JP2012211670A - Power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To shorten a period in which power transmitted to a drive shaft from an engine via a stepped transmission is blocked or reduced when a gear position of the stepped transmission is shifted to the next gear position from the present gear position.SOLUTION: When shifting the gear position of the stepped transmission 44 to the next gear position from the present gear position, by releasing an m-speed engagement member 64-m in an engagement state corresponding to the present gear position and an output-side engagement member 64-5 (or an input-side engagement member 64-7), and by making electromagnetic coupling torque Tcoup act on an output-side rotor 18 from an input-side rotor 28 by an alternate current of a rotor winding 30, rotation speeds Nmg of the output-side rotor 18 and an input shaft 61 are changed. By this arrangement, torque made to act on the input shaft 61 can be increased, and a time necessary for changing the rotation speed Nmg of the input shaft 61 to a target input-shaft rotation speed Nrefn corresponding to the next gear position can be shortened.

Description

  The present invention relates to a power transmission device, and more particularly to a power transmission device capable of transmitting power from an engine to a drive shaft using electromagnetic coupling between rotors.

  The related art of this type of power transmission device is disclosed in Patent Document 1 below. The power transmission device according to Patent Document 1 includes a first rotor in which windings are disposed and mechanically coupled to an engine, and a magnet that is electromagnetically coupled to the windings of the first rotor and is mechanically disposed on a drive shaft. A second rotor coupled to the stator, a stator provided with a winding electromagnetically coupled to the magnet of the second rotor, a slip ring electrically connected to the winding of the first rotor, and a slip ring; A brush that is in electrical contact, a first inverter that is controlled so as to be able to transfer power between the battery and the stator winding, and a power between the battery and the first rotor via the slip ring and the brush. And a second inverter that is controlled so as to be able to transmit and receive. In Patent Document 1, the power from the engine transmitted to the first rotor is transmitted to the second rotor by electromagnetic coupling between the windings of the first rotor and the magnets of the second rotor. The shaft can be driven. Furthermore, since power can be transferred between the battery and the winding of the first rotor via the second inverter, by controlling the power of the winding of the first rotor by the second inverter, The rotation speed can be controlled. In this case, when the rotation speed of the first rotor is higher than the rotation speed of the second rotor, the generated power of the winding of the first rotor is supplied to the battery side via the second inverter, and the rotation of the first rotor When the speed is lower than the rotational speed of the second rotor, the battery power is supplied to the windings of the first rotor via the second inverter. Further, the electromagnetic coupling between the stator winding and the magnet of the second rotor causes the second rotor to generate power using the electric power supplied from the battery side to the stator winding via the first inverter. Therefore, the torque transmitted to the drive shaft can be controlled by controlling the power supply to the stator winding by the first inverter.

JP-A-9-56010 Japanese Patent Laying-Open No. 2005-147312 JP 2009-73472 A JP 2009-274536 A

  In Patent Document 1, for example, a stepped transmission such as an automatic transmission (AT) or an automatic manual transmission (AMT) is provided between the second rotor and the drive shaft so that the drive shaft is driven by engine power. In this case, even if the rotational speed of the drive shaft increases, it is possible to suppress an increase in the rotational speed of the engine by changing the gear position of the stepped transmission to a direction in which the gear ratio decreases. When changing the speed of the stepped transmission from the current speed to the next speed, the rotational speed of the input shaft of the stepped transmission is changed from the speed corresponding to the current speed to the speed corresponding to the next speed. However, during this period, the power transmitted from the engine to the drive shaft via the stepped transmission is interrupted or reduced. In order to shorten the period during which the power transmitted from the engine to the drive shaft is interrupted or reduced, the rotational speed of the input shaft of the stepped transmission is changed from the rotational speed corresponding to the current gear to the speed corresponding to the next gear. In order to change the rotational speed of the input shaft of the stepped transmission quickly, a large torque is applied to the input shaft of the stepped transmission. Is required. In particular, since the rotational inertia is increased by mechanically connecting the input shaft of the stepped transmission to the second rotor, it is required to apply a large torque to the input shaft of the stepped transmission.

  The present invention shortens a period in which the interruption or reduction of the power transmitted from the engine to the drive shaft via the stepped transmission is changed when the stepped speed of the stepped transmission is changed from the current speed to the next speed. The purpose is to do.

  The power transmission device according to the present invention employs the following means in order to achieve the above-described object.

  The power transmission device according to the present invention includes a first rotor provided with a rotor conductor capable of generating a rotating magnetic field when power from an engine is transmitted and an alternating current flows, and rotates when an alternating current flows. A stator provided with a stator conductor capable of generating a magnetic field and a second rotor capable of rotating relative to the first rotor in response to the action of a rotating magnetic field generated by the rotor conductor Torque is applied between the first rotor and the second rotor in which torque is applied to the stator in response to the rotating magnetic field generated by the stator conductor, and input from the second rotor. A stepped transmission that shifts the power transmitted to the shaft at a gear ratio according to the shift speed and transmits it from the output shaft to the drive shaft, and releases the engaging member corresponding to the current shift speed to the next shift speed The gear position is changed from the current gear position to the next gear position by engaging the engagement member corresponding to A step-variable transmission, a first power conversion device that performs power conversion between the power storage device and the stator conductor, and power between one of the power storage device and the first power conversion device and the rotor conductor. A second power conversion device that performs the conversion, a power conversion in the first power conversion device, and a torque that is applied between the stator and the second rotor by an alternating current of the stator conductor; A control device that controls power conversion in the power conversion device and controls a torque that is applied between the first rotor and the second rotor by an alternating current of the rotor conductor. When changing the shift stage of the transmission from the current shift stage to the next shift stage, if the engagement member corresponding to the current shift stage is released, the rotational speed of the input shaft of the stepped transmission corresponds to the next shift stage. The first rotor is driven by the AC current of the rotor conductor so as to approach the input shaft rotation speed. By exerting a torque on the second rotor, and summarized in that changing the rotational speed of the input shaft of the second rotor and stepped transmission.

  In one aspect of the present invention, when changing the shift stage of the stepped transmission from the current shift stage to the next shift stage, the control device releases the engagement member corresponding to the current shift stage. Torque is applied from the first rotor to the second rotor by the alternating current of the rotor conductor so that the rotational speed of the input shaft approaches the target input shaft rotational speed corresponding to the next gear, and the alternating current of the stator conductor It is preferable to change the rotational speeds of the input shafts of the second rotor and the stepped transmission by applying a torque from the stator to the second rotor by an electric current.

  In one aspect of the present invention, when the shift gear of the stepped transmission is upshifted from the current gear to the next gear, the control device releases the engaging member corresponding to the current gear from the stator conductor. The power conversion in the first power conversion device is controlled so as to recover the power, the torque is applied from the stator to the second rotor by the alternating current of the stator conductor, and the second power is supplied to the rotor conductor. By controlling the power conversion in the power converter and applying torque from the first rotor to the second rotor by the alternating current of the rotor conductor, the rotational speed of the input shaft of the stepped transmission is changed to the next gear stage. It is preferred to reduce to the corresponding target input shaft rotational speed.

  In one aspect of the present invention, the control device corresponds to the rotation speed of the input shaft of the stepped transmission corresponding to the next shift step when the shift step of the stepped transmission is upshifted from the current shift step to the next shift step. When reducing to the target input shaft rotational speed, it is preferable to limit the torque applied from the first rotor to the second rotor by the alternating current of the rotor conductor to be equal to or less than the engine load loss torque.

  In one aspect of the present invention, the control device corresponds to the rotation speed of the input shaft of the stepped transmission corresponding to the next shift step when the shift step of the stepped transmission is upshifted from the current shift step to the next shift step. When decreasing to the target input shaft rotational speed, it is preferable to apply torque from the first rotor to the second rotor by the alternating current of the rotor conductor and to increase the load loss torque of the engine.

  In one aspect of the present invention, the control device corresponds to the rotation speed of the input shaft of the stepped transmission corresponding to the next shift step when the shift step of the stepped transmission is upshifted from the current shift step to the next shift step. When decreasing to the target input shaft rotation speed, it is preferable to control the torque applied from the first rotor to the second rotor by the alternating current of the rotor conductor based on the rotation speed of the engine.

  In one aspect of the present invention, when the shift gear of the stepped transmission is downshifted from the current shift speed to the next shift speed, the control device releases the engagement member corresponding to the current shift speed from the rotor conductor. The power conversion in the second power converter is controlled so as to recover the power, the torque is applied from the first rotor to the second rotor by the alternating current of the rotor conductor, and the power is supplied to the stator conductor. By controlling the power conversion in the first power converter and applying torque from the stator to the second rotor by the alternating current of the stator conductor, the rotational speed of the input shaft of the stepped transmission is changed to the next gear stage. It is preferred to increase to the corresponding target input shaft rotational speed.

  According to the present invention, when the gear stage of the stepped transmission is changed from the current gear stage to the next gear stage, if the engaging member corresponding to the current gear stage is released, the first rotation is performed by the alternating current of the rotor conductor. By applying torque from the child to the second rotor, the torque to be applied to the input shaft of the stepped transmission can be increased, and the rotational speed of the input shaft of the stepped transmission can be set to a target corresponding to the next gear stage. It is possible to shorten the time required for changing to the input shaft rotation speed. As a result, the period during which the power transmitted from the engine to the drive shaft via the stepped transmission is interrupted or reduced can be shortened.

It is a figure which shows schematic structure of a hybrid drive device provided with the power transmission device which concerns on embodiment of this invention. It is a figure which shows schematic structure of the power transmission device which concerns on embodiment of this invention. 2 is a diagram illustrating a configuration example of an input side rotor 28, an output side rotor 18, and a stator 16 of the rotating electrical machine 10. FIG. 2 is a diagram illustrating a configuration example of an input side rotor 28, an output side rotor 18, and a stator 16 of the rotating electrical machine 10. FIG. 3 is a diagram illustrating a configuration example of a transmission 44. FIG. FIG. 6 is a diagram illustrating a result of calculating a temporal change in the rotational speed of the output side rotor 18 when a torque in the deceleration direction is applied from the stator 16 to the output side rotor 18 in the upshift operation. FIG. 6 is a diagram for explaining torque to be applied to the output side rotor 18 in an upshift operation. It is a figure explaining the power flow in upshift operation. FIG. 6 is a diagram illustrating a result of calculating a temporal change in the rotational speed of the output side rotor 18 when a torque in the deceleration direction is applied from the input side rotor 28 and the stator 16 to the output side rotor 18 in the upshift operation. FIG. 5 is a diagram illustrating an example of a temporal change in torque applied from the input side rotor 28 to the output side rotor 18 and torque applied from the stator 16 to the output side rotor 18 in the upshift operation. FIG. 6 is a diagram illustrating an example of temporal changes in the rotational speed of the input-side rotor 28 and the rotational speed of the output-side rotor 18 in the upshift operation. It is a figure explaining the torque made to act on the output side rotor 18 in a downshift operation. It is a figure explaining the power flow in a downshift operation. It is a figure which shows the result of having calculated an example of the upshift operation | movement when the capacity | capacitance of inverters 40 and 41 is made larger than the capacity | capacitance of the electrical storage apparatus. It is a figure which shows the result of having calculated an example of the upshift operation | movement when the capacity | capacitance of inverters 40 and 41 is made equal to the capacity | capacitance of the electrical storage apparatus.

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments for carrying out the present invention (hereinafter referred to as embodiments) will be described with reference to the drawings.

  1 to 5 are diagrams showing an outline of a configuration of a hybrid drive device including a power transmission device according to an embodiment of the present invention, FIG. 1 shows an overview of the overall configuration, and FIGS. FIG. 5 shows an outline of the configuration of the transmission 44. The hybrid drive device according to the present embodiment is provided between an engine (internal combustion engine) 36 provided as a prime mover capable of generating power (mechanical power), and between the engine 36 and a drive shaft 37 (wheels 38). A transmission (mechanical transmission) 44 capable of changing the transmission ratio, and a rotating electrical machine 10 provided between the engine 36 and the transmission 44 and capable of generating power (mechanical power) and generating power. Prepare. In addition, about the hybrid drive device which concerns on this embodiment, it can be used as a power output device for driving a vehicle, for example.

  The rotating electrical machine 10 includes a stator 16 fixed to a stator case (not shown), a first rotor 28 that can rotate relative to the stator 16, a stator 16 and a first rotor 28 in a radial direction perpendicular to the rotor rotation axis, and a predetermined amount. The second rotor 18 is opposed to the stator 16 and the first rotor 28 with a gap. The stator 16 is disposed at a position radially outward from the first rotor 28 and spaced from the first rotor 28, and the second rotor 18 is positioned between the stator 16 and the first rotor 28 in the radial direction. Is arranged. That is, the first rotor 28 is disposed opposite to the second rotor 18 at a position radially inward of the second rotor 18, and the stator 16 is disposed opposite to the second rotor 18 at a position radially outward from the second rotor 18. Has been. Since the first rotor 28 is mechanically connected to the engine 36, the power from the engine 36 is transmitted to the first rotor 28. On the other hand, the second rotor 18 is mechanically coupled to the drive shaft 37 via the transmission 44, so that the power from the second rotor 18 is shifted by the transmission 44 to the drive shaft 37 (wheel 38). It is transmitted after. In the following description, the first rotor 28 is an input side rotor, and the second rotor 18 is an output side rotor.

  The input-side rotor 28 includes a rotor core (first rotor core) 52 and a plurality of (for example, three-phase) rotor windings 30 disposed on the rotor core 52 along the circumferential direction thereof. When a plurality of phases (for example, three phases) of alternating current flows through the plurality of rotor windings 30, the rotor windings 30 can generate a rotating magnetic field that rotates in the circumferential direction of the rotor.

  The stator 16 includes a stator core (stator core) 51 and a plurality of (for example, three-phase) stator windings 20 disposed on the stator core 51 along the circumferential direction thereof. When a plurality of phases (for example, three phases) of alternating current flows through the plurality of stator windings 20, the stator windings 20 can generate a rotating magnetic field that rotates in the stator circumferential direction.

  The output-side rotor 18 includes a rotor core (second rotor core) 53 and permanent magnets 32 and 33 that are disposed on the rotor core 53 along the circumferential direction thereof and generate a field magnetic flux. The permanent magnet 32 is disposed on the outer peripheral portion of the rotor core 53 so as to face the stator 16 (stator core 51), and the permanent magnet 33 is opposed to the input-side rotor 28 (rotor core 52) on the inner peripheral portion of the rotor core 53. Arranged. Here, the permanent magnets 32 and 33 can also be integrated.

  A more detailed configuration example of the input side rotor 28, the output side rotor 18, and the stator 16 is shown in FIG. In the example shown in FIG. 4, the input side rotor 28, the output side rotor 18, and the stator 16 are arranged concentrically. In the stator core 51 of the stator 16, a plurality of teeth 51 a protruding radially inward (toward the output-side rotor 18) are arranged at intervals along the circumferential direction of the stator. The magnetic pole is configured by being wound around the teeth 51a. A plurality of teeth 52a protruding radially outward (toward the output-side rotor 18) are arranged on the rotor core 52 of the input-side rotor 28 at intervals along the circumferential direction of the rotor. Is wound around these teeth 52a, thereby forming a magnetic pole. The teeth 51a of the stator 16 and the permanent magnets 32 of the output-side rotor 18 are opposed to each other in the radial direction perpendicular to the rotation center axis of the output-side rotor 18 (which coincides with the rotation center axis of the input-side rotor 28). The teeth 52a of the side rotor 28 and the permanent magnets 33 of the output side rotor 18 are arranged to face each other in the radial direction. The winding axis of the stator winding 20 and the winding axis of the rotor winding 30 coincide with this radial direction (the direction in which the input side rotor 28 and the output side rotor 18 face each other). The permanent magnets 32 and 33 are arranged at intervals in the circumferential direction of the rotor, and the permanent magnet 32 is embedded in the rotor core 53 in a V shape. However, the permanent magnets 32 and 33 may be exposed on the surface (outer peripheral surface or inner peripheral surface) of the output-side rotor 18 or may be embedded in the output-side rotor 18 (in the rotor core 53). .

  The clutch 48 is provided in parallel with the rotating electrical machine 10 (the input-side rotor 28 and the output-side rotor 18) between the engine 36 and the transmission 44. By engaging / disengaging the clutch 48, mechanical engagement / disengagement between the input-side rotor 28 and the output-side rotor 18 can be selectively performed. By engaging the clutch 48 and mechanically engaging the input-side rotor 28 and the output-side rotor 18, the input-side rotor 28 and the output-side rotor 18 are integrally rotated at the same rotational speed. On the other hand, by releasing the clutch 48 and releasing the mechanical engagement between the input-side rotor 28 and the output-side rotor 18, a difference in rotational speed between the input-side rotor 28 and the output-side rotor 18 is allowed. The clutch 48 here can be switched between engagement and disengagement using, for example, hydraulic pressure or electromagnetic force, and further adjusts the fastening force by adjusting the hydraulic pressure or electromagnetic force supplied to the clutch 48. You can also

  About the structure of the transmission 44, the structure similar to a well-known constant meshing type manual transmission is applicable. That is, as shown in FIG. 5, the transmission 44 is mechanically connected to the output-side rotor 18, so that power from the output-side rotor 18 is transmitted, and the drive shaft 37 (wheels 38). ) And a plurality of (four stages in the example shown in FIG. 5) transmission gear mechanisms 63-1, each having a different transmission ratio (gear ratio). -63-4 and the input shaft 61 and the output shaft 62 are engaged via any one of the plurality of transmission gear mechanisms 63-1 to 63-4, and the transmission gear mechanism to be engaged is switched. And a stepped transmission having an engaging mechanism 64 that is capable of operating.

  In the transmission gear mechanism (first speed gear mechanism) 63-1, one of the input side gear 63-1a and the output side gear 63-1b that mesh with each other is engaged with one of the input shaft 61 and the output shaft 62. The other of the input side gear 63-1a and the output side gear 63-1b is supported rotatably with respect to the other of the input shaft 61 and the output shaft 62. In the example shown in FIG. 5, the input side gear 63-1a of the first speed gear mechanism 63-1 is engaged with the input shaft 61, and the output side gear 63-1b of the first speed gear mechanism 63-1 is output shaft 62. Is supported rotatably. Similarly, when k is an integer of 2 to 4, even in the transmission gear mechanism (k-speed gear mechanism) 63-k, one of the input side gear 63-ka and the output side gear 63-kb that mesh with each other. Is engaged with one of the input shaft 61 and the output shaft 62, and the other of the input side gear 63-ka and the output side gear 63-kb is rotatably supported with respect to the other of the input shaft 61 and the output shaft 62. Yes. In the example shown in FIG. 5, the input side gear 63-2a of the second gear mechanism 63-2 is engaged with the input shaft 61, and the output gear 63-2b of the second gear mechanism 63-2 is the output shaft 62. Is supported rotatably. The input side gear 63-3a of the third speed gear mechanism 63-3 and the input side gear 63-4a of the fourth speed gear mechanism 63-4 are rotatably supported with respect to the input shaft 61, and the third speed gear mechanism 63 is supported. Output side gear 63-3b and output side gear 63-4b of the fourth speed gear mechanism 63-4 are engaged with the output shaft 62. Here, the transmission gear mechanisms 63-1 to 63-4 are all forward gear mechanisms for moving the vehicle forward (forwardly driving the wheels 38), and the transmission gear ratio (gear ratio, input side gear rotation). When arranged in the descending order of speed / output side gear rotation speed), “first gear mechanism 63-1” → “second gear mechanism 63-2” → “third gear mechanism 63-3” → “fourth gear mechanism” 63-4 ".

  In the engagement mechanism 64, the first speed engagement member 64-1 is mechanically connected to the output side gear 63-1b of the first speed gear mechanism 63-1, and the second speed engagement member 64-2 is the second speed gear mechanism. 63-2 is mechanically connected to the output side gear 63-2b, and the output side engaging member 64-5 is output at a position between the first speed engaging member 64-1 and the second speed engaging member 64-2. The output side engaging sleeve 64-6 is engaged with the shaft 62, and is movable along the axial direction of the output shaft 62. Further, in the engagement mechanism 64, the third speed engagement member 64-3 is mechanically connected to the input side gear 63-3a of the third speed gear mechanism 63-3, and the fourth speed engagement member 64-4 is fourth speed. The input side engagement member 64-7 is mechanically coupled to the input side gear 63-4a of the gear mechanism 63-4, and the position between the third speed engagement member 64-3 and the fourth speed engagement member 64-4 Is engaged with the input shaft 61, and the input-side engagement sleeve 64-8 is movable along the axial direction of the input shaft 61.

  In the stepped transmission 44, it is possible to select any one of a plurality of shift speeds (1st to 4th speed in the example shown in FIG. 5) and to switch the selected shift speed. It is. When the first speed gear or the second speed gear is selected, the engagement mechanism 64 includes the output side engagement member 64-5 and the m-speed engagement member 64-m (m is 1 or 2) as the output side engagement sleeve 64. -6, and the output side gear 63-mb of the m speed gear mechanism 63-m is engaged with the output shaft 62, so that the m speed gear mechanism 63-m (input side gear 63-ma and The input shaft 61 and the output shaft 62 are engaged via the output side gear 63-mb). When selecting the 3rd speed gear or the 4th speed gear, the engagement mechanism 64 includes the input side engagement member 64-7 and the m speed engagement member 64-m (m is 3 or 4) as the input side engagement sleeve 64. -8 is engaged, and the input side gear 63-ma of the m-speed gear mechanism 63-m is engaged with the input shaft 61, whereby the input shaft 61 and the output are output via the m-speed gear mechanism 63-m. The shaft 62 is engaged. When the m-speed gear is selected, the power from the output-side rotor 18 transmitted to the input shaft 61 is shifted by the m-speed gear mechanism 63-m at a gear ratio corresponding to the m-speed gear at the current shift stage. And transmitted from the output shaft 62 to the wheel 38. When switching from the mth gear of the current gear to the nth gear of the next gear (m and n are integers of 1 to 4 and m ≠ n), the engagement mechanism 64 changes to the current gear. By releasing the m-speed engagement member 64-m and the output-side engagement member 64-5 (or the input-side engagement member 64-7) in the corresponding engagement state, the m-speed gear mechanism 63-m is interposed. The engagement between the input shaft 61 and the output shaft 62 is released, and the n-speed engagement member 64-n and the output-side engagement member 64-5 (or the input-side engagement member 64) in the released state corresponding to the next shift stage are released. −7) is engaged, and the input shaft 61 and the output shaft 62 are engaged via the n-speed gear mechanism 63-n. As a result, the transmission gear mechanism that engages the input shaft 61 and the output shaft 62 can be switched from the m-speed gear mechanism 63-m to the n-speed gear mechanism 63-n, and the shift speed of the transmission 44 is changed to the current shift speed. The shift operation for changing from the first gear to the next gear can be performed.

  As for the engagement mechanism 64 here, a synchromesh for synchronizing the rotation of the output shaft 62 and the output side gear 63-mb (m is 1 or 2) when selecting the 1st gear or the 2nd gear. Synchronization mesh mechanism) and a synchromesh for synchronizing the rotation of the input shaft 61 and the input side gear 63-ma (m is 3 or 4) when selecting the third gear or the fourth gear. You can also Also, a dog clutch mechanism for engaging the output shaft 62 and the output side gear 63-mb (m is 1 or 2), and the input shaft 61 and the input side gear 63-ma (m is 3 or 4) are engaged. It is also possible to constitute the engagement mechanism 64 including a dog clutch mechanism for the purpose. As described above, the always-meshing manual transmission includes the speed change gear mechanisms 63-1 to 63-4 and the engagement mechanism 64, and the speed ratio between the input shaft 61 and the output shaft 62 is increased in multiple stages (see FIG. In the example shown in FIG. 5, a speed change mechanism that can be changed in four steps) can be configured.

  The chargeable / dischargeable power storage device 42 provided as a direct current power source can be constituted by a secondary battery, for example, and stores electrical energy. Inverter 40 provided as a first power conversion device that performs power conversion between power storage device 42 and stator winding 20 includes a switching element and a diode (rectifier element) connected in reverse parallel to the switching element. It can be realized by a known configuration, and can be supplied to each phase of the stator winding 20 by converting DC power from the power storage device 42 to AC (for example, three-phase AC) by switching operation of the switching element. . Furthermore, the inverter 40 can also convert power in a direction in which alternating current flowing in each phase of the stator winding 20 is converted into direct current and electric energy is collected in the power storage device 42. Thus, the inverter 40 can perform bidirectional power conversion between the power storage device 42 and the stator winding 20.

  The slip ring 95 is mechanically coupled to the input side rotor 28, and is electrically connected to each phase of the rotor winding 30. The brush 96 whose rotation is fixed is pressed against the slip ring 95 to be in electrical contact. The slip ring 95 rotates with the input-side rotor 28 while sliding with respect to the brush 96 (maintaining electrical contact with the brush 96). The brush 96 is electrically connected to the inverter 41. An inverter 41 provided as a second power conversion device that performs power conversion between any of the power storage device 42 and the inverter 40 and the rotor winding 30 includes a switching element and a diode (rectifier connected in reverse parallel to the switching element). Element), the DC power from the power storage device 42 is converted into alternating current (for example, three-phase alternating current) by the switching operation of the switching element, and the rotor is connected via the brush 96 and the slip ring 95. It is possible to supply each phase of the winding 30. Furthermore, the inverter 41 can also perform power conversion in a direction in which an alternating current flowing in each phase of the rotor winding 30 is converted into a direct current. At that time, AC power of the rotor winding 30 is extracted by the slip ring 95 and the brush 96, and the extracted AC power is converted to DC by the inverter 41. The electric power converted into direct current by the inverter 41 can be supplied to each phase of the stator winding 20 after being converted into alternating current by the inverter 40. That is, the inverter 40 can convert either (at least one) of the DC power from the inverter 41 and the DC power from the power storage device 42 into AC and supply it to each phase of the stator winding 20. In addition, the power converted into direct current by the inverter 41 can be recovered by the power storage device 42. Thus, the inverter 41 can perform bidirectional power conversion between any of the power storage device 42 and the inverter 40 and the rotor winding 30.

  The electronic control unit 50 controls the alternating current flowing in each phase of the stator winding 20 by controlling the switching operation of the switching element of the inverter 40 and controlling the power conversion in the inverter 40. The electronic control unit 50 controls the alternating current flowing in each phase of the rotor winding 30 by controlling the switching operation of the switching element of the inverter 41 and controlling the power conversion in the inverter 41. The electronic control unit 50 also performs control for switching mechanical engagement / release of the input side rotor 28 and the output side rotor 18 by switching engagement / release of the clutch 48. Further, the electronic control unit 50 also performs control of the operating state of the engine 36 and drive control of the engagement mechanism 64 for selecting the gear position of the transmission 44. In the present embodiment, selection of the shift stage of the transmission 44 by drive control of the engagement mechanism 64 is performed by the electronic control unit 50, and the transmission 44 functions as an automatic manual transmission (AMT).

  When a plurality of phases (for example, three phases) of alternating current flows through the plurality of stator windings 20 by the switching operation of the inverter 40, the stator windings 20 generate a rotating magnetic field that rotates in the circumferential direction of the stator. The torque (magnet torque) can be applied to the output-side rotor 18 by electromagnetic interaction (attraction and repulsion) between the rotating magnetic field generated in the stator winding 20 and the field magnetic flux generated in the permanent magnet 32. The output side rotor 18 can be rotationally driven. That is, the electric power supplied from the power storage device 42 to the stator winding 20 via the inverter 40 can be converted into the power (mechanical power) of the output-side rotor 18, and the stator 16 and the output-side rotor 18 are connected to the synchronous motor ( PM motor part). Furthermore, it is possible to convert the power of the output side rotor 18 into the electric power of the stator winding 20 and collect it in the power storage device 42 via the inverter 40. As described above, the stator winding 20 of the stator 16 and the permanent magnet 32 of the output side rotor 18 are electromagnetically coupled, so that the rotating magnetic field generated in the stator winding 20 is applied to the output side rotor 18. A torque (magnet torque) can be applied between the stator 16 and the output-side rotor 18. Further, for example, as shown in FIG. 4, an example in which a magnetic material (ferromagnetic material) is disposed between the permanent magnets 32 as salient pole portions facing the stator 16 (tooth 51a), or the permanent magnet 32 is on the output side. In the example embedded in the rotor 18 (in the rotor core 53), the reluctance torque in addition to the magnet torque is also applied to the stator 16 and the output side rotor in response to the rotating magnetic field generated by the stator 16 acting on the output side rotor 18. 18 to act. The electronic control unit 50 controls the torque acting between the stator 16 and the output-side rotor 18 by controlling the amplitude and phase angle of the alternating current flowing through the stator winding 20 by the switching operation of the inverter 40, for example. Can do.

  Further, as the input side rotor 28 rotates relative to the output side rotor 18, a rotation difference is generated between the input side rotor 28 (rotor winding 30) and the output side rotor 18 (permanent magnet 33). An induced electromotive force is generated in the winding 30, and an induced current (alternating current) flows in the rotor winding 30 due to the induced electromotive force, thereby generating a rotating magnetic field. The torque can be applied to the output-side rotor 18 by the electromagnetic interaction between the rotating magnetic field generated by the induced current of the rotor winding 30 and the field flux of the permanent magnet 33, and the output-side rotor 18 is driven to rotate. Can do. As described above, the rotor winding 30 of the input-side rotor 28 and the permanent magnet 33 of the output-side rotor 18 are electromagnetically coupled, so that the rotating magnetic field generated in the rotor winding 30 acts on the output-side rotor 18. As a result, torque (magnet torque) acts between the input-side rotor 28 and the output-side rotor 18. Therefore, power (mechanical power) can be transmitted between the input-side rotor 28 and the output-side rotor 18, and the input-side rotor 28 and the output-side rotor 18 can function as an induction electromagnetic coupling unit.

  When the torque (electromagnetic coupling torque) is generated between the input side rotor 28 and the output side rotor 18 by the induced current of the rotor winding 30, the electronic control unit 50 causes the induced current to flow through the rotor winding 30. The switching operation of the inverter 41 is performed so as to allow this. At that time, the electronic control unit 50 controls the alternating current flowing through the rotor winding 30 by the switching operation of the inverter 41, so that the electromagnetic coupling torque acting between the input-side rotor 28 and the output-side rotor 18. Can be controlled. On the other hand, the electronic control unit 50 maintains the switching element of the inverter 41 in the OFF state and stops the switching operation, so that the induced current does not flow through the rotor winding 30, and the input side rotor 28 and the output side rotor 18 In the meantime, the torque stops working.

  Next, the operation of the hybrid drive device according to this embodiment will be described.

  When the engine 36 is generating power, the power of the engine 36 is transmitted to the input side rotor 28, and the input side rotor 28 is rotationally driven in the engine rotation direction. When the rotational speed of the input side rotor 28 becomes higher than the rotational speed of the output side rotor 18 in a state where the clutch 48 is released, an induced electromotive force is generated in the rotor winding 30. The electronic control unit 50 performs the switching operation of the inverter 41 so as to allow the induced current to flow through the rotor winding 30. As a result, electromagnetic coupling torque in the engine rotation direction acts on the output side rotor 18 from the input side rotor 28 due to the electromagnetic interaction between the induced current of the rotor winding 30 and the field flux of the permanent magnet 33, and the output side rotor 18 Driven in the direction of engine rotation. Thus, the power from the engine 36 transmitted to the input side rotor 28 is transmitted to the output side rotor 18 by electromagnetic coupling between the rotor winding 30 of the input side rotor 28 and the permanent magnet 33 of the output side rotor 18. The The power transmitted to the output side rotor 18 is transmitted to the drive shaft 37 (wheels 38) after being shifted by the transmission 44, and used for forward driving of the load such as forward drive of the vehicle. Therefore, the wheel 38 can be rotationally driven in the forward direction using the power of the engine 36, and the vehicle can be driven in the forward direction. Further, since the rotation difference between the input side rotor 28 and the output side rotor 18 can be allowed, the engine 36 does not stall even if the rotation of the wheels 38 is stopped. Therefore, the rotating electrical machine 10 can function as a starting device, and there is no need to separately provide a starting device such as a friction clutch or a torque converter.

  Further, AC power generated in the rotor winding 30 is taken out via the slip ring 95 and the brush 96. The extracted AC power is converted into DC by the inverter 41. Then, by the switching operation of the inverter 40, the DC power from the inverter 41 is converted into AC by the inverter 40 and then supplied to the stator winding 20, whereby an AC current flows through the stator winding 20 and rotates to the stator 16. A magnetic field is formed. The torque in the engine rotation direction can be applied to the output side rotor 18 also by the electromagnetic interaction between the rotating magnetic field of the stator 16 and the field flux of the permanent magnet 32 of the output side rotor 18. As a result, a torque amplification function for amplifying the torque of the output side rotor 18 in the engine rotation direction can be realized. It is also possible to collect DC power from the inverter 41 in the power storage device 42.

  Further, by controlling the switching operation of the inverter 40 so that electric power is supplied from the power storage device 42 to the stator winding 20, the wheel 38 is rotated in the normal rotation direction using the power of the engine 36, and the stator winding 20. The rotational drive of the wheel 38 in the forward rotation direction can be assisted by the power of the output-side rotor 18 generated using the power supplied to the wheel. Further, at the time of load deceleration operation, the electronic control unit 50 controls the switching operation of the inverter 40 so that power is recovered from the stator winding 20 to the power storage device 42, so that the load power is transmitted to the stator winding 20 and the permanent magnet. The electric power of the stator winding 20 can be converted by the electromagnetic coupling with 32 and recovered in the power storage device 42.

  Further, by engaging the clutch 48 and mechanically connecting the input side rotor 28 and the output side rotor 18, an alternating current does not flow through the rotor winding 30, and the input side rotor 28 and the output side rotor 18 are not connected. Even if torque does not act on the power, the power from the engine 36 can be transmitted to the drive shaft 37 (wheels 38) via the clutch 48. This makes it possible to suppress Joule loss caused by the induction current flowing through the rotor winding 30 due to the slip between the input-side rotor 28 and the output-side rotor 18.

  In addition, when EV (Electric Vehicle) traveling is performed by driving the load using the power of the rotating electrical machine 10 without using the power of the engine 36 (rotating the wheel 38), the electronic control unit 50 By controlling the switching operation, drive control of the load is performed. For example, the electronic control unit 50 controls the switching operation of the inverter 40 so that the DC power from the power storage device 42 is converted into AC and supplied to the stator winding 20, thereby supplying power to the stator winding 20. Is converted into power of the output-side rotor 18 by electromagnetic coupling between the stator winding 20 and the permanent magnet 32, and the drive shaft 37 (wheel 38) is rotationally driven. Thus, even if the engine 36 is not generating power, the wheels 38 can be rotationally driven by supplying power to the stator winding 20. In addition, when performing EV traveling, the clutch 48 is controlled to a released state.

  The electronic control unit 50 also performs the switching operation of the inverter 40 so as to supply electric power from the power storage device 42 to the stator windings 20 when performing reverse running in which the vehicle is moved backward (wheels 38 are rotated in the reverse direction). By controlling, it is possible to transmit the power generated in the output side rotor 18 to the wheel 38 via the transmission 44 and to rotate the wheel 38 in the reverse direction. As described above, when reverse traveling is performed by EV traveling, it is possible to omit the reverse (reverse) transmission gear mechanism in the transmission 44. However, it is also possible to perform reverse traveling by providing a reverse transmission gear mechanism in the transmission 44 and transmitting the power from the engine 36 to the wheels 38 via the transmission 44 (reverse transmission gear mechanism). It is.

  Further, when starting the engine 36, the electronic control unit 50 converts the DC power from the power storage device 42 into AC by the inverter 41 and supplies it to the rotor winding 30 via the slip ring 95 and the brush 96. By controlling the switching operation of the inverter 41, torque in the engine rotation direction is applied from the output side rotor 18 to the input side rotor 28 by the alternating current of the rotor winding 30. As a result, the input side rotor 28 is rotated in the engine rotation direction using the power supplied from the power storage device 42 to the rotor winding 30 to crank the engine 36. During cranking of the engine 36, torque is applied to the input-side rotor 28 connected to the engine 36 by electromagnetic interaction between the rotating magnetic field of the input-side rotor 28 and the field flux of the permanent magnet 33 of the output-side rotor 18. The output side rotor 18 also receives the reaction torque. Therefore, when starting the engine 36 during EV traveling, the switching operation of the inverter 40 is controlled so that electric power is supplied from the power storage device 42 to the stator winding 20 and the torque that cancels the reaction torque is applied to the output-side rotor 18. As a result, the output-side rotor 18 can be rotationally driven using the power supplied to the stator winding 20. In addition, when starting the engine 36, the clutch 48 is controlled to a released state.

  When the power of the engine 36 is transmitted to the drive shaft 37, the stepped transmission 44 has the m-speed engagement member 64-m and the output-side engagement member 64-5 (or the input-side engagement member 64) in the engaged state. -7) is released, and the n-speed engagement member 64-n in the released state and the output side engagement member 64-5 (or the input side engagement member 64-7) are engaged, so that m It is possible to perform a shift operation for switching from the speed gear to the n-th gear of the next shift stage (m and n are integers of 1 to 4 and m ≠ n). During the shifting operation, the m-speed engagement member 64-m and the output-side engagement member 64-5 (or the input-side engagement member 64-7) are released, and then the n-speed engagement member 64-n and the output are output. During the period until the side engaging member 64-5 (or the input side engaging member 64-7) is engaged, the rotational speed Nmg of the input shaft 61 (output side rotor 18) is set to the current gear stage (m speed gear). It is necessary to change from the corresponding rotational speed Nrefm to the rotational speed Nrefn corresponding to the next gear position (n-th gear). During the upshift operation (m <n), it is necessary to decrease the rotational speed Nmg of the input shaft 61, and during the downshift operation (m> n), it is necessary to increase the rotational speed Nmg of the input shaft 61. is there. However, after releasing the m-speed engagement member 64-m and the output-side engagement member 64-5 (or the input-side engagement member 64-7), the n-speed engagement member 64-n and the output-side engagement member 64 are released. -5 (or the input side engaging member 64-7) is engaged until the transmission of power in the transmission 44 is interrupted, so that the power of the engine 36 is applied to the drive shaft 37 (wheel 38). It will not be transmitted. In order to shorten the period during which power is not transmitted to the wheels 38 during the speed change operation (period during which power transmission in the transmission 44 is interrupted), the rotational speed Nmg of the input shaft 61 is set to the current gear stage (m-speed gear). It is desirable to quickly change from the rotational speed Nrefm according to) to the rotational speed Nrefn according to the next gear position (n-th gear).

Here, in order to shorten the period during which power is not transmitted to the wheel 38 during the speed change operation, the m-speed engagement member 64-m and the output side engagement member 64-5 (or the input side engagement member 64-7). ) During the period from when the n-speed engagement member 64-n is engaged with the output side engagement member 64-5 (or the input side engagement member 64-7). By applying PM motor torque Tmg between the stator 16 and the output-side rotor 18, the rotational speed Nmg of the input shaft 61 is changed from the rotational speed Nrefm corresponding to the m-speed gear to the rotational speed Nrefn corresponding to the n-speed gear. Consider the case of changing. In the upshift operation from the current gear to the next gear, when the PM motor torque Tmg in the deceleration direction (opposite to the engine rotation direction) is applied from the stator 16 to the output side rotor 18 by the alternating current of the stator winding 20 FIG. 6 shows the result of calculating the time change of the rotational speed Nmg of the input shaft 61 (output-side rotor 18). In the calculation, the inertia moment on the input shaft 61 side (including the output-side rotor 18) of the transmission 44 is 0.062 kg · m ² , the rotational speed Nrefm of the input shaft 61 corresponding to the current gear stage is 5500 rpm, The rotational speed Nrefn of the input shaft 61 corresponding to the gear stage is set to 3000 rpm, and the capacity of the inverter 40 (maximum power that can be converted into power) and the capacity of the power storage device 42 (maximum power that can be charged and discharged) are 5 kW, 7 kW, 10 kW, and 15 kW. , The time change of the rotational speed Nmg of the input shaft 61 is calculated. As shown in FIG. 6, the time required to change the rotational speed Nmg of the input shaft 61 from the rotational speed Nrefm = 5500 rpm corresponding to the current gear to the rotational speed Nrefn = 3000 rpm corresponding to the next gear is It becomes shorter as the maximum power that can be converted at 40 is increased, and becomes 1.46 seconds at 5 kW, 1.04 seconds at 7 kW, 0.72 seconds at 10 kW, and 0.48 seconds at 15 kW. However, when the rotational speed Nmg of the input shaft 61 is changed by applying the PM motor torque Tmg, the amount of power of the stator winding 20 is increased by the rotational speed difference Nmg between the output side rotor 18 and the stator 16. The amount of power Pmg converted between the stator winding 20 and the power storage device 42 via the inverter 40 also increases. As a result, it is necessary to increase the capacity of the inverter 40 (maximum power that can be converted) and the capacity of the power storage device 42 (maximum power that can be charged / discharged).

  Therefore, in the present embodiment, the electronic control unit 50 changes the gear position of the stepped transmission 44 when the gear position of the stepped transmission 44 is changed from the m-speed gear of the current gear stage to the n-speed gear of the next gear stage. When the m-speed engagement member 64-m and the output-side engagement member 64-5 (or the input-side engagement member 64-7) in the combined state are released, the inverter 41 causes the AC current to flow through the rotor winding 30. By controlling the power conversion (switching operation) and applying the electromagnetic coupling torque Tcoup between the input side rotor 28 and the output side rotor 18, the rotational speed Nmg of the input shaft 61 is changed to the next speed (n-speed gear). The rotational speed Nmg of the output side rotor 18 and the input shaft 61 is changed so as to approach the target input shaft rotational speed Nrefn corresponding to. More specifically, after releasing at least the m-speed engagement member 64-m and the output-side engagement member 64-5 (or the input-side engagement member 64-7), the n-speed engagement member 64-n and the output are output. During the period until the side engaging member 64-5 (or the input side engaging member 64-7) is engaged, the electromagnetic coupling torque Tcouple from the input side rotor 28 to the output side rotor 18 due to the alternating current of the rotor winding 30. , The rotation speed Nmg of the input shaft 61 is changed from the rotation speed Nrefm corresponding to the m-th gear to the target input shaft rotation speed Nrefn corresponding to the n-th gear. At this time, the target input shaft rotational speed Nrefn corresponding to the n-th gear is determined from the transmission ratio of the n-speed gear mechanism 63-n and the rotational speed (vehicle speed) of the drive shaft 37.

  Furthermore, in this embodiment, the electronic control unit 50 releases the m-speed engagement member 64-m and the output side engagement member 64-5 (or the input side engagement member 64-7), and An electromagnetic coupling torque Tcoup is applied between the input side rotor 28 and the output side rotor 18 by an alternating current, and power conversion (switching operation) in the inverter 40 is controlled so that an alternating current flows through the stator winding 20. Thus, by applying the PM motor torque Tmg between the stator 16 and the output-side rotor 18, the output-side rotor is set so that the rotational speed Nmg of the input shaft 61 approaches the target input shaft rotational speed Nrefn corresponding to the n-th gear. 18 and the rotational speed Nmg of the input shaft 61 are changed. More specifically, after releasing at least the m-speed engagement member 64-m and the output-side engagement member 64-5 (or the input-side engagement member 64-7), the n-speed engagement member 64-n and the output are output. During the period until the side engaging member 64-5 (or the input side engaging member 64-7) is engaged, the electromagnetic coupling torque Tcouple from the input side rotor 28 to the output side rotor 18 due to the alternating current of the rotor winding 30. And the PM motor torque Tmg from the stator 16 to the output-side rotor 18 by the alternating current of the stator winding 20 can also be used to change the rotational speed Nmg of the input shaft 61 from the rotational speed Nrefm corresponding to the m-speed gear. The target input shaft rotational speed Nrefn corresponding to the n-th gear is changed. At that time, the PM motor torque Tmg acting on the output side rotor 18 from the stator 16 by the alternating current of the stator winding 20 is the electromagnetic cup acting on the output side rotor 18 from the input side rotor 28 by the alternating current of the rotor winding 30. The direction is the same as the ring torque Tcoup.

  In the upshift operation from the m-speed gear to the n-speed gear (m <n), the m-speed engagement member 64-m and the output-side engagement member 64-5 (or the input-side engagement member 64-7) are released. Then, as shown by an arrow B in FIGS. 7 and 8, the switching operation of the inverter 41 is controlled so that electric power is supplied to the rotor winding 30, and the deceleration direction (engine rotation direction and By applying the electromagnetic coupling torque Tcoup in the reverse direction, the rotational speed Nmg of the input shaft 61 (output-side rotor 18) is reduced to the target input shaft rotational speed Nrefn corresponding to the n-th gear. At the same time, as indicated by an arrow A in FIGS. 7 and 8, the switching operation of the inverter 40 is controlled so that power is recovered from the stator winding 20, and the deceleration direction from the stator 16 to the output-side rotor 18 (reverse to the engine rotation direction). Also, the rotational speed Nmg of the input shaft 61 is decreased to the target input shaft rotational speed Nrefn corresponding to the n-th gear by applying the PM motor torque Tmg in the direction). At that time, as indicated by arrows A and B in FIG. 8, the AC power recovered from the stator winding 20 is converted into DC by the inverter 40, and further converted from DC to AC by the inverter 41, and the brush 96. And supplied to the rotor winding 30 via the slip ring 95. The difference between the supplied power Pcouple to the rotor winding 30 and the recovered power Pmg from the stator winding 20 is covered by the power Pb of the power storage device 42.

  However, in the upshift operation, when the electromagnetic coupling torque Tcoup in the deceleration direction is applied from the input side rotor 28 to the output side rotor 18 by the alternating current of the rotor winding 30, the reaction is counteracted by the output side rotor 18 to the input side rotor. The electromagnetic coupling torque Tcouple in the speed increasing direction (engine rotation direction) acts on the motor 28. If the torque in the speed increasing direction acting on the input-side rotor 28 becomes too large, the rotation of the engine 36 suddenly rises, giving a sense of discomfort to the driver of the vehicle. Therefore, in the upshift operation, when the rotational speed Nmg of the input shaft 61 is decreased to the target input shaft rotational speed Nrefn corresponding to the n-th gear, generation of torque of the engine 36 is stopped and output from the input-side rotor 28 is performed. The electromagnetic coupling torque Tcoup in the deceleration direction applied to the side rotor 18 is preferably limited to a load loss torque Tl or less of the engine 36 so that the rotation of the engine 36 does not suddenly blow up. The load loss torque Tl of the engine 36 here is necessary to keep the rotational speed Neng of the engine 36 constant in a state where the electromagnetic coupling torque Tcoup is not acting between the input side rotor 28 and the output side rotor 18. This is expressed as a torque generated by the engine 36. For example, the load loss torque Tl of the engine 36 can be set from the friction torque of the engine 36. In this case, the load loss torque Tl of the engine 36 is set to change according to the rotational speed Neng of the engine 36. It is also possible. Furthermore, it is possible to set the load loss torque Tl of the engine 36 in consideration of not only the friction torque of the engine 36 but also the driving torque of engine auxiliary equipment such as a pump and a generator.

In the upshift operation from the current gear to the next gear, the electromagnetic coupling torque Tcoup in the deceleration direction is applied from the input side rotor 28 to the output side rotor 18 by the alternating current of the rotor winding 30 and the stator winding 20 FIG. 9 shows the result of calculating the time variation of the rotational speed Nmg of the input shaft 61 (output side rotor 18) when the PM motor torque Tmg in the deceleration direction is applied from the stator 16 to the output side rotor 18 by the alternating current. . In the calculation, the inertia moment on the input shaft 61 side (including the output side rotor 18) of the stepped transmission 44 is 0.062 kg · m ² , and the inertia moment on the engine 36 side (including the input side rotor 28). 0.1 kg · m ² , the rotational speed Nrefm of the input shaft 61 corresponding to the current gear stage is 5500 rpm, the rotational speed Nrefn of the input shaft 61 corresponding to the next gear stage is 3000 rpm, and the electromagnetic coupling torque Tcouple is the load of the engine 36 Loss torque Tl is limited to 21 Nm or less, and the capacity of inverters 40 and 41 (maximum power that can be converted) and the capacity of power storage device 42 (maximum power that can be charged and discharged) are changed to 5 kW, 7 kW, 10 kW, and 15 kW. The time change of the rotational speed Nmg of the input shaft 61 is calculated. As shown in FIG. 9, the time required to change the rotational speed Nmg of the input shaft 61 from the rotational speed Nrefm = 5500 rpm corresponding to the current gear to the rotational speed Nrefn = 3000 rpm corresponding to the next gear is It becomes shorter as the maximum power that can be converted at 40 and 41 increases, and becomes 0.50 seconds at 5 kW, 0.44 seconds at 7 kW, 0.37 seconds at 10 kW, and 0.30 seconds at 15 kW. By applying torque in the same direction to the output side rotor 18 from both the input side rotor 28 and the stator 16, the same inverter capacity (power) can be used compared to the case where torque is applied to the output side rotor 18 only from the stator 16. The torque that acts on the output-side rotor 18 (input shaft 61) can be increased under the condition of the maximum power that can be converted), and the rotational speed Nmg of the input shaft 61 is changed from the rotational speed Nrefm corresponding to the current gear to the next shift. It is possible to shorten the time required for changing to the rotational speed Nrefn corresponding to the stage.

  During the speed change operation, the rotational speed difference Neng−Nmg between the input side rotor 28 (engine 36) and the output side rotor 18 is sufficiently smaller than the rotational speed difference Nmg between the output side rotor 18 and the stator 16. Therefore, when the power of the rotor winding 30 and the power of the stator winding 20 are the same, the electromagnetic coupling torque Tcouple acting on the output side rotor 18 from the input side rotor 28 is the PM acting on the output side rotor 18 from the stator 16. It is sufficiently larger than the motor torque Tmg. Therefore, even when the electromagnetic coupling torque Tcoup is applied only from the input side rotor 28 to the output side rotor 18 without applying the PM motor torque Tmg from the stator 16 to the output side rotor 18, the output side from the stator 16 only. Compared with the case where the PM motor torque Tmg is applied to the rotor 18, the torque applied to the output side rotor 18 (input shaft 61) can be increased under the same inverter capacity (maximum power that can be converted). The time required for changing the rotational speed Nmg of the input shaft 61 from the rotational speed Nrefm corresponding to the current shift speed to the rotational speed Nrefn corresponding to the next shift speed can be shortened.

  In an upshift operation (m <n) from the mth gear of the current gear to the nth gear of the next gear (m <n), the electromagnetic coupling torque Tcoup applied from the input side rotor 28 to the output side rotor 18, FIG. 10A shows an example of a time change of the PM motor torque Tmg applied to the rotor 18 and the torque Tcoup + Tmg applied to the input shaft 61 (output-side rotor 18) (both are positive in the engine rotation direction). FIG. 10B shows an example of temporal changes in the rotational speed Neng of the input side rotor 28) and the rotational speed Nmg of the input shaft 61 (output side rotor 18). In the example shown in FIGS. 10A and 10B, when a shift command from the current shift stage to the next shift stage is output at time t0, the clutch 48 is disengaged and the machine between the input side rotor 28 and the output side rotor 18 is released. The m-speed engagement member 64-m and the output-side engagement member 64-5 (or the input-side engagement member 64-7) in the engaged state corresponding to the current gear position are released. Then, an electromagnetic coupling torque Tcouple in the deceleration direction is applied from the input side rotor 28 to the output side rotor 18 by the alternating current of the rotor winding 30, and the speed is reduced from the stator 16 to the output side rotor 18 by the alternating current of the stator winding 20. The direction PM motor torque Tmg is applied. As a result, the rotational speed Nmg of the input shaft 61 is decreased from the rotational speed Nrefm (5500 rpm) corresponding to the current gear to the rotational speed Nrefn (3000 rpm) corresponding to the next gear. In the example shown in FIGS. 10A and 10B, the electric energy Pcoup of the rotor winding 30 under the condition that the electromagnetic coupling torque Tcoup is equal to the load loss torque Tl (21 Nm) of the engine 36 is equal to or less than the capacity (5 kW) of the inverter 41. In this case, an electromagnetic coupling torque Tcoup equal to the load loss torque Tl of the engine 36 is generated so that the rotational speed Neng of the engine 36 is kept constant (5500 rpm), and the electromagnetic coupling torque Tcoup is the load loss of the engine 36. When the electric power Pcouple of the rotor winding 30 under the condition equal to the torque Tl exceeds the capacity of the inverter 41, the electromagnetic coupling torque Tcoup so that the electric power Pcopup of the rotor winding 30 is limited to the capacity of the inverter 41. Is generated. At the same time, the PM motor torque Tmg is generated so that the power amount Pmg of the stator winding 20 is limited to the capacity (5 kW) of the inverter 40. At times t0 to t1, as shown in FIG. 10A, the deceleration-direction electromagnetic coupling torque Tcoup acting on the output-side rotor 18 from the input-side rotor 28 becomes the deceleration-direction PM acting on the output-side rotor 18 from the stator 16. The rotational speed Neng of the engine 36 is higher than the rotational speed Nmg of the input shaft 61 as shown in FIG. 10B.

  When the rotational speed Nmg of the input shaft 61 decreases to the rotational speed Nrefn (3000 rpm) corresponding to the next shift stage at time t1, the released n-speed engagement member 64-n corresponding to the next shift stage and the output side engagement The member 64-5 (or the input side engaging member 64-7) is engaged. Then, the switching operation of the inverter 41 is controlled so that power is recovered from the rotor winding 30, and the electromagnetic coupling torque Tcoup in the acceleration direction is applied from the input side rotor 28 to the output side rotor 18 (input from the output side rotor 18). And the switching operation of the inverter 40 is controlled so that electric power is supplied to the stator winding 20, and PM in the acceleration direction is transferred from the stator 16 to the output side rotor 18. Motor torque Tmg is applied. As a result, the power of the output side rotor 18 is changed by the transmission 44 (n-speed gear mechanism 63-n) and transmitted to the wheels 38, and the rotational speed Neng of the engine 36 (input side rotor 28) is changed to the input shaft 61 ( The rotational speed of the output rotor 18) is reduced to Nmg. In the example shown in FIGS. 10A and 10B, torque is applied from the stator 16 and the input-side rotor 28 to the output-side rotor 18 so that the power amounts Pmg and Pcoup of the stator winding 20 and the rotor winding 30 are limited to 5 kW or less. Let When the rotational speed Neng of the engine 36 decreases to the rotational speed Nmg of the input shaft 61 at time t2, the input side rotor 28 and the output side rotor 18 are mechanically engaged by engaging the clutch 48.

  On the other hand, in the downshift operation (m> n) from the m-speed gear to the n-speed gear, the m-speed engagement member 64-m and the output-side engagement member 64-5 (or the input-side engagement member 64-7). 11 and 12, the switching operation of the inverter 41 is controlled so as to recover the electric power from the rotor winding 30 as indicated by an arrow B in FIGS. The rotational speed Nmg of the input shaft 61 (output-side rotor 18) is increased to the target input shaft rotational speed Nrefn corresponding to the n-th gear by applying the electromagnetic coupling torque Tcoup in the rotational direction. When the electromagnetic coupling torque Tcoup is applied, a torque larger than the electromagnetic coupling torque Tcoup is applied to the engine so that the rotational speed Neng of the input side rotor 28 is maintained higher than the rotational speed Nmg of the output side rotor 18. By generating in 36, the rotational speed Neng of the engine 36 is increased as the rotational speed Nmg of the output-side rotor 18 increases. In that case, compared with the case where the m-speed engagement member 64-m and the output side engagement member 64-5 (or the input side engagement member 64-7) are released (before the electromagnetic coupling torque Tcouple is applied). Thus, it is possible to reduce the load loss torque Tl of the engine 36 by reducing the driving torque of the engine auxiliary equipment by reducing the discharge pressure of the pump or reducing the generated power of the generator. is there. Then, the electromagnetic coupling torque Tcouple is applied, and the switching operation of the inverter 40 is controlled so as to supply power to the stator winding 20 as shown by the arrow A in FIGS. The PM motor torque Tmg in the speed increasing direction (engine rotation direction) is also applied to increase the rotation speed Nmg of the input shaft 61 to the target input shaft rotation speed Nrefn corresponding to the nth gear. At that time, as indicated by arrows A and B in FIG. 12, the AC power recovered from the rotor winding 30 via the slip ring 95 and the brush 96 is converted into DC by the inverter 41, and further, It is converted from direct current to alternating current and supplied to the stator winding 20.

  In the present embodiment described above, when the gear stage of the stepped transmission 44 is changed from the m-th gear of the current gear stage to the n-th gear of the next gear stage, the m-speed engaged state corresponding to the current gear stage. When the engagement member 64-m and the output-side engagement member 64-5 (or the input-side engagement member 64-7) are released, the electromagnetic cup from the input-side rotor 28 to the output-side rotor 18 is caused by the alternating current of the rotor winding 30. By applying the ring torque Tcoup, the rotational speed Nmg of the input shaft 61 is changed to the target input shaft rotational speed Nrefn corresponding to the n-th gear. The rotational speed difference Neng−Nmg between the input-side rotor 28 and the output-side rotor 18 is sufficiently smaller than the rotational speed difference Nmg between the output-side rotor 18 and the stator 16, and the amount of power with respect to the generated torque can be suppressed. Therefore, the torque applied to the input shaft 61 can be increased while reducing the capacity of the inverters 40 and 41 (maximum power that can be converted) and the capacity of the power storage device 42 (maximum power that can be charged and discharged). The time required to change the rotational speed Nmg of the input shaft 61 to the target input shaft rotational speed Nrefn corresponding to the n-th gear can be shortened. Therefore, it is possible to shorten the period during which power is not transmitted to the wheel 38 during the speed change operation (period during which power transmission in the transmission 44 is interrupted). Further, in the upshift operation from the m-th gear to the n-th gear, when the rotational speed Nmg of the input shaft 61 is decreased to the target input shaft rotational speed Nrefn corresponding to the n-th gear, the input side rotor 28 is changed to the output side rotor. By restricting the electromagnetic coupling torque Tcoup in the deceleration direction to be applied to the engine 18 to be equal to or less than the load loss torque Tl of the engine 36, it is possible to suppress the excessive increase in the rotation of the engine 36.

  In the upshift operation, when the rotational speed Nmg of the input shaft 61 is decreased to the target input shaft rotational speed Nrefn corresponding to the n-th gear, the electromagnetic coupling torque Tcoup is applied and the m-speed engaging member 64- m and the output-side engagement member 64-5 (or the input-side engagement member 64-7) are released (before the electromagnetic coupling torque Tcoup is applied), or the discharge pressure of the pump is increased, It is also possible to increase the load loss torque Tl of the engine 36 by increasing the driving torque of the engine accessory by increasing the power generated by the generator. As a result, it is possible to increase the electromagnetic coupling torque Tcouple in the deceleration direction that is applied from the input side rotor 28 to the output side rotor 18 while suppressing the increase in rotation of the engine 36, and the rotational speed Nmg of the input shaft 61 is reduced to n. The time required for changing to the target input shaft rotational speed Nrefn corresponding to the high gear can be further shortened.

  Further, in the upshift operation, when the rotational speed Nmg of the input shaft 61 is decreased to the target input shaft rotational speed Nrefn corresponding to the n-th gear, the rotational speed Neng of the engine 36 (input-side rotor 28) is m-speed. Compared with the case where the combined member 64-m and the output side engaging member 64-5 (or the input side engaging member 64-7) are released, the output from the input side rotor 28 is prevented so as not to blow up more than a predetermined rotational speed. It is also possible to control the electromagnetic coupling torque Tcouple in the deceleration direction applied to the side rotor 18 based on the rotational speed Neng of the engine 36. For example, when the rotational speed Neng of the engine 36 increases, the electromagnetic coupling torque Tcoup in the deceleration direction that acts on the output-side rotor 18 is decreased. The electromagnetic coupling torque Tcoup is increased. As a result, it is possible to increase the electromagnetic coupling torque Tcoup in the deceleration direction that acts on the output-side rotor 18 from the input-side rotor 28, while suppressing the rising of the rotation of the engine 36.

  Furthermore, in the present embodiment, when the rotational speed Nmg of the input shaft 61 is changed to the target input shaft rotational speed Nrefn corresponding to the n-th gear, PM is transferred from the stator 16 to the output-side rotor 18 by the alternating current of the stator winding 20. By applying the motor torque Tmg together with the electromagnetic coupling torque Tcoup, the torque applied to the input shaft 61 can be further increased, and the rotational speed Nmg of the input shaft 61 is set to the target input shaft rotational speed Nrefn corresponding to the n-th gear. It is possible to further shorten the time required to change the distance up to. In this case, the generated electric power generated in one of the stator winding 20 and the rotor winding 30 is supplied to the other of the stator winding 20 and the rotor winding 30 via the inverters 40 and 41, so that the electromagnetic coupling torque. Since Tcoup and PM motor torque Tmg can be applied to the output-side rotor 18, the power Pb of the power storage device 42 can be reduced compared to the inverters 40 and 41 passing power Pmg and Pcoup, and the capacity of the inverters 40 and 41. As compared with the above, the capacity of the power storage device 42 can be further reduced.

  FIG. 13 shows the result of calculating an example of the upshift operation when the capacity of the inverters 40 and 41 is larger than the capacity of the power storage device 42 (capacity 10 kW of the inverters 40 and 41, capacity 5 kW of the power storage device 42). FIG. 14 shows a result of calculating an example of the upshift operation in the case where the capacities of 40 and 41 are equal to the capacities of the power storage devices 42 (capacity 5 kW of the inverters 40 and 41 and capacities 5 kW of the power storage devices 42). 13 (a) and 14 (a) show the time change of the rotational speed Neng of the engine 36, the rotational speed Nmg of the output-side rotor 18 and the rotational speed difference Neng−Nmg (both are positive in the engine rotational direction). 13 (b) and 14 (b) show electromagnetic coupling torque Tcoup that acts on the output-side rotor 18 from the input-side rotor 28 and PM motor torque Tmg () that acts on the output-side rotor 18 from the stator 16. 13 (c) and 14 (c) show the electric power Pb of the power storage device 42 (positive when discharging and negative when charging), and the inverter 40. Passing power Pmg (positive when power is supplied to the stator winding 20 and negative when recovering power from the stator winding 20), and inverter 41 passing power Pcoup (rotor winding) The time power supply to the 30 positive, indicating the time change of the negative) the time power recovery from the rotor windings 30. As shown in FIGS. 13 and 14, by making the capacity of the inverters 40 and 41 larger than the capacity of the power storage device 42, the torque applied to the input shaft 61 can be further increased, and the rotational speed Nmg of the input shaft 61. Can be changed more rapidly. In the example shown in FIGS. 13 and 14, the time required to change the rotational speed Nmg of the input shaft 61 from 5500 rpm to 3000 rpm can be shortened from 0.51 seconds to 0.39 seconds.

  In the present embodiment, the transmission 44 may be an automatic transmission (AT). In this case, the transmission 44 is also a stepped transmission that can select a shift speed from a plurality of shift speeds, and is provided between the input shaft 61 and the output shaft 62, and has a plurality of degrees of freedom of rotation. A planetary gear mechanism, a plurality of friction engagement devices for limiting the degree of freedom of rotation of the planetary gear mechanism, and the engagement / engagement of each friction engagement device by controlling the hydraulic pressure supplied to each friction engagement device. It can be realized by a known configuration including a hydraulic control device that controls the release. Each friction engagement device can be constituted by a clutch or a brake, for example. In the transmission 44, by selectively engaging the friction engagement device corresponding to the gear stage using the hydraulic pressure in the hydraulic control device so that the rotational freedom degree of the planetary gear mechanism becomes one degree of freedom, It is possible to transmit the power from the output side rotor 18 transmitted to the input shaft 61 to the wheel 38 from the output shaft 62 after shifting at a gear ratio corresponding to the gear position. Further, the transmission 44 releases the engagement state of the friction engagement device corresponding to the current shift step and engages the release state of the friction engagement device corresponding to the next shift step, thereby changing the shift step (input shaft). It is possible to change the gear ratio between the gear ratio 61 and the output shaft 62 from the gear ratio corresponding to the current gear to the gear ratio corresponding to the next gear. Thus, the automatic transmission includes a planetary gear mechanism and a plurality of friction engagement devices, and a transmission mechanism that can change the gear ratio between the input shaft 61 and the output shaft 62 in multiple stages. Can be configured.

  Even in the example in which the stepped transmission 44 is an automatic transmission, during the shifting operation, the friction engagement device corresponding to the current shift stage is released and the friction engagement device corresponding to the next shift stage is engaged. During the period, it is necessary to change the rotation speed Nmg of the input shaft 61 from the rotation speed Nrefm corresponding to the current shift speed to the rotation speed Nrefn corresponding to the next shift speed, and from the engine 36 to the wheels 38 via the transmission 44. The transmitted power is reduced. Therefore, even in the example in which the stepped transmission 44 is an automatic transmission, the electronic control unit 50 is configured to change the speed of the stepped transmission 44 in the same manner as the example in which the stepped transmission 44 is an automatic manual transmission (AMT). Is changed from the current gear to the next gear, the switching operation of the inverter 41 is controlled so that an alternating current flows through the rotor winding 30 when the friction engagement device in the engaged state corresponding to the current gear is released. Then, by applying the electromagnetic coupling torque Tcoup from the input side rotor 28 to the output side rotor 18, the output side rotor so that the rotational speed Nmg of the input shaft 61 approaches the target input shaft rotational speed Nrefn corresponding to the next gear stage. 18 and the rotational speed Nmg of the input shaft 61 are changed. At the same time, the rotational speed Nmg of the input shaft 61 can be reduced by controlling the switching operation of the inverter 40 so that an alternating current flows through the stator winding 20 and applying the PM motor torque Tmg from the stator 16 to the output side rotor 18. It is possible to change the rotational speed Nmg of the output side rotor 18 and the input shaft 61 so as to approach the target input shaft rotational speed Nrefn corresponding to the next shift speed. This shortens the time required for changing the rotational speed Nmg of the input shaft 61 from the rotational speed Nrefm corresponding to the current gear stage to the rotational speed Nrefn corresponding to the next gear stage during the shift operation. The period during which the power transmitted to the wheels 38 decreases can be shortened while reducing the capacity of inverters 40 and 41 (maximum power that can be converted) and the capacity of power storage device 42 (maximum power that can be charged and discharged). be able to.

  As mentioned above, although the form for implementing this invention was demonstrated, this invention is not limited to such embodiment at all, and it can implement with a various form in the range which does not deviate from the summary of this invention. Of course.

  DESCRIPTION OF SYMBOLS 10 Rotating electric machine, 16 Stator, 18 Output side rotor (2nd rotor), 20 Stator winding, 28 Input side rotor (1st rotor), 30 Rotor winding, 32, 33 Permanent magnet, 36 Engine, 37 Drive shaft, 38 wheels, 40, 41 inverter, 42 power storage device, 44 transmission (stepped transmission), 50 electronic control unit, 51 stator core, 52, 53 rotor core, 61 input shaft, 62 output shaft, 63-1 to 63-4 Transmission gear mechanism, 64 engagement mechanism, 95 slip ring, 96 brush.

Claims (7)

A first rotor provided with a rotor conductor capable of generating a rotating magnetic field when power from the engine is transmitted and an alternating current flows;
A stator provided with a stator conductor capable of generating a rotating magnetic field when an alternating current flows;
A second rotor that is rotatable relative to the first rotor, wherein torque acts between the first rotor and the stator conductor in response to the rotating magnetic field generated by the rotor conductor. A second rotor in which a torque acts between the stator and the stator according to the action of the generated rotating magnetic field;
A stepped transmission that shifts power transmitted from a second rotor to an input shaft at a gear ratio according to a gear and transmits the power from an output shaft to a drive shaft, and includes an engagement member corresponding to the current gear. A stepped transmission capable of changing the shift stage from the current shift stage to the next shift stage by releasing and engaging the engagement member corresponding to the next shift stage;
A first power converter that performs power conversion between the power storage device and the stator conductor;
A second power conversion device that performs power conversion between either the power storage device or the first power conversion device and the rotor conductor;
The power conversion in the first power converter is controlled, the torque applied between the stator and the second rotor is controlled by the alternating current of the stator conductor, and the power conversion in the second power converter is controlled. A control device for controlling the torque applied between the first rotor and the second rotor by the alternating current of the rotor conductor;
With
When changing the shift stage of the stepped transmission from the current shift stage to the next shift stage, the control device releases the engaging shaft corresponding to the current shift stage and the rotation speed of the input shaft of the stepped transmission is By applying torque from the first rotor to the second rotor by the alternating current of the rotor conductor so as to approach the target input shaft rotation speed corresponding to the gear position, the input of the second rotor and the stepped transmission is performed. A power transmission device that changes the rotational speed of the shaft. The power transmission device according to claim 1,
When changing the shift stage of the stepped transmission from the current shift stage to the next shift stage, the control device releases the engaging shaft corresponding to the current shift stage and the rotation speed of the input shaft of the stepped transmission is Torque is applied from the first rotor to the second rotor by the alternating current of the rotor conductor so as to approach the target input shaft rotational speed corresponding to the gear position, and the second from the stator by the alternating current of the stator conductor. A power transmission device that changes the rotational speeds of the input shafts of the second rotor and the stepped transmission by applying a torque to the rotor. The power transmission device according to claim 1 or 2,
When the shift stage of the stepped transmission is upshifted from the current shift stage to the next shift stage, the control device releases the engagement member corresponding to the current shift stage so that power is recovered from the stator conductor. The power conversion in the second power conversion device is controlled so that torque is applied to the second rotor from the stator by the alternating current of the stator conductor by controlling power conversion in the power conversion device, and power is supplied to the rotor conductor. And by applying torque to the second rotor from the first rotor by the alternating current of the rotor conductor, the rotational speed of the input shaft of the stepped transmission is changed to the target input shaft rotational speed corresponding to the next gear stage. To reduce the power transmission device. The power transmission device according to any one of claims 1 to 3,
The control device reduces the rotational speed of the input shaft of the stepped transmission to the target input shaft rotational speed corresponding to the next shift stage when the shift stage of the stepped transmission is upshifted from the current shift stage to the next shift stage. A power transmission device that restricts the torque applied from the first rotor to the second rotor by the alternating current of the rotor conductor to be equal to or less than the load loss torque of the engine. The power transmission device according to any one of claims 1 to 4,
The control device reduces the rotational speed of the input shaft of the stepped transmission to the target input shaft rotational speed corresponding to the next shift stage when the shift stage of the stepped transmission is upshifted from the current shift stage to the next shift stage. A power transmission device that causes torque to act on the second rotor from the first rotor by the alternating current of the rotor conductor and increases the load loss torque of the engine. The power transmission device according to any one of claims 1 to 5,
The control device reduces the rotational speed of the input shaft of the stepped transmission to the target input shaft rotational speed corresponding to the next shift stage when the shift stage of the stepped transmission is upshifted from the current shift stage to the next shift stage. A power transmission device that controls torque to be applied from the first rotor to the second rotor by the alternating current of the rotor conductor based on the rotational speed of the engine. The power transmission device according to any one of claims 1 to 6,
When the gear shift stage of the stepped transmission is downshifted from the current shift speed to the next shift speed, the control device releases the engagement member corresponding to the current shift speed so as to recover power from the rotor conductor. The power conversion in the power converter is controlled so that torque is applied from the first rotor to the second rotor by the alternating current of the rotor conductor, and power is supplied to the stator conductor. By controlling the power conversion and applying torque from the stator to the second rotor by the alternating current of the stator conductor, the rotational speed of the input shaft of the stepped transmission is set to the target input shaft rotational speed corresponding to the next gear. To increase the power transmission device.