechanism described above, at least one rotation transmission among the rotation transmission of the taper roller, the rotation of the ring roller, the rotation of the sun roller, and the rotation of the transmission ring is performed. Except between the taper roller and the transmission ring, the rotation transmission by the roller is replaced with the rotation transmission by the gear.

  According to this configuration, the friction wheel type is transmitted by friction, so the transmission efficiency is relatively low, whereas the gear type has the effect that a higher transmission efficiency can be obtained compared to the friction wheel type. Can play.

  A vehicle for achieving the above object includes the above hybrid drive mechanism. According to this vehicle, even when the vehicle is stopped, it is possible to generate electric power by rotating the motor generator with the output of the internal combustion engine, and when the vehicle is running, the motor generator is operated at the highest efficiency point. Power generation. Further, when the vehicle is running, the output of the internal combustion engine can be supplemented by supplying power to the motor generator. As a result, fuel consumption is improved.

  According to another aspect of the vehicle control method for achieving the above object, when the vehicle is stopped during operation of the internal combustion engine, the contact position between the transmission ring and the taper roller is output. The shaft is moved to a position where rotation of the shaft is stopped, and the motor generator is rotated to generate electric power.When the output of the internal combustion engine is larger than energy required for traveling when the vehicle is traveling, In response to changes in the vehicle speed by changing the contact position with the taper roller, the motor generator is rotated to generate power, and when the output of the internal combustion engine is smaller than the energy required for traveling when the vehicle is traveling The method of driving the motor generator to compensate for the output of the internal combustion engine while responding to a change in vehicle speed by changing the position of the contact position between the transmission ring and the taper roller. That.

  According to this method, even when the vehicle is stopped, it is possible to generate electric power by rotating the motor generator with the output of the internal combustion engine, and when the vehicle is running, the motor generator is operated at the highest efficiency point. Power generation. Further, when the vehicle is running, the output of the internal combustion engine can be supplemented by supplying power to the motor generator. As a result, fuel consumption is improved.

  According to the hybrid drive mechanism, the vehicle, and the control method thereof according to the present invention, even when the vehicle is stopped, it is possible to generate electric power by rotating the motor generator with the output of the internal combustion engine. It becomes possible to generate electric power by operating the motor generator at the highest efficiency point.

It is the figure which showed the structure of the hybrid drive mechanism of the 1st Embodiment of this invention. It is the figure which showed another structure of the hybrid drive mechanism of the 1st Embodiment of this invention. It is the figure which showed the structure of the hybrid drive mechanism of the 2nd Embodiment of this invention. It is the figure which showed the structure of the hybrid drive mechanism of the 3rd Embodiment of this invention. It is the figure which showed the structure of the 1st hybrid drive mechanism of a prior art. It is the figure which showed the structure of the 2nd hybrid drive mechanism of a prior art. It is the figure which showed the structure of the 3rd hybrid drive mechanism of a prior art. It is the figure which showed the structure of the 4th hybrid drive mechanism of a prior art. It is the figure which showed the relationship between the vehicle speed in the 1st, 3rd, and 4th hybrid drive mechanism of a prior art, and electric power generation amount. It is the figure which showed the relationship between the engine speed in the 2nd hybrid drive mechanism of a prior art, and electric power generation amount. It is a figure which shows a loading cam part. It is XX sectional drawing which shows the state of the loading cam part of the state at the time of no load. It is XX sectional drawing which shows the state of the loading cam part of the state at the time of load. It is a partial front view which shows the structure of a differential and loading mechanism. It is a partial side view which shows the structure of the differential and loading mechanism of FIG. It is a partial front view which shows another structure of a differential and loading mechanism. It is a partial side view which shows the structure of the differential and loading mechanism of FIG. FIG. 18 is a partial side view showing a state changed from the state of FIG. 17 in the differential and loading mechanism of FIG. 16.

  Hereinafter, a hybrid drive mechanism, a vehicle, and a control method thereof according to embodiments of the present invention will be described with reference to the drawings. In this example, the planetary friction wheel type continuously variable transmission in which the rotation transmission medium is formed by a roller that transmits the rotation by friction is described. However, the rotation transmission medium transmits the rotation by meshing the gear teeth. It may be formed by a planetary gear type continuously variable transmission. Further, although all of the rollers may be replaced with gears, only a part of the rollers may be replaced with gears, and a combination of gears and rollers may be used.

  1 and 2 show the configuration of the hybrid drive mechanism 10 according to the first embodiment of the present invention. The hybrid mechanism 10 includes an engine (internal combustion engine) (not shown), a continuously variable transmission 20, and a motor generator 30, and an input shaft 22 of the continuously variable transmission 20 is connected to an output shaft of the engine. A wheel (not shown) is driven by the output shaft 28 of the continuously variable transmission 20, and power is generated by the motor generator 30 connected to the sun roller 25 of the continuously variable transmission 20. For convenience of explanation, the input shaft 22 side to which the engine is connected is the front side (arrow A side), and the output shaft 28 side that drives the wheels is the rear side (arrow B side).

  The hybrid mechanism 10 includes a planetary friction wheel type continuously variable transmission 20, and the planetary friction wheel type continuously variable transmission 20 is configured as follows. The motor generator 30 is connected to the end of the rotary shaft 25 c of the sun roller 25 of the continuously variable transmission 20, and the motor generator 30 is rotated by the rotation of the input shaft 22 of the continuously variable transmission 20. In the configuration of FIG. 1, the motor generator 30 is connected to the rear end of the sun roller 25, and in the configuration of FIG. 2, the motor generator 30 is connected to the front end of the sun roller 25.

  As shown in FIGS. 1 and 2, main components of the planetary friction wheel type continuously variable transmission 20 include a case 21, an input shaft 22, a carrier 23, a planetary friction wheel 24 having a taper roller 24b, a sun roller 25, a ring. There are a roller 26, a loading cam 27, an output shaft 28, a transmission ring (outer roller) 29, and the like.

  The input shaft 22 is connected to the rotation shaft of the engine and is supported rotatably with respect to the case 21. A disk-shaped carrier 23 whose outer peripheral side is bent rearward is fixed to the input shaft 22, and the carrier 23 is connected to a plurality of planetary friction wheels 24 via a support mechanism such as a bearing 23 a provided on the carrier 23. It is rotatably supported and is configured to rotate with the rotation of the input shaft 22.

  There are a plurality of planetary friction wheels 24, for example, about three to five, around the input shaft 22 that is the rotation shaft of the carrier 23 so that they are equidistant from the center of the input shaft 22 and in the circumferential direction. It arrange | positions so that it may become equal intervals. The planetary friction wheel 24 is provided with a first roller 24a, a taper roller 24b, and a second roller 24c from the carrier 23 side. These rollers 24a, 24b, and 24c are configured to rotate integrally around a rotation shaft 24d.

  The first roller 24a and the second roller 24c are in contact with the first roller 25a and the second roller 25b of the sun roller 25, respectively, and rotate the sun roller 25 around the rotation shaft 25b. The rotation shaft 25 c of the sun roller 25 is configured to have an axis on the same straight line as the axis of the input shaft 22. Further, the taper roller 24 b comes into contact with the transmission ring 29 that does not rotate with respect to the case 21, and rotates (rotates) together with the rotation (revolution) of the carrier 23.

  The tapered roller 24b is formed in a tapered shape (conical shape) in which the outer diameter on the front side is small and the outer diameter on the rear side is increased so that the outer peripheral side thereof is parallel to the input shaft 22, and is inclined at an inclination angle α. In this state, the taper roller 24b, that is, the planetary friction wheel 24 is rotatably supported by the carrier 23. More specifically, the inclination angle β formed by the outer peripheral side of the taper roller 24b and the rotation shaft 24d of the planetary friction wheel 24 is the same as the inclination angle α formed by the rotation shaft 24d of the planetary friction wheel 24 and the input shaft 22. (Α = β).

The second roller 24c contacts the inner peripheral side of the ring roller 26 and the second roller 25b of the sun roller 25, and rotates these rollers 26 and 25b.

  The ring roller 26 rotates the output shaft 28, which is arranged on the same straight line as the input shaft 22, via the loading cam 27. The output shaft 28 is rotatably supported by a bearing 21 b of the case 21.

  This loading cam 27 is a portion in which the ring roller 26 and the output shaft 28 are tapered in a rotational direction like a V-shaped groove or an arc-shaped groove (the internal components when the ring roller 26 and the output shaft 28 are displaced, The ring roller 26 and the portion where the output shaft 28 is extruded in the axial direction) have a spherical or columnar cam in the above-mentioned groove portion, and when a load is applied, it acts on the contact point of each roller Plays a role in increasing power. An example of the shape is shown in FIG. 11, FIG. 12 shows a no-load state, and FIG. 13 shows a load state.

The carrier 23 presses the front surface 25e of the sun roller 25 to the rear side via the pressurizing spring 23b and the bearing 25d.

  The transmission ring 29 is provided so as not to rotate with respect to the case 21 with respect to the rotational direction, but is configured to be movable in the axial direction of the input shaft 22, that is, in the front-rear direction (AB direction). The speed change ring 29 is configured to move in the front-rear direction by a control operation signal (not shown) manually or by a speed change operation mechanism (not shown) to move the contact point with the inclined surface of the taper roller 24b. .

  As a moving mechanism of the transmission ring 29, for example, the transmission ring 29 is screwed and supported by a plurality of screw shafts 29a provided in the case 21 in parallel with the axial direction of the input shaft 22, and the plurality of screw shafts are supported. At least one of 29a is configured to transmit rotation from a speed change motor (not shown) formed by a step motor or the like to control the rotation of the screw shaft 29a. This speed change motor is rotated forward or reverse manually or by a control signal from a control device (not shown). As a result, the transmission ring 29 is moved in the axial direction of the input shaft 22 with the rotation of the screw shaft 29a, and the contact position between the transmission ring 29 and the taper roller 24b is moved in the front-rear direction.

  Next, rotation transmission in the planetary friction wheel type continuously variable transmission 20 having the above-described configuration will be described. When the input shaft 22 connected to the output shaft of the engine rotates, the carrier 23 fixed to the input shaft 22 rotates and the planetary friction wheel 24 supported by the carrier 23 revolves. Since the taper roller 24b of the revolving planetary friction wheel 24 is in contact with the speed change ring 29 that is fixed to the case 21 and does not rotate, it rotates.

Since the second roller 24 c of the planetary friction wheel 24 is in contact with the inner peripheral side of the ring roller 26, the ring roller 26 is rotated by the rotation of the planetary friction wheel 24. Further, the ring roller 26 rotates the output shaft 28 via the loading cam 27. At the same time, since the first roller 24a and the second roller 24c of the planetary friction wheel 24 are in contact with the first roller 25a and the second roller 25b of the sun roller 25, respectively, the sun roller 25 is rotated.

  At this time, if the rotation direction of the input shaft 22 is forward rotation, the planetary friction wheel 24 rotates in the reverse rotation direction while revolving in the forward rotation direction. The planetary friction wheel 24 rotates at the rotation speed Nb with respect to the revolution speed Na. The relationship between the revolution speed Na and the rotation speed Nb is proportional to the ratio ηa (= Ra / Rb) between the inner diameter Ra of the speed change ring 29 and the outer diameter Rb of the portion where the speed change ring 29 of the taper roller 24b is in contact. Nb = Na × ηa.

  The ring roller 26 is rotated by the second roller 24c of the planetary friction wheel 24. The rotation speed Nc of the ring roller 26 with respect to the rotation speed Nb of the planetary friction wheel 24 is the second rotation speed of the planetary friction wheel 24 at the contact point. It is proportional to the ratio ηb (Rc / Rd) related to the outer diameter (Rc) of the roller 24c and the inner diameter (Rd) of the ring roller 26. That is, Nc = Nb × ηb.

  On the other hand, the rotational speed Nd of the ring roller 26 with respect to the case 21 is Nd = Nc−Na = Na (ηa × ηb−1) in consideration of the revolution rotational speed Na. Here, the ratio ηb (= Nc / Nb) of the rotational speed Nc of the ring roller 26 to the rotational speed Nb of the planetary friction wheel 24 is fixed, but a ratio indicating the relationship between the revolution speed Na and the rotational speed Nb. ηa varies depending on the front and rear positions of the transmission ring 29.

  Further, the first roller 25a and the second roller 25b of the sun roller 25 are respectively rotated by the first roller 24a and the second roller 24c of the planetary friction wheel 24, and the sun roller 25 with respect to the rotation speed Nb of the planetary friction wheel 24. Is proportional to the ratio ηc (Re / Rf) related to the outer diameter (Re1) of the first roller 24a of the planetary friction wheel 24 and the outer diameter (Rf1) of the first roller 25a of the sun roller 25 at the contact point. To do. That is, Ne = Nb × ηc. In order to smoothly transmit the rotation, the ratio (Re2 /) of the outer diameter (Re2) of the second roller 24c of the planetary friction wheel 24 and the outer diameter (Rf2) of the second roller 25b of the sun roller 25 at the contact point. Rf2) is formed to have the same ratio (Re1 / Rf1) between the outer diameter (Re1) of the first roller 24a of the planetary friction wheel 24 and the outer diameter (Rf1) of the first roller 25a of the sun roller 25 at the contact point.

  Further, the rotation speed Nf of the sun roller 25 with respect to the case 21 is Nf = Ne−Na = Na (ηa × ηc−1) in consideration of the revolution rotation speed Na. Here, the ratio ηc (= Nc / Nb) of the rotation speed Ne of the sun roller 25 to the rotation speed Nb of the planetary friction wheel 24 is fixed, but the ratio ηa indicating the relationship between the revolution speed Na and the rotation speed Nb. Changes depending on the front and rear positions of the transmission ring 29.

  Here, a contact point between the transmission ring 29 in the front-rear direction and the taper roller 24b where the inner diameter Ra of the transmission ring 29 and the inner diameter Rb of the taper roller 24b satisfy (Ra / Rb) = ηa = 1 / ηb is defined as a neutral point Pn. When the transmission ring 29 is at the neutral point Pn, the rotational speed Nd of the output shaft 28 becomes zero regardless of the rotational speed Na of the input shaft 22. On the other hand, the rotational speed Nf of the sun roller 25 is Nf = Na (ηa × ηc−1) = Na (ηc / ηb−1), and unless ηc = ηb, the sun roller 25 rotates without stopping.

  Here, the ratio ηa (= Ra / Rb) of the rotation speed Nb with respect to the revolution speed Na can be changed depending on the contact position of the transmission ring 29 and the taper roller 24b, in other words, the position of the transmission ring 29 in the front-rear direction. When the contact position is ahead of the neutral point Pn, ηa is larger than (1 / ηb), so Nd = Nc−Na = Na × ηb × (ηa−1 / ηb) is positive and the output The shaft 28 rotates at the rotation speed Nd in the same direction as the input shaft 22. On the other hand, when the contact position is behind the neutral point Pn, ηa is smaller than (1 / ηb), so Nd = Nc−Na = Na × ηb × (ηa−1 / ηb) is negative. The output shaft 28 rotates in the opposite direction to the input shaft 22 at a rotational speed −Nd. When the contact position is at the neutral point Pn, as described above, ηa is equal to (1 / ηb), so Nd = Nc−Na = Na × ηb × (ηa−1 / ηb) is zero. Even though the input shaft 22 is rotating, the output shaft 28 has stopped rotating.

  As described above, the rotation of the output shaft 28 can change the rotation speed and the rotation direction according to the contact position of the transmission ring 29 and the taper roller 24b with respect to the rotation of the input shaft 22, and continuously steplessly. The rotation speed can be changed with.

  On the other hand, if the rotation of the sun roller 25 is not ηc = ηb, the output shaft 28 rotates without stopping even if the output shaft 28 stops. Therefore, the ratio ηb (Rc / R) is set so that ηc becomes a value different from ηb. Rd) is related to the outer diameter (Rc) of the second roller 24c of the planetary friction wheel 24, the inner diameter (Rd) of the ring roller 26, and the second diameter of the planetary friction wheel 24 is related to the ratio ηc (Re2 / Rf2). An outer diameter (Re2≈Rc or Re2 = Rc) of the roller 24b and an outer diameter (Rf2) of the second roller 25b of the sun roller 25 are formed. Further, based on this ratio ηc (Re2 / Rf2), the planetary friction wheel An outer diameter (Re1) of 24 first rollers 24a and an outer diameter (Rf1) of the first roller 25a of the sun roller 25 are formed.

Next, a hybrid drive mechanism according to a second embodiment will be described. As shown in FIG. 3, in this hybrid drive mechanism 10A, two planetary friction wheel type continuously variable transmissions 20A and 20B are arranged, and the rotation shafts 25Ac and 25Bc of the sun rollers 25A and 25B are arranged on a straight line. At the same time, the output rollers 31 that transmit rotation to an output shaft (not shown) are sandwiched between the ring rollers 26A and 26B so that the ring rollers 26A and 26B rotate the same output ring 31. A differential and loading mechanism 32 is provided.

The differential / loading mechanism 32 absorbs the speed difference between the ring rollers 26A and 26B by the rotation of the differential / loading mechanism 32, and each load is applied in the same manner as the loading cam 27 described above. The pressing force of the roller is increased. Examples of the structure of the differential and loading mechanism 32 are shown in FIGS.

  The motor generator 30A is connected to the rotating shaft 25Ac of the sun roller 25A of the planetary friction wheel type continuously variable transmission 20A, and the motor generator 30B is connected to the rotating shaft 25Bc of the sun roller 25B of the planetary friction wheel type continuously variable transmission 30B. Is done.

  According to this configuration, the effect of reducing the surface pressure at the contact portion of each roller, or downsizing the planetary friction wheel type continuously variable transmission, downsizing the motor generator, or increasing the output due to an increase in the number of motor generators. Can be played.

Next, a hybrid drive mechanism according to a third embodiment will be described. As shown in FIG. 4, in this hybrid drive mechanism 10B, as in the hybrid drive mechanism 10A of the second embodiment, two planetary friction wheel type continuously variable transmissions 20A and 20B described above are provided. The rotary shafts 25Ac and 25Bc of 25A and 25B are arranged on a straight line, and are arranged so that the ring rollers 26A and 26B face each other across the output ring 31 that transmits the rotation to the output shaft (not shown). A differential and loading mechanism 32 is provided so that the ring rollers 26A and 26B rotate the output ring 31.

  Further, the rotation shaft 25Ac of the sun roller 25A of one planetary friction wheel type continuously variable transmission 20A and the rotation shaft 25Bc of the sun roller 25B of the other planetary friction wheel type continuously variable transmission 20B can be connected and disconnected. It is configured to transmit rotation from one sun roller 25A (or 25B) to the other sun roller 25B (25A) at the time of connection and not to transmit rotation to each other at the time of disconnection. It is provided only on the rotation shaft 25Ac of the sun roller 25A.

  That is, the rotation shaft 25Ac of one sun roller 25A and the rotation shaft 25Bc of the other sun roller 25B are coupled by, for example, a spline shaft movable in the axial direction, and when connected, the other sun roller 25B (25A) is driven. Configure as you can. Further, one motor generator 30 is attached only to the rotation shaft 25Ac (25Bc) of one sun roller 25A (25B).

  And the vehicle of this invention is comprised including said hybrid drive mechanism 10, 10A, 10B.

  Next, a control method for a vehicle configured to include the hybrid drive mechanisms 10, 10A, 10B will be described. In this vehicle control method, when the vehicle is stopped while the engine is operating, the contact position between the transmission ring 29 and the taper roller 24b is moved to the position Pn where the rotation of the output shaft 28 stops. When the motor generators 30, 30A, 30B are rotated to generate power and the engine output is larger than the energy required for traveling, the contact position between the transmission ring 29 and the taper roller 24b can be changed. While responding to changes in vehicle speed, the motor generators 30, 30 </ b> A, 30 </ b> B are rotated to generate power, and when the output of the engine is smaller than the energy required for traveling when the vehicle is traveling, The motor generators 30, 30 </ b> A, and 30 </ b> B are driven to compensate for engine output while responding to changes in vehicle speed by changing the contact position with the taper roller 24 b.

  According to the hybrid drive mechanisms 10, 10 </ b> A, 10 </ b> B configured as described above, and the vehicle including these hybrid drive mechanisms 10, 10 </ b> A, 10 </ b> B, and the vehicle control method, the rotation of the engine (internal combustion engine) When it is transmitted to the input shaft 22 of the continuously variable transmission 20, 20A, 20B and the engine rotates at a certain engine speed Na, that is, the carrier 23 rotates at the engine speed Na, and the sun roller 25 rotates. Even when rotating at Nf, if the contact position between the transmission rings 29, 29A, 29B and the taper roller 23 is at a specific position, that is, at the neutral point Pn, the output shaft 28 or the output ring 31 is rotated. Stop.

  By utilizing this, even when the vehicle is stopped when the rotation of the output shaft 26 is stopped, the rotation of the engine can be transmitted to the input shaft 22 to rotate the sun rollers 25, 25A, 25B. , The motor generators 30, 30A, 30B connected to the ends of the rotary shafts 25c, 25Ac of the sun rollers 25, 25A can be rotationally driven to generate electric power. As a result, power generation is possible even when the vehicle is stopped.

  Further, even during traveling, by changing the contact position between the transmission ring 29 and the taper toe 24b, the rotation of the output shaft 28 can be continuously variable with respect to the rotation of the input shaft 22, so that the vehicle speed changes. However, the vehicle speed can be easily changed by changing the rotational speed Nd of the output shaft 28 while maintaining the engine rotational speed Na. Therefore, it becomes possible to operate the motor generators 30, 30A, 30B, in which the rotation of the engine is transmitted through the rotation of the sun rollers 25, 25A, 25B, at the highest efficiency point.

  That is, regardless of the engine speed Na, the vehicle can be maintained in a stopped state, and the output speed Nd during travel can be changed depending on the front and rear positions of the transmission ring 29. It is possible to operate at the highest efficiency point of the motor generators 30, 30A, 30B while maintaining the engine speed Na and the rotational speed Nf of the sun rollers 25, 25A, 25B at a speed with good power generation efficiency. .

  Further, during running, the motor generators 30, 30A, 30B can be driven by feeding power from a battery or the like, thereby making it possible to supplement the engine output.

  According to the hybrid drive mechanism, the vehicle, and the control method thereof of the present invention, even when the vehicle is stopped, it is possible to generate electric power by rotating the motor generator with the output of the internal combustion engine. Since the generator can be operated at the highest efficiency point to generate electric power, it can be used as a hybrid drive mechanism, a vehicle and a control method thereof in a vehicle such as an automobile.

10, 10A, 10B Hybrid drive mechanism 20, 20A, 20B Planetary friction wheel type continuously variable transmission 30, 30A, 30B Motor generator 25, 25A, 25B Sun roller 25c, 25Ac, 25Bc Sun roller rotation shaft 21 Case 22 Input shaft 23 Carrier 24 Planetary friction wheel 24a Planetary friction wheel first roller 24b Tapered roller 24c Planetary friction wheel second roller 24d Planetary friction wheel rotation shaft 25 Sun roller 25a Sun roller first roller 25b Sun roller second roller 25c Sun roller rotation shaft
26, 26A, 26B Ring roller 27 Loading cam 28 Output shaft 29 Speed change ring A Front side (input shaft side)
B Rear side (output shaft side)
Na revolution speed Nb rotation speed Nc rotation speed of ring roller with respect to rotation speed of planetary friction wheel Nd rotation speed with respect to ring roller case Ne rotation speed of sun roller with respect to rotation speed of planetary friction wheel Ra inner diameter of transmission ring Nf sun roller Rotational speed Pn Neutral point Ra Inner diameter of transmission ring Rb Outer diameter of tapered roller transmission ring in contact Rc Outer diameter of second roller of planetary friction wheel at contact point Rd Inner diameter of ring roller at contact point Re1 Outer diameter of first roller of planetary friction wheel at contact point Re2 Outer diameter of second roller of planetary friction wheel at contact point Rf1 Outer diameter of first roller of sun roller at contact point Rf2 Outer diameter of second roller of sun roller α Planet Inclination angle between the rotating shaft of the friction wheel and the input shaft β The outer circumference of the taper roller and planetary friction Inclination angle ηa ratio formed between the rotary shaft (= Ra / Rb)
ηb ratio (= Rc / Rd)
ηc ratio (= Re / Rf = Re2 / Rf2)

Claims (6)

In the hybrid drive system having an internal combustion engine and the transmission and the motor generator, as well as constructed by connecting the transmission to the internal combustion engine,
The transmission is composed of a planetary friction wheel type continuously variable transmission,
The planetary friction wheel type continuously variable transmission,
Which is connected to the rotating shaft of the internal combustion engine, and an input shaft rotatably supported by the case of the satellite frictional gear continuously variable transmission,
A carrier that rotates with the input shaft;
A planetary friction wheel rotatably supported by the carrier;
A tapered roller that is part of the planetary friction wheel;
A second roller that is part of the planetary friction wheel and rotates integrally with the taper roller;
A ring roller that rotates in contact with the second roller;
An output shaft that rotates integrally with the ring roller and is rotatably supported by the case;
A transmission ring that is provided so as not to rotate with respect to the case, and that is movable only in the axial direction of the input shaft;
A speed change operation mechanism for moving the speed change ring in the axial direction of the input shaft and changing a contact position between the speed change ring and the taper roller;
A sun roller that rotates in contact with a second roller that is part of the planetary friction wheel,
The rotation of the input shaft is transmitted to the output shaft and the sun roller, and the contact position between the transmission ring and the tapered roller is changed by the speed change operation mechanism, whereby the output shaft Is configured to forward, stop, reverse
Furthermore, the motor generator is connected to an end portion of the rotation shaft of the sun roller of the planetary friction wheel continuously variable transmission, and the motor generator is rotated by the rotation of the input shaft to generate power. A hybrid drive mechanism characterized by The two planetary friction wheel continuously variable transmission, across the output ring for transmitting rotation to the output shaft, the arranged so that the ring roller side face each other, each of said ring roller rotates the output ring The hybrid drive mechanism according to claim 1, wherein the hybrid drive mechanism is configured as described above.   The rotating shaft of the sun roller of one of the planetary friction wheel type continuously variable transmission and the rotating shaft of the sun roller of the other planetary friction wheel type continuously variable transmission are configured to be connectable and disengageable. The rotation is transmitted from one sun roller to the other sun roller, and when the break occurs, the rotation is not transmitted to each other, and the motor generator is connected to the sun roller of the planetary friction vehicle continuously variable transmission. The hybrid drive mechanism according to claim 2, wherein the hybrid drive mechanism is provided only on the rotating shaft.   At least one rotation transmission among the rotation of the taper roller, the rotation of the ring roller, the rotation of the sun roller, and the rotation of the transmission ring, except between the taper roller and the transmission ring. The hybrid drive mechanism according to claim 1, wherein the rotation transmission by the roller is replaced with the rotation transmission by a gear.   A vehicle comprising the hybrid drive mechanism according to any one of claims 1 to 4. 6. The vehicle according to claim 5, wherein when the vehicle is stopped during operation of the internal combustion engine, the contact position between the transmission ring and the taper roller is moved to a position where rotation of the output shaft stops, and the motor generator Rotate the machine to generate electricity,
When the output of the internal combustion engine is larger than the energy required for traveling when the vehicle is traveling, the motor generator is rotated while responding to the change in vehicle speed by changing the contact position between the transmission ring and the taper roller. Power generation,
Further, when the output of the internal combustion engine is smaller than the energy required for traveling when the vehicle is traveling, the motor generator is adapted to change in the vehicle speed by changing the position of the contact position between the transmission ring and the taper roller. To control the output of the internal combustion engine.

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