JP2010089634A - Hybrid driving device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hybrid driving device capable of properly changing a relative position of an axial direction between a rotor and a stator of a rotating electric machine according to an operation state of a vehicle without providing an exclusive driving mechanism. <P>SOLUTION: This hybrid driving device includes an input member I connected to an engine E, an output member O connected to a wheel, the rotating electric machine MG having rotor Ro and stator St and connected to the output member O so that driving force may be transmitted, and a transmission TM having an input side rotating member 10 connected to the input member I and an output side rotating member 20 connected to the output member O to change a shift ratio between the input side rotating member 10 and the output side rotating member 20. The transmission TM includes a shift operation part M moving in a prescribed direction according to a change of the shift ratio. Either one of the rotor Ro and the stator St of the rotating electric machine MG is connected to the shift operation part M to be moved in the axial direction by interlocking with moving of the shift operation part M. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention includes an input member connected to an engine, an output member connected to a wheel, a rotor and a stator, a rotating electrical machine connected to the output member so as to be able to transmit a driving force, and the input member A transmission that includes a connected input-side rotating member and an output-side rotating member connected to the output member, and that changes a gear ratio between the input-side rotating member and the output-side rotating member; The present invention relates to a hybrid drive device.

  In recent years, hybrid vehicles that can improve engine fuel efficiency and reduce exhaust gas by combining an engine and a rotating electrical machine as a driving force source have been put into practical use. As an example of a hybrid drive device used in such a hybrid vehicle, for example, a single rotating electric machine is provided in addition to the engine as a driving force source of the vehicle, and the rotation of the engine is continuously variable transmission, stepped automatic transmission, etc. A drive device for a so-called parallel hybrid vehicle has been already known that is configured so as to be able to be shifted by various transmissions and transmitted to the wheels and to transmit the driving force of the rotating electrical machine to the wheels. Here, the rotating electrical machine is configured to be connected to the wheel via a transmission common to the engine (see, for example, Patent Document 1 below), or is connected to the wheel not via a transmission common to the engine. It is set as a structure (for example, refer the following patent document 2).

  In these parallel hybrid vehicle drive devices, the rotating electrical machine rotates at a speed proportional to the speed ratio of the transmission device when the vehicle speed and the transmission device are used. The rotor will also rotate at a high rotational speed. In order to reduce the counter electromotive force generated in the stator coil during such high-speed rotation of the rotor, so-called field weakening control is generally performed. However, this field weakening control has a problem in that the efficiency of the rotating electrical machine is reduced because the phase of the current waveform supplied to the stator coil is shifted from the optimum phase. Therefore, in order to reduce the counter electromotive force generated in the stator coil without performing field-weakening control during high-speed rotation of the rotor, a configuration of a rotating electrical machine having a drive mechanism that moves the rotor in the axial direction with respect to the stator is already known. (For example, refer to Patent Document 3 below). According to this rotating electrical machine, the amount of magnetic flux from the magnet of the rotor crossing the stator coil can be reduced by increasing the deviation of the relative position between the rotor and the stator in the axial direction. Accordingly, the back electromotive force generated in the stator coil can be reduced without performing field-weakening control even when the rotor rotates at high speed.

JP 2000-023313 A JP 2000-220734 A JP 2008-131790 A

  However, in such a rotating electrical machine, it is necessary to include a drive mechanism such as a hydraulic cylinder or a pump for moving the rotor in the axial direction. In addition, in order to use such a rotating electric machine for a drive device of a hybrid vehicle, a control device for appropriately controlling the drive mechanism in accordance with the operating state of the hybrid vehicle is also required. For this reason, the number of parts of the hybrid drive device increases, which causes an increase in cost and increases in weight and volume, resulting in deterioration in mountability on a vehicle.

  The present invention has been made in view of the above problems, and an object thereof is to provide a relative position in the axial direction between the rotor and the stator of the rotating electrical machine according to the operation state of the vehicle without providing a dedicated drive mechanism. An object of the present invention is to provide a hybrid drive device that can appropriately change the above.

  In order to achieve the above object, the present invention has an input member connected to an engine, an output member connected to a wheel, a rotor and a stator, and is connected to the output member so as to be able to transmit a driving force. A rotating electrical machine, an input-side rotating member connected to the input member, and an output-side rotating member connected to the output member, and changing a gear ratio between the input-side rotating member and the output-side rotating member The transmission is characterized in that the transmission includes a transmission operation unit that moves in a predetermined direction in accordance with a change in the transmission ratio, and is either one of a rotor and a stator of the rotating electrical machine. One is that it is connected to the shift operation unit so as to move in the axial direction in conjunction with the movement of the shift operation unit.

  In the present application, “connection” includes not only a structure that directly transmits rotation but also a structure that indirectly transmits rotation via one or more members. In the present application, the “rotary electric machine” is used as a concept including any of a motor (electric motor), a generator (generator), and a motor / generator functioning as both a motor and a generator as necessary. In the present application, “driving force” is used as a concept including torque.

  According to this characteristic configuration, since either the rotor or the stator of the rotating electrical machine can be moved in the axial direction in conjunction with the speed change operation unit provided in the transmission, the rotor or the stator of the rotating electrical machine is moved in the axial direction. There is no need to provide a dedicated drive mechanism for the operation. In addition, since either the rotor or the stator of the rotating electrical machine is moved in the axial direction in conjunction with the speed change operation unit that moves in a predetermined direction according to the change in the speed ratio of the transmission, there is no need to provide a dedicated control device. Thus, the axial relative position of the rotor and the stator of the rotating electrical machine can be appropriately changed according to the operation state of the vehicle that appears as the transmission gear ratio.

  Here, the speed change operation unit is configured to rotate integrally with the input side rotation member or the output side rotation member and to move in the rotation axis direction thereof, and the rotor of the rotating electrical machine is configured to change the speed change operation. It is preferable that the structure is arranged coaxially with the rotation shaft of the part and fixed to the speed change operation part.

  According to this configuration, the rotor of the rotating electrical machine can be moved in the axial direction in accordance with a change in the gear ratio between the input side rotating member and the output side rotating member together with the speed change operation unit, and via the speed change operation unit. Thus, it is possible to transmit the driving force from the rotating electrical machine to the input side rotating member or the output side rotating member and to transmit the driving force from the input side rotating member or the output side rotating member to the rotating electrical machine. Therefore, the rotor of the rotating electrical machine is axially arranged in accordance with the change in the transmission gear ratio by simply arranging the rotor of the rotating electrical machine coaxially with the rotation shaft of the speed changing operation unit and fixing the rotor to the speed changing operation unit. It is possible to simultaneously realize both the configuration in which the driving force is moved and the configuration in which the driving force can be transmitted between the rotating electrical machine and the input-side rotating member or the output-side rotating member.

  Further, it is preferable that the axial deviation between the rotor and the stator of the rotating electrical machine increases as the speed ratio decreases.

  Here, the “transmission ratio” is a ratio at which the rotation transmitted from the input-side rotating member to the output-side rotating member is decelerated, and the rotation of the input-side rotating member increases as the speed ratio value increases. It is greatly decelerated and transmitted to the output side rotating member.

  According to this configuration, when the gear ratio of the transmission is large, the axial displacement between the rotor and the stator of the rotating electrical machine becomes small, and the rotating electrical machine can output a large driving force. Conversely, when the gear ratio of the transmission is small, the axial deviation between the rotor and the stator of the rotating electrical machine increases and the counter electromotive force generated in the stator coil due to the rotation of the rotor is reduced, so that the rotor can be rotated at high speed. In addition, the efficiency of the rotating electrical machine at the time of high-speed rotation is increased. Here, in general, in a vehicle equipped with a transmission, when the transmission gear ratio is large, the vehicle speed is relatively low and a large driving force is required. When the transmission gear ratio is small, the vehicle speed is relatively low. In many cases, a high driving force is not required. Therefore, according to the present configuration, in a situation where a large driving force is required, a state in which a large driving force can be output from the rotating electrical machine can be obtained in accordance with the operation state of the vehicle that is expressed as the gear ratio of such a transmission. In a situation where a large driving force is not required and the rotating electrical machine rotates at a relatively high speed, the rotor can be rotated at a high speed and the efficiency of the rotating electrical machine during high-speed rotation can be increased. Accordingly, it is possible to realize a hybrid drive device that can output a necessary driving force from the rotating electrical machine in response to a request from the vehicle side and that has high efficiency during high-speed rotation of the rotating electrical machine such as during high-speed traveling.

  Further, it is preferable that the axial positions of the rotor and the stator of the rotating electrical machine coincide with each other when the speed ratio is maximum.

  According to this configuration, the rotating electrical machine can output the maximum torque when the transmission gear ratio is maximum. Therefore, the maximum torque can be output from the rotating electrical machine at the maximum gear ratio at which the largest driving force is required, depending on the operation state of the vehicle that appears as the gear ratio of the transmission. It is possible to fully meet the requirements.

  The rotating electrical machine is preferably connected to the output member via the transmission so as to be able to transmit a driving force.

  According to this configuration, the rotation of the rotating electrical machine can be transmitted to the output member after being shifted by the transmission with a speed ratio selected according to the operation state of the vehicle, similarly to the rotation of the engine. Accordingly, since the rotation of the rotating electrical machine can be decelerated or increased according to the operation state of the vehicle and transmitted to the output member, the rotating electrical machine can be used more efficiently.

  The transmission includes a driving pulley as the input-side rotating member, a driven pulley as the output-side rotating member, a V-shaped groove that the driving pulley has, and a V-shaped groove that the driven pulley has. A belt type continuously variable transmission including a wound transmission belt, wherein the speed change operation unit is a movable sheave for changing a groove width of the V-shaped groove in the drive pulley or the driven pulley. It is preferable.

  According to this configuration, when a belt-type continuously variable transmission widely used as a transmission is provided, integrally with a drive pulley as an input side rotation member or a driven pulley as an output side rotation member in the transmission. The movable sheave that rotates and moves in the direction of the rotation axis is used as the speed change operation unit. Accordingly, the rotor and the stator of the rotating electrical machine are appropriately provided according to the change of the transmission gear ratio without including a dedicated drive mechanism and a dedicated control device for moving the rotor or stator of the rotating electrical machine in the axial direction. The relative position in the axial direction can be changed. Further, if the rotor of the rotating electrical machine is disposed coaxially with the rotating shaft of the movable sheave and is fixed to the movable sheave, the rotor of the rotating electrical machine is moved in the axial direction in accordance with a change in the transmission gear ratio, and Both the configuration in which the driving force can be transmitted from the rotating electrical machine to the output member can be realized at the same time. Furthermore, if the rotor of the rotating electrical machine is connected to the movable sheave of the drive pulley, the rotation of the rotating electrical machine can be shifted by the transmission and transmitted to the output member, so that the rotating electrical machine can be used more efficiently. It becomes possible.

1. First Embodiment First, a first embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a skeleton diagram showing an overall schematic configuration of a hybrid drive apparatus H according to the present embodiment. FIG. 1 also shows a schematic configuration of the control system of the hybrid drive device H, where solid arrows indicate transmission paths for various information, and broken arrows indicate hydraulic pressure supply paths. 2 and 3 are explanatory diagrams for explaining the operating states of the transmission device TM and the rotating electrical machine MG of the hybrid drive device H according to the present embodiment, and FIG. 2 shows a large transmission ratio of the transmission device TM. FIG. 3 shows a state where the gear ratio of the transmission TM is small.

  As shown in these drawings, the hybrid drive device H includes an input shaft I connected to an engine E as a driving force source, and also includes one rotating electrical machine MG as a driving force source. Both the engine E and the rotating electrical machine MG are connected to the output shaft O so as to be able to transmit a driving force. That is, the hybrid drive device H is configured as a drive device for a so-called parallel hybrid vehicle. The hybrid drive device H includes a belt-type continuously variable transmission as the transmission TM. In the transmission TM, the transmission input shaft 13 is connected to the input shaft I via the forward / reverse switching device 50 and the torque converter 40. Further, the transmission output shaft 23 is connected to the output shaft O via the counter reduction mechanism 60 and the output differential gear device 70. The output shaft O is connected to a wheel (not shown). Although not shown in detail, each component of the hybrid drive device H is accommodated in the case Cs. In this embodiment, the input shaft I corresponds to the input member in the present invention, and the output shaft O corresponds to the output member in the present invention.

  In the present embodiment, the drive-side movable sheave 11 that constitutes the drive pulley 10 of the transmission apparatus TM is the transmission operation unit M, and the rotor Ro of the rotating electrical machine MG is disposed coaxially with the drive-side movable sheave 11. At the same time, the drive side movable sheave 11 is fixed. Therefore, the rotor Ro of the rotating electrical machine MG moves in the axial direction in conjunction with the movement in the rotational axis direction of the drive-side movable sheave 11 corresponding to the gear ratio of the transmission device TM. Further, since the rotor Ro of the rotating electrical machine MG rotates integrally with the drive side movable sheave 11, the driving force is transmitted from the rotating electrical machine MG to the driving pulley 10 and from the driving pulley 10 to the rotating electrical machine MG via the drive side movable sheave 11. The driving force can be transmitted. Thus, by connecting the rotor Ro of the rotating electrical machine MG to the drive pulley 10 of the transmission TM, the rotating electrical machine MG is connected to the output shaft O through the transmission TM so as to be able to transmit a driving force. Yes. Hereinafter, the configuration of each part of the hybrid drive device H will be described in detail.

1-1. Configuration of Overall Drive Transmission System of Hybrid Drive Device As shown in FIG. 1, the input shaft I is connected to an engine E. More specifically, the input shaft I is connected so that one end thereof rotates integrally with an output rotation shaft such as a crankshaft of the engine E. Here, the engine E is an internal combustion engine driven by combustion of fuel, and for example, various known engines such as a gasoline engine and a diesel engine can be used. The other end of the input shaft I is connected to the torque converter 40.

  The torque converter 40 is disposed between the input shaft I and the transmission device TM, and in this embodiment, between the forward / reverse switching device 50 disposed on the input shaft I side of the transmission device TM, and the input shaft I is connected to the transmission shaft TM. This is a fluid coupling that transmits the rotation and driving force of the engine E transmitted to the transmission device TM side. The torque converter 40 is provided to assist smooth running of the vehicle by transmitting rotation and driving force via a fluid when the vehicle starts or accelerates. Here, the torque converter 40 is provided between a pump impeller 41 connected so as to rotate integrally with the input shaft I, a turbine runner 42 connected so as to rotate integrally with the intermediate shaft 46, and one-way. And a stator 43 supported by the case Cs via a clutch. The torque converter 40 transmits the driving force between the driving-side pump impeller 41 and the driven-side turbine runner 42 via hydraulic oil filled therein. The driving force of the engine E (input shaft I) transmitted from the pump impeller 41 to the turbine runner 42 is transmitted to the forward / reverse switching device 50 via the intermediate shaft 46.

  The torque converter 40 includes a lockup clutch 44 that selectively connects the pump impeller 41 and the turbine runner 42. The hydraulic pressure for operating the lockup clutch 44 is supplied from the oil pump OP via the hydraulic control device 82, although the supply path is not shown in FIG. Further, the torque converter 40 includes a damper 45 for suppressing the vibration in the rotational direction of the input shaft I from the engine E from being transmitted to the intermediate shaft 46 when the lockup clutch 44 is in the engaged state. Yes. Similar to the lock-up clutch 44, the damper 45 is provided on a connection member that connects the pump impeller 41 and the turbine runner 42. Further, the hybrid drive device H includes an oil pump OP for supplying hydraulic pressure to each part of the hybrid drive device H including the transmission TM. Here, the oil pump OP is connected so that the rotor integrally rotates with the pump impeller 41 and is configured to rotate integrally with the input shaft I.

  The forward / reverse switching device 50 includes a direct coupling clutch 51, a reverse brake 52, and a planetary gear mechanism 53. The planetary gear mechanism 53 is a double pinion type planetary gear mechanism disposed coaxially with the intermediate shaft 46. In other words, the planetary gear mechanism 53 includes a carrier ca that supports a plurality of pairs of pinion gears, and a sun gear s and a ring gear r that mesh with the pinion gears, respectively, as rotating elements. The sun gear s is connected to rotate integrally with the intermediate shaft 46. The ring gear r is selectively fixed to the case Cs via a reverse brake 52 described later. The carrier ca is connected to rotate integrally with the transmission input shaft 13 of the transmission TM. If the three rotating elements of the planetary gear mechanism 53 are a first rotating element, a second rotating element, and a third rotating element in the order of rotational speed, the sun gear s is the first rotating element, the ring gear r is the second rotating element, and the carrier. ca becomes the third rotation element. The “order of rotational speed” is either the order from the high speed side to the low speed side, or the order from the low speed side to the high speed side, and can be any depending on the rotation state of the planetary gear mechanism 53. Even in this case, the order of the rotating elements does not change.

  The direct coupling clutch 51 is a clutch that is selectively connected so that two of the three rotating elements of the planetary gear mechanism 53 rotate together. By bringing the direct coupling clutch 51 into an engaged state, the planetary gear mechanism The whole 53 is in a directly connected state that rotates integrally. In the present embodiment, the direct coupling clutch 51 is a clutch that selectively connects the sun gear s of the planetary gear mechanism 53 and the carrier ca. The reverse brake 52 is a brake for selectively fixing, to the case Cs, the second rotation element that is intermediate in the order of the rotation speed among the three rotation elements of the planetary gear mechanism 53. In the present embodiment, the reverse brake 52 is a brake that selectively fixes the ring gear r, which is the second rotating element, to the case Cs. In a state where the ring gear r is fixed to the case Cs by the reverse brake 52, the rotation of the sun gear s that is the first rotation element is reversed and transmitted to the carrier ca that is the third rotation element. In the present embodiment, the direct coupling clutch 51 and the reverse brake 52 are both friction engagement elements that are brought into contact with each other and are engaged with each other by a frictional force. A multi-plate clutch or a multi-plate brake that operates by hydraulic pressure is used. Can be used. The hydraulic pressure for operating these is supplied from the oil pump OP via the hydraulic control device 82, although the supply path is not shown in FIG.

  Accordingly, when the direct coupling clutch 51 is engaged and the reverse brake 52 is released (disengaged), the planetary gear mechanism 53 as a whole is directly coupled to rotate integrally, and the engine E (input) transmitted to the intermediate shaft 46 is input. The rotation of the shaft I) is transmitted to the transmission input shaft 13 as it is. Therefore, in this state, the forward / reverse switching device 50 is in the forward state in which the rotation of the engine E is transmitted as it is to the transmission device TM. When the direct clutch 51 is disengaged (disengaged) and the reverse brake 52 is engaged, the rotation of the engine E (input shaft I) transmitted to the intermediate shaft 46 is reversed by the planetary gear mechanism 53. It is transmitted to the transmission input shaft 13. Therefore, in this state, the forward / reverse switching device 50 is in the reverse state in which the rotation of the engine E is reversed and transmitted to the transmission device TM. Further, when both the direct coupling clutch 51 and the reverse brake 52 are in the released (disengaged) state, the sun gear s and the carrier ca can freely rotate with each other, and the intermediate shaft 46 and the transmission input shaft 13 are interposed. In this state, rotation is not transmitted. Therefore, in this state, the forward / reverse switching device 50 is in a separated state in which the rotation is not transmitted between the engine E (input shaft I) and the transmission TM. In other words, the forward / reverse switching device 50 switches the engagement state of the direct clutch 51 and the reverse brake 52 to transmit the rotation of the input shaft I (engine E) as it is, and the rotation direction reversed. It is configured to be able to switch between a reverse state and a separated state that is not transmitted.

  The transmission TM shifts the rotation of the transmission input shaft 13 and the driving pulley 10 that rotates together with the transmission input shaft 13 and transmits the rotation to the driven pulley 20 and the transmission output shaft 23 that rotates integrally therewith. The transmission input shaft 13 extends from the drive pulley 10 to the input shaft I side (the right side in FIG. 1), and is connected to rotate integrally with the carrier ca of the planetary gear mechanism 53 constituting the forward / reverse switching device 50. Yes. The transmission output shaft 23 extends from the driven pulley 20 to the input shaft I side (the right side in FIG. 1), and the transmission output gear 24 is fixed to the extending portion. In the present embodiment, the rotary electric machine MG is arranged coaxially with the drive-side movable sheave 11 of the drive pulley 10, and the rotation and driving force of the rotary electric machine MG are transmitted to the drive pulley 10. The detailed configuration of the transmission apparatus TM will be described later. The rotation of the transmission output shaft 23 is transmitted to the output shaft O via the counter reduction mechanism 60 and the output differential gear device 70. The counter reduction mechanism 60 includes a first counter gear 61, a second counter gear 62, and a counter shaft 63 that connects the first counter gear 61 and the second counter gear 62 so as to rotate together. The first counter gear 61 meshes with the transmission output gear 24 that is fixed to the transmission output shaft 23 so as to rotate integrally therewith. The first counter gear 61 has a larger diameter than the transmission output gear 24. Accordingly, the rotation of the transmission output gear 24 is decelerated and transmitted to the first counter gear 61. On the other hand, the second counter gear 62 meshes with the differential input ring gear 71 of the output differential gear device 70. The second counter gear 62 has a smaller diameter than the first counter gear 61. Accordingly, the rotation transmitted to the first counter gear 61 is decelerated on the number of teeth and transmitted to the second counter gear 62. The output differential gear device 70 distributes the rotation and driving force of the differential input ring gear 71 to the output shafts O on the left and right sides. Wheels (not shown) are connected to the left and right output shafts O, respectively.

  In the present embodiment, the hybrid drive device H includes a torque converter 40, a forward / reverse switching device 50, a transmission input shaft 13 and a drive pulley 10 of the transmission TM, and a rotating electrical machine MG that are coaxial with the input shaft I. It is arranged on one axis. The transmission output shaft 23, the driven pulley 20, and the transmission output gear 24 of the transmission TM are disposed on a second axis parallel to the first axis. Further, the counter reduction mechanism 60 is disposed on a third axis parallel to the first axis, and the output differential gear device 70 and the output shaft O are disposed on a fourth axis parallel to the first axis. Therefore, the hybrid drive device H according to the present embodiment has a four-axis configuration in which each part is arranged on four parallel axes.

1-2. Configuration of Transmission The transmission TM includes an input-side rotating member (driving pulley 10 in the present embodiment) connected to the input shaft I and an output-side rotating member (driven pulley 20 in the present embodiment) connected to the output shaft O. Is a device that includes a mechanism for changing the transmission gear ratio between the input shaft I and the output shaft O and changes the rotation of the input shaft I at an appropriate transmission gear ratio. The rotation of the input shaft I is transmitted to the transmission input shaft 13 of the transmission TM through the torque converter 40 and the forward / reverse switching device 50 as described above. Further, the transmission apparatus TM includes a transmission operation unit M that moves in a predetermined direction in accordance with a change in the transmission ratio. In the present embodiment, the transmission TM is a drive pulley 10 as an input side rotation member, a driven pulley 20 as an output side rotation member, a V-shaped groove that the drive pulley 10 has, and a V shape that the driven pulley 20 has. The belt-type continuously variable transmission includes a transmission belt 30 wound around a groove. And this transmission apparatus TM is effective in which the transmission belt 30 of each pulley 10 and 20 is wound by changing groove width W1, W2 of the V-shaped groove | channel which each of the drive pulley 10 and the driven pulley 20 has. The gear ratio can be changed steplessly by changing the diameter. Further, in this example, by using such a structure of the transmission device TM, the drive-side movable sheave 11 for changing the groove width of the V-shaped groove in the drive pulley 10 is moved according to the gear ratio. Part M.

  The drive pulley 10 includes a drive-side movable sheave 11 and a drive-side fixed sheave 12 that rotate integrally with the transmission input shaft 13. Although not shown, the transmission input shaft 13 is rotatably supported by the case Cs via a bearing. The driving-side movable sheave 11 and the driving-side fixed sheave 12 are arranged on the transmission input shaft 13 so as to face each other, and conical surfaces that are inclined so that the facing interval widens radially outward on the respective facing surfaces. The conical plate-like member is formed. In the present embodiment, the drive side movable sheave 11 is disposed on the opposite side to the input shaft I (left side in FIG. 1) with respect to the drive side fixed sheave 12. A V-shaped groove of the driving pulley 10 is formed between the conical surfaces facing each other between the driving side movable sheave 11 and the driving side fixed sheave 12. Here, the drive side fixed sheave 12 is integrally fixed to the transmission input shaft 13. On the other hand, the drive-side movable sheave 11 is configured to be movable in the axial direction of the transmission input shaft 13 that is a rotating shaft thereof. The drive pulley 10 includes a hydraulic chamber 83 to which hydraulic pressure is supplied on the back surface of the drive side movable sheave 11 as a drive mechanism for moving the drive side movable sheave 11 in the axial direction. And the drive pulley width W1, which is the groove width of the V-shaped groove, is changed by moving the drive side movable sheave 11 in the axial direction by hydraulic pressure. The hydraulic pressure for operating the drive side movable sheave 11 is supplied from the oil pump OP via the hydraulic pressure control device 82.

  The driven pulley 20 includes a driven-side movable sheave 21 and a driven-side fixed sheave 22 that rotate integrally with the transmission output shaft 23. Although illustration is omitted, the transmission output shaft 23 is rotatably supported by the case Cs via a bearing. The driven-side movable sheave 21 and the driven-side fixed sheave 22 are disposed on the transmission output shaft 23 so as to face each other, and conical surfaces that are inclined so that the facing interval is widened outward in the radial direction. The conical plate-like member is formed. In the present embodiment, the driven-side movable sheave 21 is disposed on the input shaft I side (right side in FIG. 1) with respect to the driven-side fixed sheave 22. A V-shaped groove of the driven pulley 20 is formed between the opposing conical surfaces between the driven-side movable sheave 21 and the driven-side fixed sheave 22. Here, the driven side fixed sheave 22 is integrally fixed to the transmission output shaft 23. On the other hand, the driven-side movable sheave 21 is configured to be movable in the axial direction of the transmission output shaft 23 that is the rotation shaft thereof. The driven pulley 20 includes a hydraulic chamber 84 to which hydraulic pressure is supplied on the back surface of the driven movable sheave 21 as a drive mechanism for moving the driven movable sheave 21 in the axial direction. Then, the driven pulley width W2, which is the groove width of the V-shaped groove, is changed by moving the driven-side movable sheave 21 in the axial direction by hydraulic pressure. The hydraulic pressure for operating the driven movable sheave 21 is supplied from the oil pump OP via the hydraulic control device 82.

  The transmission TM moves the drive-side movable sheave 11 of the drive pulley 10 in the axial direction to change the drive pulley width W1, and moves the driven-side movable sheave 21 of the driven pulley 20 in the axial direction to move the driven pulley width W2. Is changed to change the gear ratio. Here, for each of the driving pulley 10 and the driven pulley 20, if the movable sheaves 11, 21 are moved away from the fixed sheaves 12, 22, the pulley widths W 1, W 2 are widened, and the pulley widths W 1, W 2 are wide. If it becomes, the effective diameter by which the transmission belt 30 is wound will become small. Conversely, if the movable sheaves 11 and 21 are moved closer to the fixed sheaves 12 and 22, the pulley widths W1 and W2 become narrower, and if the pulley widths W1 and W2 become narrower, the effective diameter becomes larger. In addition, the effective diameter of each pulley 10 and 20 is a diameter of the position where the transmission belt 30 contacts the V-shaped groove of each pulley 10 and 20. If the effective diameter of the drive pulley 10 is reduced and the effective diameter of the driven pulley 20 is increased, the transmission ratio (reduction ratio) increases, and the rate at which the rotation transmitted from the drive pulley 10 to the driven pulley 20 is reduced. Increases (the rate of speed increase decreases). Conversely, if the effective diameter of the driving pulley 10 is increased and the effective diameter of the driven pulley 20 is decreased, the transmission ratio (reduction ratio) is decreased, and the rotation transmitted from the driving pulley 10 to the driven pulley 20 is decelerated. The ratio becomes smaller (the rate of acceleration increases).

  FIG. 2 shows an example of a state in which the driving pulley width W1 of the driving pulley 10 is set to the maximum width W1 (max) and the driven pulley width W2 of the driven pulley 20 is set to the minimum width W2 (min). In this state, the speed ratio of the transmission TM is maximized, and the rotation transmitted from the drive pulley 10 to the driven pulley 20 is greatly reduced. FIG. 3 shows an example of a state in which the drive pulley width W1 of the drive pulley 10 is set to the minimum width W1 (min) and the driven pulley width W2 of the driven pulley 20 is set to the maximum width W2 (max). In this state, the speed ratio of the transmission TM is minimized, and the rotation transmitted from the drive pulley 10 to the driven pulley 20 is greatly increased.

  The gear ratio of the transmission TM is determined according to the vehicle speed and the accelerator opening. Here, the vehicle speed is detected by the vehicle speed sensor 85. As shown in FIG. 1, in this example, the vehicle speed sensor 85 is a rotational speed sensor that detects the rotational speed of the transmission output shaft 23. The detection position of the rotational speed by the vehicle speed sensor 85 may be any position from the transmission output shaft 23 to the output shaft O, and the speed ratio (reduction ratio) from the detection position to the wheel is determined based on the detected rotational speed. ) To obtain the vehicle speed. Further, the accelerator opening is detected by an accelerator operation detection sensor (not shown). This accelerator operation detection sensor is a sensor for detecting the amount of operation of the accelerator pedal by the driver of the vehicle. In the present embodiment, the control unit 81 of the hybrid drive device H refers to a predetermined shift control map and outputs the output shaft O at a necessary rotational speed and driving force according to the vehicle speed and accelerator opening detected by each sensor. A speed ratio capable of rotationally driving is determined. Further, the control unit 81 outputs a command signal corresponding to the determined gear ratio to the hydraulic control device 82. Thereby, the hydraulic control device 82 controls the hydraulic pressures of the hydraulic chamber 83 of the drive pulley 10 and the hydraulic chamber 84 of the driven pulley 20 to control the drive pulley width W1 and the driven pulley width W2. Thereby, the transmission apparatus TM obtains the transmission ratio determined by the control unit 81.

  FIG. 4 is a diagram illustrating an example of a shift control map referred to by the control unit 81. The polygonal line shown in this figure is a constant gear ratio line representing the relationship between the vehicle speed and the accelerator opening that are set to the same gear ratio. In the present embodiment, since the transmission TM is a continuously variable transmission, a very large number of constant transmission ratio lines are set in the actual transmission control map. It is shown. As shown in this figure, the control unit 81 selects a larger gear ratio as the vehicle speed decreases, and selects a smaller gear ratio as the vehicle speed increases. In addition, the control unit 81 selects a larger gear ratio as the accelerator opening increases, and decreases as the accelerator opening decreases, except for some areas close to the minimum accelerator opening and areas close to the maximum accelerator opening. Select the gear ratio.

  Therefore, the control unit 81 increases the gear ratio in a situation where the accelerator opening is large and a large driving force is required to be transmitted to the output shaft O, and the accelerator opening is small and a large driving force is applied to the output shaft O. Reduce the gear ratio in situations where transmission is not required. Thereby, the transmission apparatus TM amplifies or attenuates the driving force transmitted from the engine E as necessary, and transmits it to the output shaft O. Further, the control unit 81 reduces the gear ratio and keeps the rotational speed of the engine E (input shaft I) relatively low in a situation where the vehicle speed is high and the rotational speed of the output shaft O is high. In a situation where the rotational speed is low, the gear ratio is increased to relatively increase the rotational speed of the engine E (input shaft I). Thereby, the transmission apparatus TM makes the output shaft O relatively small in the change in the rotation speed of the engine E with respect to the change in the rotation speed, and operates the engine E efficiently.

1-3. Configuration of Rotating Electric Machine The rotating electric machine MG includes a stator St fixed to the case Cs, and a rotor Ro that is rotatably supported together with the drive pulley 10 on the radially inner side of the stator St. The rotating electrical machine MG is used as a driving force source of the vehicle, and is connected to the output shaft O so that the driving force can be transmitted. Here, the rotating electrical machine MG is an AC motor, and although not shown, is electrically connected to a power storage device such as a battery or a capacitor via an inverter. The rotating electrical machine MG can perform both a function as a motor (electric motor) that generates power upon receiving power supply and a function as a generator (generator) that generates power upon receiving power supply. It is possible.

  When rotating electric machine MG functions as a motor, it receives power supplied from the power storage device and performs powering to assist the driving force of engine E. Specifically, the rotating electrical machine MG functions as an assist motor that assists the driving force of the engine E by powering when the vehicle is accelerated and transmitting a driving force (torque) in the positive direction to the output shaft O. On the other hand, when rotating electrical machine MG functions as a generator, it supplies the generated power to each part such as an auxiliary machine of the vehicle, or supplies the generated power to the power storage device for charging. Specifically, the rotating electrical machine MG regenerates when the vehicle decelerates and transmits a negative driving force (torque) to the output shaft O to generate a braking force of the vehicle and to generate the generated electric power. To charge. In addition, when the vehicle is cruising at a substantially constant vehicle speed, the rotating electrical machine MG generates power with a small load to supply power to each part such as an auxiliary machine, and when the charge amount of the power storage device is small. The power storage device is also charged. Such an operation of the rotating electrical machine MG is performed via an inverter in accordance with a control command from the control unit 81.

  As described above, in the present embodiment, the drive-side movable sheave 11 that constitutes the drive pulley 10 of the transmission TM is the transmission operation unit M, and the rotor Ro of the rotating electrical machine MG is interlocked with the movement of the drive-side movable sheave 11. The rotor Ro is connected to the drive-side movable sheave 11 so as to move in the axial direction. Specifically, the rotor Ro of the rotating electrical machine MG is disposed coaxially with the drive side movable sheave 11 and is fixed to the drive side movable sheave 11. By the way, the drive side movable sheave 11 rotates integrally with the drive side fixed sheave 12 constituting the transmission input shaft 13 and the drive pulley 10. Therefore, the rotor Ro of the rotating electrical machine MG is rotatably supported by the case Cs with the transmission input shaft 13 as a rotation axis together with the drive pulley 10 and is connected to rotate integrally with the drive pulley 10. Thus, the rotating electrical machine MG is connected to the output shaft O through the transmission device TM and the counter reduction mechanism 60 and the output differential gear device 70 so as to be able to transmit the driving force. The drive-side movable sheave 11 is configured to be movable in the axial direction of the transmission input shaft 13. Therefore, the rotating electrical machine MG is configured such that the rotor Ro moves in the axial direction in conjunction with the axial movement of the drive side movable sheave 11. On the other hand, since the stator St of the rotating electrical machine MG is fixed to the case Cs, it does not move in any direction including the axial direction. Therefore, the relative position of the rotor Ro and the stator St in the axial direction changes due to the movement of the rotor Ro in the axial direction. In other words, the relative position in the axial direction of the rotor Ro and the stator St changes in conjunction with the axial movement of the drive-side movable sheave 11 as the speed change operation unit M.

  As described above, the rotor Ro of the rotating electrical machine MG is fixed to the drive-side movable sheave 11, so that the rotor Ro of the rotating electrical machine MG is axially moved together with the drive-side movable sheave 11 in accordance with the change in the gear ratio of the transmission apparatus TM. Move to. Therefore, in the present embodiment, the axial displacement between the rotor Ro and the stator St of the rotating electrical machine MG increases as the speed ratio decreases in relation to the speed ratio of the transmission apparatus TM. . Specifically, as shown in FIG. 2, in the state where the transmission gear ratio of the transmission TM is maximum, that is, in the state where the drive-side movable sheave 11 is in a position where the drive pulley width W1 of the drive pulley 10 is maximum, The rotor Ro is fixed to the drive-side movable sheave 11 so that the axial positions of the rotor Ro and the stator St of the rotating electrical machine MG coincide (no deviation). With this configuration, when the speed ratio of the transmission apparatus TM is the maximum, the axial deviation between the rotor Ro and the stator St is the smallest (no deviation), and as the speed ratio becomes smaller, as shown in FIG. In addition, the axial displacement between the rotor Ro and the stator St increases. In the present embodiment, the axial positions of the rotor Ro and the stator St are set to coincide with each other when the drive pulley width W1 is maximized. The drive pulley width W1 is reduced, and the rotor Ro is moved in the axial direction toward the input shaft I with respect to the stator St, so that the deviation is increased.

  By the way, the rotary electric machine MG can output the maximum torque in the original performance in a state where there is no axial displacement between the rotor Ro and the stator St. As the axial displacement between the rotor Ro and the stator St increases, the torque that can be output by the rotating electrical machine MG decreases. However, as the axial deviation between the rotor Ro and the stator St increases, the amount of the magnet of the rotor Ro that affects the coil of the stator St decreases. That is, by increasing the axial displacement between the rotor Ro and the stator St, the axial length of the rotor Ro and the stator St is reduced by an amount corresponding to the displacement. it can. As a result, when the gear ratio is small, it is possible to achieve a state similar to driving a small rotating electrical machine MG, so that the counter electromotive force generated in the coil of the stator St by rotating the rotor Ro is reduced. Can do. Therefore, the rotor can be rotated at a high speed, and the loss of power can be suppressed particularly during the high speed rotation, and the power required to perform the same work can be reduced. Therefore, the efficiency of the rotating electrical machine MG can be increased when driving in a situation where the required torque is relatively small.

  5 and 6 are correlation diagrams showing the relationship between the torque that can be output by the rotating electrical machine MG and the rotational speed, and FIG. 5 shows that the positions of the rotor Ro and the stator St of the rotating electrical machine MG coincide with each other in the axial direction. FIG. 6 is a correlation diagram in a state in which the axial displacement between the rotor Ro and the stator St of the rotating electrical machine MG is enlarged. The curves shown as 95 to 97% in these drawings are isoefficiency lines representing regions where the efficiency of the rotating electrical machine MG is equal. Here, the efficiency of the rotating electrical machine MG is expressed as a ratio of work output as the rotation of the rotor Ro with respect to the electric power supplied to the rotating electrical machine MG. Further, an area A1 in these drawings shows an outline of an operation area of the rotating electrical machine MG that is frequently used in a state in which the speed change ratio of the transmission apparatus TM is relatively large, and the speed change ratio of the transmission apparatus TM is relatively small. An outline of an operation region of the rotating electrical machine MG that is frequently used in a state is shown.

  Generally, in a vehicle equipped with the transmission TM, when the transmission TM has a large gear ratio, the vehicle speed is relatively low and a large driving force is often required. Therefore, as shown as region A1 in FIG. 5, the rotating electrical machine MG is also required to output a large driving force at a relatively low rotational speed. According to the configuration of the present embodiment, as described above, the axial shift between the rotor Ro and the stator St of the rotating electrical machine MG decreases as the transmission ratio of the transmission apparatus TM increases, and the transmission apparatus TM has the maximum transmission ratio. In this state, the rotor Ro is connected to the drive-side movable sheave 11 so that the axial positions of the rotor Ro and the stator St of the rotating electrical machine MG coincide with each other. As a result, the rotating electrical machine MG can output a large driving force as the transmission ratio of the transmission apparatus TM increases, and the rotating electrical machine can output the maximum driving force with the transmission apparatus TM having the maximum transmission ratio. It becomes a state. Therefore, a large driving force can be output from the rotating electrical machine MG in a situation where a large driving force is often required according to the operation state of the vehicle that appears as the gear ratio of the transmission device TM.

  On the other hand, in a vehicle equipped with the transmission TM, when the transmission ratio of the transmission TM is small, the vehicle speed is relatively high and a large driving force is often not required. Therefore, as indicated by the area A2 in FIGS. 5 and 6, the rotating electrical machine MG is also required to rotate at a relatively high rotational speed while outputting a relatively small driving force. According to the configuration of the present embodiment, as described above, the rotor Ro is movable on the drive side so that the axial displacement between the rotor Ro and the stator St of the rotating electrical machine MG increases as the gear ratio of the transmission TM decreases. It is connected to the sheave 11. As a result, the rotating electrical machine MG reduces the amount of the magnet of the rotor Ro that affects the coil of the stator St as the gear ratio of the transmission TM decreases, and the rotation of the rotor Ro causes the coil of the stator St to rotate. The generated back electromotive force can be reduced. Therefore, the efficiency of the rotating electrical machine MG at the time of high-speed rotation of the rotor Ro can be increased in accordance with the vehicle operating state that appears as the gear ratio of the transmission device TM, that is, the situation where high-speed rotation of the rotor Ro is often required. . A region A2 indicated by a broken line in FIG. 5 corresponds to a region A2 shown in FIG. As shown in FIGS. 5 and 6, the axial displacement between the rotor Ro and the stator St is increased in comparison with the state where the axial positions of the rotor Ro and the stator St remain matched. The efficiency when the rotary electric machine MG is used in a state where the output torque is relatively small is relatively high. As shown in FIG. 6, in the state in which the axial displacement between the rotor Ro and the stator St is increased, the rotating electrical machine MG cannot output a high torque. There is no problem because a large driving force is hardly required for the rotating electrical machine MG in a state where the ratio is small.

  As described above, in the hybrid drive device H according to the present embodiment, a large drive force can be output from the rotating electrical machine MG in a situation where a large drive force is required according to the operation state of the vehicle that appears as the gear ratio of the transmission device TM. In a situation where the rotary electric machine MG rotates at a relatively high speed without requiring a large driving force, the rotor Ro can be rotated at a high speed and the efficiency of the rotary electric machine MG at the time of high speed rotation can be increased. . Therefore, the efficiency at the time of high-speed rotation of the rotary electric machine MG such as during high-speed running can be increased while the required driving force can be output from the rotary electric machine MG in response to a request from the vehicle side.

  In the present embodiment, since the rotor Ro of the rotating electrical machine MG is connected to rotate integrally with the drive pulley 10, the rotating electrical machine MG drives the output shaft O via the transmission device TM. Can be transmitted. According to this configuration, the rotation of the rotating electrical machine MG is transmitted to the output shaft O after being shifted by the transmission apparatus TM at a speed ratio selected according to the operation state of the vehicle, similarly to the rotation of the engine E (input shaft I). can do. Therefore, since the rotation of the rotating electrical machine MG can be decelerated or increased according to the operation state of the vehicle and transmitted to the output shaft O, the rotation speed of the rotating electrical machine MG with respect to the change in the rotational speed of the output shaft O can be reduced. The change can be made relatively small, and the rotating electrical machine MG can be used more efficiently.

2. Second Embodiment Next, a second embodiment of the present invention will be described. FIG. 7 is a skeleton diagram showing an overall schematic configuration of the hybrid drive apparatus H according to the second embodiment. The method shown is the same as in FIG. 8 and 9 are explanatory diagrams for explaining the operation of the transmission TM and the rotary electric machine MG of the hybrid drive device H according to the present embodiment, and FIG. 8 is a state in which the gear ratio of the transmission TM is large. FIG. 9 shows a state where the gear ratio of the transmission apparatus TM is small. As shown in this figure, in the hybrid drive device H according to the present embodiment, the driven movable sheave 21 that constitutes the driven pulley 20 of the transmission TM is the transmission operation unit M, and the rotor Ro of the rotating electrical machine MG is the driven. It is different from the first embodiment in that it is arranged coaxially with the side movable sheave 21 and is fixed to the driven side movable sheave 21. Hereinafter, the hybrid drive device H according to the present embodiment will be described focusing on differences from the first embodiment. Note that points not particularly described are the same as those in the first embodiment.

  As described above, in the present embodiment, the driven-side movable sheave 21 for changing the groove width of the V-shaped groove in the driven pulley 20 using the structure of the belt-type continuously variable transmission is changed according to the gear ratio. The shifting operation unit M moves. The rotor Ro is connected to the driven movable sheave 21 so that the rotor Ro of the rotating electrical machine MG moves in the axial direction in conjunction with the movement of the driven movable sheave 21. Specifically, the rotor Ro of the rotating electrical machine MG is disposed coaxially with the driven-side movable sheave 21 and is fixed to the driven-side movable sheave 21. The driven movable sheave 21 rotates integrally with the transmission output shaft 23 and the driven fixed sheave 22 that constitutes the driven pulley 20. Accordingly, the rotor Ro of the rotating electrical machine MG is rotatably supported by the case Cs with the driven pulley 20 and the transmission output shaft 23 as a rotating shaft, and is connected to rotate integrally with the driven pulley 20. Thus, the rotating electrical machine MG is connected to the output shaft O through the counter speed reduction mechanism 60 and the output differential gear device 70 so as to be able to transmit the driving force without passing through the transmission device TM. The driven movable sheave 21 is configured to be movable in the axial direction of the transmission output shaft 23. Therefore, the rotating electrical machine MG is configured such that the rotor Ro moves in the axial direction in conjunction with the axial movement of the driven movable sheave 21. On the other hand, since the stator St of the rotating electrical machine MG is fixed to the case Cs, it does not move in any direction including the axial direction. Therefore, the relative position in the axial direction between the rotor Ro and the stator St changes in conjunction with the axial movement of the driven movable sheave 21 as the speed change operation unit M.

  As described above, the rotor Ro of the rotating electrical machine MG is fixed to the driven-side movable sheave 21 so that the rotor Ro of the rotating electrical machine MG is axially moved along with the driven-side movable sheave 21 in accordance with a change in the speed ratio of the transmission apparatus TM. Move to. Therefore, in the present embodiment, the axial displacement between the rotor Ro and the stator St of the rotating electrical machine MG increases as the speed ratio decreases in relation to the speed ratio of the transmission apparatus TM. . Specifically, as shown in FIG. 8, in the state where the transmission gear ratio of the transmission TM is maximum, that is, in the state where the driven-side movable sheave 21 is present at the position where the driven pulley width W2 of the driven pulley 20 is minimum. The rotor Ro is fixed to the driven-side movable sheave 21 so that the axial positions of the rotor Ro and the stator St of the rotating electrical machine MG coincide (no deviation). With this configuration, when the speed ratio of the transmission apparatus TM is the maximum, the axial deviation between the rotor Ro and the stator St is the smallest (no deviation), and as the speed ratio becomes smaller, as shown in FIG. In addition, the axial displacement between the rotor Ro and the stator St increases. In the present embodiment, the axial positions of the rotor Ro and the stator St are set to coincide with each other in the state where the driven pulley width W2 is minimized, so that the gear ratio of the transmission device TM becomes smaller. The driven pulley width W2 is increased, and the rotor Ro is moved in the axial direction to the side opposite to the input shaft I with respect to the stator St, so that the displacement is increased.

  Further, since the rotor Ro of the rotating electrical machine MG rotates integrally with the driven-side movable sheave 21, transmission of driving force from the rotating electrical machine MG to the driven pulley 20 and the driven pulley 20 to the rotating electrical machine MG via the driven-side movable sheave 21. The driving force can be transmitted. In this embodiment, by connecting the rotor Ro of the rotating electrical machine MG to the driven pulley 20 of the transmission apparatus TM in this way, the rotating electrical machine MG can transmit the driving force to the output shaft O without passing through the transmission apparatus TM. It is a connected configuration. According to this configuration, the transmission path of the driving force from the rotating electrical machine MG to the output shaft O can be shortened compared to the configuration in which the driving force is transmitted via the transmission device TM. Therefore, the loss in the transmission path of the driving force can be suppressed, and the power transmission efficiency can be increased accordingly.

3. Other Embodiments (1) In the above embodiment, the configuration in which the input shaft I is connected to the transmission TM via the torque converter 40 and the forward / reverse switching device 50 has been described as an example. However, when the vehicle can be started only by the driving force of the rotating electrical machine MG without using the driving force of the engine E, the torque converter 40 is unnecessary. Further, when the vehicle can be moved backward by separating the engine E and rotating the rotating electrical machine MG in reverse, the forward / reverse switching device 50 is not necessary. Therefore, it is also a preferred embodiment of the present invention that the hybrid drive device H does not include one or both of the torque converter 40 and the forward / reverse switching device 50.

  That is, for example, when the hybrid drive device H does not include both the torque converter 40 and the forward / reverse switching device 50, the input shaft I is connected to the transmission input shaft 13 of the transmission TM. At this time, one or both of a damper that attenuates vibration in the rotational direction and a clutch that selectively connects the input shaft I and the transmission input shaft 13 are provided between the input shaft I and the transmission input shaft 13. It is preferable. When the hybrid drive device H does not include the torque converter 40, the input shaft I is connected to the transmission input shaft 13 via the forward / reverse switching device 50. At this time, it is preferable to provide a damper that attenuates vibration in the rotational direction between the input shaft I and the forward / reverse switching device 50. When the hybrid drive device H does not include the forward / reverse switching device 50, the input shaft I is connected to the transmission input shaft 13 via the torque converter 40. At this time, it is preferable to provide a clutch that selectively connects between the torque converter 40 and the transmission input shaft 13.

(2) In the above embodiment, the configuration in which the transmission output shaft 23 is connected to the output shaft O via the counter deceleration mechanism 60 has been described as an example. However, the embodiment of the present invention is not limited to this, and a configuration without the counter deceleration mechanism 60 is one of the preferred embodiments of the present invention.

(3) In the above embodiment, the speed change operation unit M rotates integrally with the drive pulley 10 as the input side rotation member or the driven pulley 20 as the output side rotation member, and moves in the direction of the rotation axis. The drive-side movable sheave 11 or the driven-side movable sheave 21 that is configured, and the rotor Ro of the rotating electrical machine MG is arranged coaxially with the transmission operation unit M and fixed to the transmission operation unit M will be described as an example. did. However, the embodiment of the present invention is not limited to this, and the rotor Ro of the rotating electrical machine MG is connected to the speed change operation unit so as to move in the axial direction in conjunction with the movement of the speed change operation unit M in a predetermined direction. Any other configuration is possible as long as it is configured. Therefore, for example, the operation in a predetermined direction of the speed change operation unit M is transmitted to the rotor Ro of the rotating electrical machine MG via a transmission member such as a link mechanism, and thus the rotor Ro is connected so as to move in the axial direction. This is also a preferred embodiment of the present invention. In this case, it is not a requirement that the rotation of the rotor Ro of the rotating electrical machine MG be transmitted to the speed change operation unit M.

(4) In the above-described embodiment, the speed change operation unit is configured such that the rotor Ro of the rotating electrical machine MG moves in the axial direction in conjunction with the movement of the speed change operation unit M (the drive side movable sheave 11 or the driven side movable sheave 21). The configuration connected to M has been described as an example. However, the effects of the present invention as described above can be obtained by changing the relative position in the axial direction of the rotor Ro and the stator St of the rotating electrical machine MG in accordance with the gear ratio of the transmission. Therefore, the stator St of the rotating electrical machine MG may be configured to be connected to the transmission operation unit M so as to move in the axial direction in conjunction with the movement of the transmission operation unit M. One. Here, when the speed change operation unit M is a rotating member such as the drive side movable sheave 11 or the driven side movable sheave 21, the stator St is interlocked with the movement of the speed change operation unit M in the axial direction. However, it connects so that rotation of the said speed change operation | movement part M may not be transmitted. On the other hand, when the transmission operation unit M is a member that only moves in a predetermined direction according to a change in the transmission ratio and does not rotate, the stator St can be fixed to the transmission operation unit M. At this time, the rotor Ro of the rotating electrical machine MG is rotatably supported so as not to move in the axial direction, and is connected to the output member so as to be able to transmit a driving force.

(5) In the above-described embodiment, the axial position of the rotor Ro of the rotating electrical machine MG and the stator St coincide with each other when the speed ratio of the transmission TM is maximum, and the rotor of the rotating electrical machine MG decreases as the speed ratio decreases. The case where the axial displacement between Ro and the stator St is configured to increase has been described as an example. However, the embodiment of the present invention is not limited to this. Accordingly, depending on the characteristics of the hybrid vehicle and the control method, the axial displacement between the rotor Ro and the stator St of the rotating electrical machine MG may be increased as the transmission ratio of the transmission operation unit M increases. This is one of the preferred embodiments. In this case, it is also preferable that the axial positions of the rotor Ro and the stator St of the rotating electrical machine MG coincide with each other when the speed ratio of the transmission apparatus TM is at a minimum. Further, as the gear ratio of the transmission device TM becomes smaller, the deviation is once reduced from a large state, and then the deviation becomes larger again. Alternatively, after the gear device TM becomes smaller, the deviation is once enlarged. It is one of the preferred embodiments of the present invention that the shift is gradually reduced.

(6) In the above embodiment, the case where the transmission TM is a belt-type continuously variable transmission has been described as an example. However, the embodiment of the present invention is not limited to this. Therefore, other continuously variable transmissions such as a toroidal type can be used as the transmission TM, or various stepped automatic transmissions and manual transmissions can be used. In any case, the member that moves in a predetermined direction in accordance with the change in the gear ratio is the speed change operation unit M, and the rotor Ro or the stator St of the rotating electrical machine MG is connected in conjunction with the movement. For example, the present invention can be applied to a stepped automatic transmission or a manual transmission using a constantly meshing gear pair. Such a transmission generally includes a drive shaft connected to an engine and an input member, a driven shaft connected to an output member, a drive gear having the drive shaft as a rotation shaft, and the driven shaft as a rotation shaft. A plurality of gear pairs, one of which is a free-wheeling gear that is rotatable relative to the rotation shaft, and the rotation gear of each of the plurality of gear pairs is selected as the rotation shaft. And a driving member such as a shift fork that moves the meshing clutch in the direction of the rotation shaft. Therefore, the drive member is a speed change operation unit M, and the rotor Ro or the stator St of the rotating electrical machine MG is connected to the drive member so as to move in the axial direction in conjunction with the axial movement of the drive member. This is also one of the preferred embodiments of the present invention.

  The present invention is used in a hybrid vehicle having an engine and a rotating electrical machine as a driving force source, and can be suitably used for a hybrid driving device including a transmission.

FIG. 1 is a skeleton diagram showing the entire hybrid drive apparatus according to the first embodiment of the present invention; The figure which shows the state of a transmission and a rotary electric machine in the hybrid drive device which concerns on 1st embodiment of this invention when the gear ratio of a transmission is large. The figure which shows the state of a transmission and a rotary electric machine in the hybrid drive device which concerns on 1st embodiment of this invention when the gear ratio of a transmission is small. A figure showing an example of a shift control map Correlation diagram showing the relationship between torque and rotational speed that can be output by the rotating electrical machine when the axial positions of the rotor and stator are the same. Correlation diagram showing the relationship between the torque that can be output by the rotating electrical machine and the rotational speed in the state where the axial deviation between the rotor and the stator is enlarged Skeleton diagram showing entire hybrid drive apparatus according to second embodiment of the present invention The figure which shows the state of a transmission and a rotary electric machine when the gear ratio of a transmission is large in the hybrid drive device which concerns on 2nd embodiment of this invention. The figure which shows the state of a transmission and a rotary electric machine when the gear ratio of a transmission is small in the hybrid drive device which concerns on 2nd embodiment of this invention.

Explanation of symbols

H: Hybrid drive device E: Engine I: Input shaft (input member)
O: Output shaft (output member)
MG: Rotating electric machine Ro: Rotor St: Stator TM: Transmission M: Shifting operation unit 10: Drive pulley (input side rotating member)
11: Drive-side movable sheave 20: Driven pulley (output-side rotating member)
21: Driven movable sheave 30: Transmission belt

Claims (6)

An input member connected to the engine;
An output member connected to the wheel;
A rotating electrical machine having a rotor and a stator and connected to the output member so as to be able to transmit a driving force;
A transmission that includes an input-side rotating member connected to the input member and an output-side rotating member connected to the output member, and that changes a gear ratio between the input-side rotating member and the output-side rotating member; A hybrid drive device comprising:
The transmission includes a transmission operation unit that moves in a predetermined direction in accordance with a change in the transmission ratio.
The hybrid drive device connected to the speed change operation unit so that either one of the rotor and the stator of the rotating electrical machine moves in the axial direction in conjunction with the movement of the speed change operation unit. The speed change operation unit is configured to rotate integrally with the input side rotation member or the output side rotation member and to move in the rotation axis direction thereof,
2. The hybrid drive device according to claim 1, wherein a rotor of the rotating electrical machine is disposed coaxially with a rotation shaft of the speed change operation unit and is fixed to the speed change operation unit.   3. The hybrid drive device according to claim 1, wherein the shift in the axial direction between the rotor and the stator of the rotating electrical machine increases as the speed ratio decreases.   4. The hybrid drive device according to claim 1, wherein the axial positions of the rotor and the stator of the rotating electrical machine coincide with each other when the speed ratio is maximum. 5.   The hybrid drive device according to any one of claims 1 to 4, wherein the rotating electrical machine is connected to the output member via the transmission so as to be able to transmit a drive force. The transmission is wound around a driving pulley as the input side rotating member, a driven pulley as the output side rotating member, a V-shaped groove of the driving pulley, and a V-shaped groove of the driven pulley. A belt type continuously variable transmission equipped with a transmission belt,
The hybrid drive device according to any one of claims 1 to 5, wherein the speed change operation unit is a movable sheave for changing a groove width of the V-shaped groove in the drive pulley or the driven pulley.