JP2012001102A - Hybrid drive device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hybrid drive device capable of properly preventing the generation of rattling noise during a steady-state operation of an internal combustion engine.SOLUTION: The hybrid drive device includes: a connection member I drive-connected to an internal combustion engine via a damper device DA; an output member drive-connected to a wheel; and a rotary electric machine provided on a power transmission path at a side closer to an output member than the damper device DA, wherein the internal combustion engine may be started by the torque of the rotary electric machine. The damper device DA includes a hysteresis torque reducing mechanism HV reducing hysteresis torque in response to a supply hydraulic pressure from a hydraulic supply circuit SC, wherein the supply hydraulic pressure from the hydraulic supply circuit SC after the completion of the start of the internal combustion engine is higher than that at the initiation of the start operation of the internal combustion engine.

Description

  The present invention includes a connecting member that is drivingly connected to an internal combustion engine via a damper device, an output member that is drivingly connected to a wheel, and a rotating electrical machine provided on the output member side of the damper device on a power transmission path. The present invention relates to a hybrid drive device that is configured to be capable of starting an internal combustion engine by torque of a rotating electrical machine.

  As such a hybrid drive device, for example, a device described in Patent Document 1 below is already known. In such a hybrid drive device, the torsional vibration of the internal combustion engine is input to the device while being attenuated by the action of the damper device. At that time, the torsional vibration of the internal combustion engine is attenuated by the hysteresis torque generated by the frictional resistance.

  By the way, the torsional vibration of the internal combustion engine varies in magnitude between the steady operation, the start time, and the stop time. That is, the torque fluctuation of the internal combustion engine during steady operation is relatively small and the torsional vibration is also relatively small. On the other hand, the torque fluctuation of the internal combustion engine at the time of starting and stopping is relatively large and the torsional vibration is also relatively large. At this time, if the magnitude of the hysteresis torque of the damper device is set to be small in accordance with the steady operation, a large torsional vibration at the time of starting and stopping cannot be sufficiently attenuated, and the driver may feel a shock. . On the other hand, if the magnitude of the hysteresis torque of the damper device is set to be large for both starting and stopping, the small torsional vibration during steady operation cannot be sufficiently damped, and the gears of the gears provided in the device will rattle. There is a possibility that sound (rattle) will be generated.

  Therefore, the damper device provided in the hybrid drive device described in Patent Literature 1 switches the magnitude of the hysteresis torque according to the twist angle between the input side rotating member and the output side rotating member member of the damper device. It is configured to be able to. That is, the damper device is configured to apply a small hysteresis torque in a range where the twist angle is equal to or less than a predetermined angle, and to apply a large hysteresis torque in a range where the twist angle exceeds the predetermined angle. Thereby, it is possible to effectively suppress both the generation of rattling noise and the generation of shock according to the magnitude of the twist angle.

  However, in the damper device of the hybrid drive device of Patent Document 1, mechanical hysteresis is used to switch between a small hysteresis torque state and a large hysteresis torque state according to the torsion angle. Therefore, the state before the backlash is always in a small hysteresis torque state, while the backlash is always in a large hysteresis torque state. Therefore, depending on the situation, it cannot be said that there is no possibility of a large hysteresis torque state during steady operation where a small hysteresis torque state is desired. Therefore, it could not be said that there is no possibility of generating a rattling sound due to torsional vibration of the internal combustion engine depending on the situation.

JP 2006-29363 A

  Therefore, it is desired to realize a hybrid drive device that can appropriately suppress the generation of rattling noise during steady operation of the internal combustion engine.

  According to the present invention, a connecting member that is drivingly connected to an internal combustion engine via a damper device, an output member that is drivingly connected to a wheel, and a rotating electrical machine provided on the output member side of the damper device on a power transmission path And the characteristic configuration of the hybrid drive device configured to be able to start the internal combustion engine with the torque of the rotating electrical machine includes: a damper device configured to reduce hysteresis torque in accordance with hydraulic pressure supplied from a hydraulic pressure supply circuit; A torque reduction mechanism is provided, and the hydraulic pressure supplied from the hydraulic pressure supply circuit is configured to be higher than that at the start of the startup operation of the internal combustion engine after the startup of the internal combustion engine is completed.

In the present application, “driving connection” refers to a state where two rotating elements are connected so as to be able to transmit a driving force, and the two rotating elements are connected so as to rotate integrally, or It is used as a concept including a state in which two rotating elements are connected so as to be able to transmit a driving force via one or more transmission members. Examples of such a transmission member include various members that transmit rotation at the same speed or a variable speed, and include, for example, a shaft, a gear mechanism, a belt, a chain, and the like.
The “rotary electric machine” is used as a concept including a motor (electric motor), a generator (generator), and a motor / generator that performs both functions of the motor and the generator as necessary.

  According to the above characteristic configuration, when the internal combustion engine is started by the torque of the rotating electrical machine, the hydraulic pressure is supplied to the damper device from the hydraulic pressure supply circuit so as to be higher after the start is completed than when the start operation of the internal combustion engine is started. Then, the hysteresis torque reduction mechanism reduces the hysteresis torque of the damper device in accordance with the relatively high supply hydraulic pressure after completion of the start of the internal combustion engine. As described above, in the above characteristic configuration, the hysteresis torque of the damper device is switched according to the hydraulic pressure supplied from the hydraulic pressure supply circuit. Therefore, after the start of the internal combustion engine is completed, the twist angle of the damper device is For example, the hysteresis torque can be kept small by a relatively high supply hydraulic pressure. Therefore, it is possible to provide a hybrid drive device that can appropriately suppress the occurrence of rattling noise during steady operation of the internal combustion engine. Moreover, the effect of suppressing the rattling noise during the steady operation of the internal combustion engine can be easily obtained in conjunction with the start of the internal combustion engine.

  Here, the damper device includes an input-side rotating member that is drivingly connected to the internal combustion engine and an output-side rotating member that is drivingly connected to the connecting member, and the hysteresis torque reduction mechanism includes the input-side rotating member and A sliding member that generates a hysteresis torque due to frictional resistance between the output-side rotating member and a supply hydraulic pressure from the hydraulic pressure supply circuit, and the input-side rotating member and the output-side rotating member by the sliding member And a displacement mechanism that changes the relative positional relationship between the input side rotating member and the output side rotating member via the sliding member so as to reduce the frictional resistance between them. .

According to this configuration, the relative positional relationship between the input-side rotating member and the output-side rotating member via the sliding member is changed by the displacement mechanism by the hydraulic pressure supplied from the hydraulic pressure supply circuit, and the friction between them is changed. Resistance can be reduced. Therefore, a mechanism for reducing the hysteresis torque of the damper device according to the hydraulic pressure supplied from the hydraulic pressure supply circuit (hysteresis torque reduction mechanism) can be appropriately realized.
In this configuration, the frictional resistance between the input-side rotating member and the output-side rotating member by the sliding member is relatively low when the hydraulic pressure is not supplied from the hydraulic pressure supply circuit, such as before the start operation of the internal combustion engine is started. large. Therefore, during the starting operation of the internal combustion engine, the hysteresis torque can be maintained in a relatively large state without depending on the twist angle of the damper device. Therefore, it is possible to effectively suppress the occurrence of shock during the starting operation of the internal combustion engine.

  The displacement mechanism includes a guide portion that guides the output-side rotating member so as to be movable in the axial direction, and a biasing member that biases the output-side rotating member so as to press the output-side rotating member toward the sliding member in the axial direction. And a displacement mechanism hydraulic fluid chamber formed between the coupling member and the output side rotation member and communicating with the hydraulic pressure supply circuit, and according to the hydraulic pressure supplied to the displacement mechanism hydraulic fluid chamber, It is preferable that the output-side rotating member moves in the axial direction so as to be separated from the input-side rotating member and the sliding member against the urging force of the urging member.

According to this configuration, the change in the relative positional relationship in the axial direction between the input-side rotating member and the output-side rotating member of the damper device can be guided by the guide portion included in the displacement mechanism. Then, in cooperation with the guide portion, the biasing member, and the hydraulic pressure supplied to the displacement mechanism hydraulic oil chamber, the output side rotation with respect to the input side rotation member and the sliding member is performed within a predetermined movable range in the axial direction. The members can be moved relative to each other freely.
Further, in this configuration, in a state where the hydraulic pressure is not supplied from the hydraulic pressure supply circuit, the output side rotating member is pressed toward the sliding member side in the axial direction by the biasing member. Therefore, a frictional resistance caused by the sliding member is reliably generated between the input side rotating member and the output side rotating member, and a state where the hysteresis torque is large can be appropriately realized. On the other hand, in a state where the hydraulic pressure is supplied from the hydraulic pressure supply circuit, the output side rotating member moves in the axial direction so as to be separated from the input side rotating member and the sliding member against the biasing force of the biasing member. Therefore, the frictional resistance by the sliding member between the input side rotating member and the output side rotating member can be reduced, and a state where the hysteresis torque is small can be appropriately realized.

  Further, it is preferable that the connecting member and the output side rotating member are splined in the displacement mechanism hydraulic oil chamber.

  According to this configuration, the spline connecting portion appropriately configures the guide portion that guides the output-side rotating member to be movable in the axial direction while enabling transmission of the driving force between the connecting member and the output-side rotating member. can do. Further, in this configuration, by providing such a spline connecting portion in the displacement mechanism operating oil chamber, the spline connecting portion can be lubricated using oil supplied to the displacement mechanism operating oil chamber. Therefore, wear of the spline connecting portion can be suppressed.

  The damper device includes an input side rotating member that is drivingly connected to the internal combustion engine and an output side rotating member that is drivingly connected to the connecting member, and the hysteresis torque reduction mechanism includes the input side rotating member and the input side rotating member. A first sliding member provided between the output side rotating member and generating a frictional resistance based on a first friction coefficient with the output side rotating member; the input side rotating member; and the output side rotating member; A second sliding member that is provided between the output side rotating member and generates a frictional resistance based on a second friction coefficient smaller than the first friction coefficient, and the connecting member and the output side rotating member. A spline connecting portion that guides the output-side rotating member to be movable in the axial direction with respect to the connecting member, and presses the output-side rotating member in the axial direction toward the first sliding member. Energize as An urging member, and a displacement mechanism hydraulic fluid chamber communicating with the hydraulic pressure supply circuit, the first sliding member, the output-side rotating member, the second sliding member, and the urging member, An axial direction arranged in this order in the axial direction, wherein the axial end of the connecting member on the second sliding member side is formed on the output side rotating member, and the second sliding member side is closed in the axial direction It is preferable that the displacement mechanism hydraulic oil chamber is formed in a gap between the surface of the axial end and the surface of the axial hole while being inserted into the hole.

According to this configuration, the spline connecting portion enables transmission of the driving force between the connecting member and the output side rotating member, while the relative position in the axial direction between the input side rotating member and the output side rotating member of the damper device. The relationship can be configured to be changeable. Further, since the displacement mechanism hydraulic oil chamber is formed between the connecting member in the state where the axial end of the connecting member is inserted into the axial hole of the output side rotating member, hydraulic pressure is supplied to the displacement mechanism hydraulic oil chamber. In this case, the closing surface on the second sliding member side of the output side rotating member functions as a pressure receiving surface, and the output side rotating member can be moved along the axial direction to the second sliding member side.
In this configuration, when the hydraulic pressure is not supplied from the hydraulic pressure supply circuit, the second sliding member is pressed in the axial direction by the biasing member toward the output-side rotating member, and the output-side rotating member is in the axial direction. Is pressed toward the first sliding member. On the other hand, in a state where the hydraulic pressure is supplied from the hydraulic pressure supply circuit, the output-side rotating member is separated from the first sliding member against the urging force of the urging member so as to be close to the second sliding member side. Move in the direction. At this time, since the second friction coefficient is smaller than the first friction coefficient, the friction resistance based on the first friction coefficient and the friction resistance based on the second friction coefficient in accordance with the hydraulic pressure supply from the hydraulic pressure supply circuit. And the sum becomes smaller. Therefore, it is possible to appropriately realize a mechanism (hysteresis torque reduction mechanism) that reduces the hysteresis torque generated by the frictional resistance in accordance with the hydraulic pressure supplied from the hydraulic pressure supply circuit.

  The hydraulic pressure supply circuit is supplied with hydraulic pressure generated by an oil pump that rotates at a speed proportional to the rotational speed of the connecting member, or a friction engagement device that is completely engaged after the start of the internal combustion engine. The hydraulic pressure is preferably supplied.

According to the oil pump that rotates at a speed proportional to the rotation speed of the connecting member, the hydraulic pressure is not obtained when the internal combustion engine is stopped before starting the start operation, and the hydraulic pressure is sufficiently large during the steady operation after the start of the internal combustion engine is completed. Is obtained. Further, for example, in the case where a friction engagement device that operates according to hydraulic pressure and can switch between transmission and interruption of driving force is provided between the internal combustion engine and the rotary electric machine, the friction engagement device includes the rotary electric machine. The hydraulic pressure is supplied at the time of starting the internal combustion engine by torque, and the supplied hydraulic pressure is made large enough to fully engage the friction engagement device after the completion of the startup.
Therefore, the hydraulic pressure generated by the oil pump rotating at a speed proportional to the rotational speed of the connecting member as described above, or the hydraulic pressure supplied to the friction engagement device that is completely engaged after the start of the internal combustion engine, is hydraulic. By using the hydraulic pressure supplied from the supply circuit, it is possible to appropriately reduce the hysteresis torque after completion of the start of the internal combustion engine, and to effectively suppress the generation of rattling noise during the steady operation of the internal combustion engine.

  Specifically, the configuration described so far includes a differential gear device having three rotating elements which are a first rotating element, a second rotating element, and a third rotating element in the order of rotational speed, The rotating electrical machine is drivingly connected to the first rotating element of the gear device, the connecting member is drivingly connected to the second rotating element, the output member is drivingly connected to the third rotating element, and the hydraulic pressure supply circuit is connected to the first rotating element The present invention can be suitably applied to a hybrid drive device configured as a supply circuit for hydraulic pressure generated by an oil pump that rotates at a speed proportional to the rotational speed of the member.

  According to this configuration, a so-called split type hybrid drive device can be appropriately realized. According to the oil pump that rotates at a speed proportional to the rotation speed of the connecting member, the hydraulic pressure is not obtained when the internal combustion engine is stopped, and a sufficiently large hydraulic pressure is obtained during the steady operation after the start of the internal combustion engine. It becomes a state. Therefore, by forming a hydraulic pressure supply circuit as the hydraulic pressure supply circuit thus obtained, the relatively large hysteresis torque when the internal combustion engine is stopped can be appropriately reduced after the start of the internal combustion engine is completed. Therefore, in the split type hybrid drive device, it is possible to effectively suppress the occurrence of rattling noise during the steady operation of the internal combustion engine.

  Alternatively, a friction engagement device is provided between the internal combustion engine and the rotating electrical machine so as to switch between transmission and interruption of driving force by operating according to oil pressure, and the hydraulic pressure supply circuit is connected to the friction engagement device. It is also suitable to be applied to a hybrid drive device having a structure formed by branching from the hydraulic pressure supply circuit.

  According to this configuration, a so-called one-motor parallel type hybrid drive device can be appropriately realized. The hydraulic pressure supply circuit to the friction engagement device is not supplied with a hydraulic pressure so as to disconnect the internal combustion engine from the rotating electrical machine when the internal combustion engine is stopped. When the combined device is in a fully engaged state, a hydraulic pressure large enough to transmit the torque of the internal combustion engine to the wheel side is supplied. Therefore, by forming a hydraulic pressure supply circuit by branching from the hydraulic pressure supply circuit to the friction engagement device to which such hydraulic pressure is supplied, a relatively large hysteresis torque is generated when the internal combustion engine is stopped. It can be reduced appropriately after the start is completed. Therefore, in the one-motor parallel type hybrid drive device, it is possible to effectively suppress the occurrence of rattling noise during the steady operation of the internal combustion engine.

It is a skeleton figure of the hybrid drive device concerning a first embodiment. It is a fragmentary sectional view of the hybrid drive device concerning a first embodiment. It is a fragmentary sectional view of the hybrid drive device concerning a first embodiment. It is a time chart which shows the operation state of each part at the time of starting operation | movement of an internal combustion engine, and steady operation. It is a skeleton figure of the hybrid drive device concerning a second embodiment. It is a fragmentary sectional view of the hybrid drive device concerning a second embodiment.

1. First Embodiment A first embodiment of a hybrid drive apparatus according to the present invention will be described with reference to the drawings. FIG. 1 is a skeleton diagram showing the configuration of the hybrid drive apparatus H according to the present embodiment. The hybrid drive device H is a drive device for a hybrid vehicle that uses one or both of the internal combustion engine E and the rotating electrical machines MG1 and MG2 as a drive force source of the vehicle. The hybrid drive device H is configured as a so-called two-motor split type hybrid drive device.

  As shown in FIG. 1, the hybrid drive device H according to the present embodiment includes an input shaft I that is drive-coupled to the internal combustion engine E via a damper device DA, an output gear O that is drive-coupled to the wheels W, and power. And a first rotating electrical machine MG1 provided on the output gear O side of the damper device DA on the transmission path. The hybrid drive device H is configured to be able to start the internal combustion engine E by the torque of the first rotating electrical machine MG1. In such a configuration, the hybrid drive device H according to the present embodiment includes a hysteresis torque variable mechanism HV in which the damper device DA reduces the hysteresis torque according to the hydraulic pressure supplied from the hydraulic pressure supply circuit SC (see FIG. 2). ), The hydraulic pressure supplied from the hydraulic pressure supply circuit SC is configured to be higher after the start of the internal combustion engine E than when the start operation of the internal combustion engine E is started (see FIG. 4). Thereby, the hybrid drive device H that can appropriately suppress the generation of rattling noise during the steady operation of the internal combustion engine E is realized. Hereinafter, the hybrid drive device H according to the present embodiment will be described in detail.

1-1. Overall Configuration of Hybrid Drive Device First, the overall configuration of the hybrid drive device H will be described. As shown in FIG. 1, the hybrid drive device H includes a damper device DA, an input shaft I that is drivingly connected to the internal combustion engine E via the damper device DA, a first rotating electrical machine MG1, and a second rotating electrical machine MG2. A differential gear device DG, an output gear O connected to the wheels W, a counter gear mechanism C, and an output differential gear device DF. Each of these components is housed in a case 2 (see FIG. 2) that is fixed to the vehicle body. The damper device DA, the first rotating electrical machine MG1, the differential gear device DG, and the output gear O are arranged coaxially with the input shaft I.

  The input shaft I is drivingly connected to the internal combustion engine E. Here, the internal combustion engine E is a device that extracts power by being driven by combustion of fuel inside the engine. For example, various known engines such as a gasoline engine and a diesel engine can be used. In this example, the input shaft I is drivably coupled to the output rotating shaft 5 (see FIG. 2) such as a crankshaft of the internal combustion engine E via the damper device DA. The damper device DA is a device that transmits the rotation of the output rotary shaft 5 to the input shaft I while attenuating torsional vibration of the output rotary shaft 5 of the internal combustion engine E. Details of the damper device DA will be described later. It is also preferable that the input shaft I is drivingly connected to the output rotating shaft 5 of the internal combustion engine E via another member such as a clutch in addition to the damper device DA. In the present embodiment, the input shaft I corresponds to the “connecting member” in the present invention.

  The first rotating electrical machine MG1 includes a first stator St1 fixed to the case 2 and a first rotor Ro1 that is rotatably supported on the radially inner side of the first stator St1. The first rotor Ro1 of the first rotating electrical machine MG1 is drivingly connected so as to rotate integrally with the sun gear S of the differential gear device DG. The second rotating electrical machine MG2 includes a second stator St2 fixed to the case 2 and a second rotor Ro2 that is rotatably supported on the radially inner side of the second stator St2. The second rotor Ro2 of the second rotating electrical machine MG2 is drivably coupled to the output differential gear device DF via the counter gear mechanism C. The first rotating electrical machine MG1 and the second rotating electrical machine MG2 are each electrically connected to a battery (not shown) as a power storage device. Note that the battery is an example of a power storage device, and another power storage device such as a capacitor may be used, or a plurality of types of power storage devices may be used in combination. Further, the battery can be configured to be rechargeable by an external power source such as a household power source.

  Each of the first rotating electrical machine MG1 and the second rotating electrical machine MG2 functions as a motor (electric motor) that generates power by receiving power supply, and a generator (generator) that generates power by receiving power supply. It is possible to fulfill the function. Here, when the first rotating electrical machine MG1 and the second rotating electrical machine MG2 function as generators, they generate power by the torque of the internal combustion engine E or the inertial force of the vehicle, charge the battery, or function as a motor. Electric power for driving the rotating electrical machines MG1, MG2 is supplied. On the other hand, when the first rotating electrical machine MG1 and the second rotating electrical machine MG2 function as motors, the battery is charged or supplied with the electric power generated by the other rotating electrical machines MG1 and MG2 functioning as generators. Do power. In the present embodiment, the first rotating electrical machine MG1 corresponds to the “rotating electrical machine” in the present invention.

  As shown in FIG. 1, the differential gear device DG is configured by a single pinion type planetary gear mechanism arranged coaxially with the input shaft I. That is, the differential gear device DG includes, as rotating elements, a carrier CA that supports a plurality of pinion gears, and a sun gear S and a ring gear R that mesh with the pinion gears. The sun gear S is drivingly coupled so as to rotate integrally with the first rotor Ro1 of the first rotating electrical machine MG1. The carrier CA is drivingly connected so as to rotate integrally with the input shaft I. The ring gear R is drivingly connected so as to rotate integrally with an output gear O formed on the radially outer side of the input shaft I between the differential gear device DG and the damper device DA in the axial direction. These three rotating elements are a sun gear S, a carrier CA, and a ring gear R in order of rotational speed. In the present embodiment, the sun gear S, the carrier CA, and the ring gear R correspond to the “first rotating element”, “second rotating element”, and “third rotating element” in the present invention, respectively.

  The differential gear device DG functions as a power distribution device that distributes the torque of the internal combustion engine E input via the input shaft I to the first rotary electric machine MG1 and the output gear O. Further, the rotation of the input shaft I is controlled by controlling the rotational speed and torque of the first rotating electrical machine MG1 in a state where the torque of the input shaft I (internal combustion engine E) is inputted to the carrier CA of the differential gear device DG. The speed can be changed steplessly and transmitted to the output gear O. Therefore, the input step I, the differential gear device DG, and the first rotating electrical machine MG1 cooperate to constitute an electric continuously variable transmission mechanism.

  In the present embodiment, the input shaft I rotates integrally with a pump drive gear 38 formed on the radially outer side of the first rotor shaft 36 between the differential gear device DG and the first rotating electrical machine MG1 in the axial direction. So that the drive is connected. The pump drive gear 38 meshes with a driven gear 39 that is drivingly connected to the oil pump MP. Here, the oil pump MP is an inscribed gear pump having an inner rotor and an outer rotor. The inner rotor of the oil pump MP is drivingly connected so as to rotate integrally with the driven gear 39. Therefore, the inner rotor of the oil pump MP rotates at a speed proportional to the rotational speed of the input shaft I according to the gear ratio between the pump drive gear 38 and the driven gear 39. The oil pump MP cools the rotary electric machines MG1 and MG2 or generates a hydraulic pressure for supplying oil to gears and bearings provided in each part of the hybrid drive device H. The oil discharged by the oil pump MP is supplied to each part of the hybrid drive device H via a hydraulic pressure supply circuit SC including an oil passage formed in the case 2 of the hybrid drive device H, various rotating shafts, and the like. Note that it is also preferable to use a circumscribed gear pump, vane pump, or the like as the oil pump MP.

  An output gear O as an output rotation element of the differential gear device DG is drivingly connected to an output differential gear device DF via a counter gear mechanism C. Further, as described above, the second rotor Ro2 of the second rotating electrical machine MG2 is also drivingly connected to the output differential gear device DF via the counter gear mechanism C. Thus, in the present embodiment, a part of the torque of the input shaft I (internal combustion engine E) distributed to the output gear O by the differential gear device DG and the output torque of the second rotating electrical machine MG2 are combined and output. Is transmitted to the differential gear unit DF. The output differential gear device DF is drivingly connected to the wheels W, and distributes and transmits rotation and torque input to the output differential gear device DF to the left and right wheels W. In the present embodiment, the output gear O corresponds to the “output member” in the present invention.

  The hybrid drive device H according to this embodiment includes a plurality of travel modes including a split mode and an electric travel mode that can be switched. Here, in the split mode, as described above, the torque of the input shaft I (internal combustion engine E) is distributed to the first rotating electrical machine MG1 and the output gear O, and the torque distributed to the output gear O is used. In this mode, the vehicle is driven. In the split mode, the second rotating electrical machine MG2 outputs a shortage of torque with respect to the required driving force of the vehicle as needed to assist the torque distributed to the output gear O. The electric travel mode is a mode in which the vehicle is driven by the torque of the second rotating electrical machine MG2 while the internal combustion engine E is stopped. Note that the split mode and the electric travel mode are merely examples, and other than these, for example, a parallel mode or the like may be switchable. The parallel mode is a mode in which the vehicle is driven by the torque of the internal combustion engine E and the second rotating electrical machine MG2 while the first rotating electrical machine MG1 is stopped. When the parallel mode is realized, the brake 37 is engaged and the rotation of the first rotor Ro1 and the sun gear S is stopped. The driving mode realized in the hybrid drive device H is appropriately selected according to the actual required driving force of the vehicle, the vehicle speed, the remaining battery level, and the like based on a control map (not shown).

  In this example, as an example, in a state where the required driving force of the vehicle is relatively large and the vehicle speed is low, such as when the vehicle starts, the electric travel mode is selected on the condition that the remaining battery level is sufficiently secured. In this state, when the required driving force and the vehicle speed of the vehicle further increase or when the remaining battery level becomes a predetermined value or less, the internal combustion engine E is started and switched to the split mode. The starting control of the internal combustion engine E is performed by the first rotating electrical machine MG1 that is drivingly connected to the sun gear S in a state where the running torque from the wheels W is transmitted to the output gear O that rotates integrally with the ring gear R of the differential gear device DG. This is done by increasing the rotational speed and torque. That is, the rotational speed of the internal combustion engine E is increased via the input shaft I that is drivingly connected to the carrier CA, and after reaching a predetermined ignition start rotational speed, fuel injection is started and spark ignition is performed to start the internal combustion engine E. Start. Thus, the hybrid drive device H according to the present embodiment is configured to be able to start the internal combustion engine E by the torque of the first rotating electrical machine MG1. When switching from the split mode to the electric travel mode, the internal combustion engine E is stopped by stopping the fuel supply.

  As described above, in the present embodiment, the hydraulic pressure supply circuit SC is formed as a hydraulic pressure supply circuit generated by the oil pump MP that rotates at a speed proportional to the rotational speed of the input shaft I (internal combustion engine E). That is, the hydraulic pressure generated by the oil pump MP that rotates at a speed proportional to the rotational speed of the input shaft I (internal combustion engine E) is supplied to the hydraulic pressure supply circuit SC. Therefore, for example, in the above example, while the vehicle is traveling in the electric travel mode in which the internal combustion engine E is stopped, the hydraulic pressure supplied from the hydraulic pressure supply circuit SC is basically zero. On the other hand, when the input shaft I (internal combustion engine E) rotates at a predetermined rotational speed or higher after the start of the internal combustion engine E is completed after switching to the split mode, the hydraulic pressure supplied from the hydraulic pressure supply circuit SC rises to a predetermined hydraulic pressure or higher. . Thus, the hydraulic pressure supplied from the hydraulic pressure supply circuit SC is higher after the completion of the start of the internal combustion engine E than when the start operation of the internal combustion engine E is started.

1-2. Configuration of Damper Device Next, the configuration of the damper device DA provided in the hybrid drive device H according to the present embodiment will be described. As shown in FIGS. 2 and 3, the damper device DA according to this embodiment includes an input side rotating member 11, an output side rotating member 12, a coil spring 16, a first sliding member 21, and a second sliding member. The moving member 22 is provided as a main component. In the following description, the axial direction, the radial direction, and the circumferential direction are defined on the basis of the damper device DA arranged coaxially and the rotational axis X of the input shaft I. Further, as viewed from the damper device DA, the internal combustion engine E side (the right side in FIG. 2) in the axial direction is one axial direction, and the end support wall 3 side (the left side in FIG. 2) of the case 2 is the other axial side. explain.

  The input side rotation member 11 is configured to have a pair of disk-shaped members and is drivingly connected to the internal combustion engine E. In this example, as shown in FIG. 2, the input side rotation member 11 has a pair of first input side rotation member 11a and second input side rotation member 11b. In the following, the term “input side rotating member 11” refers to the first input side rotating member 11a and the second input side rotating member 11b in a comprehensive manner. The input side rotating member 11 is formed with a central hole on the radially inner side, and is disposed on the radially outer side of the cylindrical portion 13 of the output side rotating member 12. The first input side rotating member 11 a and the second input side rotating member 11 b are disposed on the opposite side in the axial direction with respect to the disk portion 14 of the output side rotating member 12. That is, the first input side rotating member 11 a is disposed on the other side in the axial direction with respect to the disc portion 14, and the second input side rotating member 11 b is disposed on the one side in the axial direction with respect to the disc portion 14. The first input side rotating member 11a and the second input side rotating member 11b are fastened to each other by a fastening member such as a rivet at the radially outer end. The input side rotating member 11 is drivingly connected so as to rotate integrally with the output rotating shaft 5 of the internal combustion engine E via the connecting portion 7 and the drive plate 6.

  The output-side rotating member 12 includes a cylindrical cylindrical portion 13 that extends in the axial direction and a disk-shaped disc portion 14 that extends radially outward from the cylindrical portion 13 and is connected to the input shaft I for driving. Has been. The disc part 14 is formed integrally with the cylindrical part 13 at the axially central part of the cylindrical part 13. The cylindrical portion 13 is disposed on the radially inner side of the input side rotating member 11, and the disc portion 14 is disposed between the first input side rotating member 11a and the second input side rotating member 11b in the axial direction. An axial hole 32 that opens to the other axial side is formed in the inner peripheral portion of the cylindrical portion 13. The axial center of the axial hole 32 coincides with the rotational axis X of the input shaft I. The axial hole 32 is formed by closing one side in the axial direction which is the second input side rotating member 11b side in the axial direction. That is, the axial hole 32 has an opening that opens to the other axial side and an axial bottom surface 32b that closes the other axial side. Spline teeth 32 a are formed on the inner peripheral surface of the axial hole 32. The spline tooth portion 32 a is in spline engagement with a spline tooth portion 31 a formed on the outer peripheral surface of the axial end portion 31 of the input shaft I. Therefore, in this embodiment, the output side rotation member 12 is spline-connected so as to rotate integrally with the input shaft I in the axial hole portion 32.

  The input side rotating member 11 and the output side rotating member 12 are configured to be relatively rotatable in the circumferential direction within a predetermined range. Between the input-side rotating member 11 and the output-side rotating member 12, a plurality of coil springs 16 are uniformly distributed along the circumferential direction. Transmission of the driving force between the input side rotating member 11 and the output side rotating member 12 is performed via a coil spring 16. The coil spring 16 is a vibration-absorbing elastic member for attenuating torsional vibration of the output rotating shaft 5 of the internal combustion engine E in cooperation with the first sliding member 21 and the second sliding member 22. It performs a central function.

  The first sliding member 21 is a disk-like member provided between the input side rotating member 11 and the output side rotating member 12. In the present example, the first sliding member 21 is provided between the first input side rotating member 11 a and the disk portion 14 of the output side rotating member 12 in the axial direction. The first sliding member 21 is positioned in the radial direction by bringing the outer peripheral surface of the axial cylindrical projection 21b formed radially inward into contact with the inner peripheral surface of the first input side rotating member 11a. Has been made. The first sliding member 21 has axial projections 21c formed at a plurality of locations in the circumferential direction so as to protrude toward the other side in the axial direction. The first sliding member 21 is in a state in which relative rotation with respect to the first input-side rotating member 11a is restricted by fitting the protrusion 21c into a predetermined hole formed in the first input rotating member 11a. It is fixed with. The relative movement in the axial direction of the first sliding member 21 with respect to the first input rotating member 11a is allowed to some extent. In the present embodiment, the first sliding member 21 corresponds to the “sliding member” in the present invention.

  The second sliding member 22 is a disk-like member provided between the input side rotating member 11 and the output side rotating member 12. In this example, the second sliding member 22 is provided between the second input side rotating member 11 b and the disk portion 14 of the output side rotating member 12 in the axial direction. The second sliding member 22 is brought into contact with the outer peripheral surface of the cylindrical portion 13 of the output side rotation member 12 by bringing the inner peripheral surface of the axial cylindrical projection 22b formed radially inward into contact with the outer peripheral surface. Positioning has been made. The second sliding member 22 has axial projections (not shown) formed so as to project toward one side in the axial direction at a plurality of locations in the circumferential direction. By fitting this protrusion into a predetermined hole formed in the second input rotating member 11b, the second sliding member 22 is in a state in which relative rotation is restricted with respect to the second input side rotating member 11b. It is fixed. The relative movement of the second sliding member 22 in the axial direction with respect to the second input rotating member 11b is allowed to some extent.

  Further, an urging member 24 is disposed between the second sliding member 22 and the second input side rotating member 11b in the axial direction. In this example, a disc spring is used as such a biasing member 24. The biasing member 24 biases the second sliding member 22 so as to press it toward the output-side rotating member 12 while the reaction force is supported on one side in the axial direction by the second input-side rotating member 11b. Yes. As a result, the second sliding surface 22 a on the other axial side of the second sliding member 22 is in contact with the surface on the one axial side of the disk portion 14 of the output side rotating member 12. In the present embodiment, the first sliding member 21, the disk portion 14, the second sliding member 22, and the biasing member 24 of the output side rotating member 12 are directed from the other side in the axial direction to one side in the axial direction. Are arranged in this order. Therefore, the urging member 24 further urges the output-side rotating member 12 via the second sliding member 22 so as to press the other side in the axial direction that is the first sliding member 21 side. As a result, the first sliding surface 21 a on the one side in the axial direction of the first sliding member 21 is in contact with the surface on the other side in the axial direction of the disk portion 14 of the output side rotating member 12.

  When the input-side rotating member 11 and the output-side rotating member 12 rotate relative to each other, the first sliding member 21 generates a hysteresis torque due to frictional resistance between the first sliding member 21 and the output-side rotating member 12. Similarly, the second sliding member 22 generates a hysteresis torque due to frictional resistance with the output side rotating member 12. Here, the hysteresis torque is torque generated by frictional resistance to attenuate vibrations. In this embodiment, the dynamic friction coefficient between the first sliding member 21 and the output side rotating member 12 is the first friction coefficient μ1, and the dynamic friction coefficient between the second sliding member 22 and the output side rotating member 12 is The second friction coefficient is μ2. In the present embodiment, the material constituting each of the first sliding surface 21a and the second sliding surface 22a is such that the second friction coefficient μ2 has a value smaller than the first friction coefficient μ1 (μ2 <μ1). Selected.

  In this embodiment, a friction washer is used as the first sliding member 21 having such a first sliding surface 21a. Such a friction washer is formed by, for example, mixing organic fibers, a resin, rubber, a friction improver, and the like and performing heat molding. You may further contain an inorganic fiber, a solid lubricant, etc. as needed. In the present embodiment, the surface on one side in the axial direction of the friction washer constituting the first sliding member 21 is the first sliding surface 21a as it is. The same applies to the second sliding member 22 having the second sliding surface 22a, and the surface on the other side in the axial direction of the friction washer constituting the second sliding member 22 becomes the second sliding surface 22a as it is. Yes.

  In the present embodiment, the hysteresis torque due to the friction resistance based on the first friction coefficient μ1 is referred to as a first hysteresis torque H1, and the hysteresis torque due to the friction resistance based on the second friction coefficient μ2 is referred to as a second hysteresis torque H2. In the present embodiment, the second friction coefficient μ2 is set to a value smaller than the first friction coefficient μ1 (μ2 <μ1), so that the pressing force acting on the sliding surface is constant (equal). In comparison, the second hysteresis torque H2 is smaller than the first hysteresis torque H1 (H2 <H1). In addition, the surface state of the surface of the axial direction both sides of the disc part 14 of the output side rotation member 12 shall be substantially the same.

  The damper device DA according to the present embodiment includes a hysteresis torque variable mechanism HV that increases or decreases the overall hysteresis torque by appropriately switching the magnitudes of the first hysteresis torque H1 and the second hysteresis torque H2 that are generated. Yes. This hysteresis torque variable mechanism HV is not a mechanism using mechanical backlash as provided in the conventional apparatus, but a hydraulically driven hysteresis that increases or decreases the hysteresis torque in accordance with the hydraulic pressure supplied from the hydraulic pressure supply circuit SC. It is a torque variable mechanism HV. Therefore, hereinafter, the hysteresis torque variable mechanism HV of the damper device DA according to the present embodiment will be described in detail.

1-3. Configuration of Hysteresis Torque Variable Mechanism The hysteresis torque variable mechanism HV according to this embodiment includes the first sliding member 21, the second sliding member 22, the urging member 24, and the spline connecting portion (spline tooth portion 31a, 32a) is further provided with a displacement mechanism hydraulic oil chamber R1. Together, these components constitute a hysteresis torque variable mechanism HV that increases or decreases the hysteresis torque in accordance with the hydraulic pressure supplied from the hydraulic pressure supply circuit SC.

  The displacement mechanism hydraulic oil chamber R <b> 1 is formed between the input shaft I and the output side rotating member 12. In the present embodiment, an axial end 31 on one axial side that is the second sliding member 22 side of the input shaft I is formed on the inner peripheral portion of the cylindrical portion 13, and the first sliding member 21 side. It is inserted into an axial hole 32 that opens to the other axial side. The axial hole 32 is formed by closing one axial side with an axial bottom surface 32b. Further, in the vicinity of the other end of the cylindrical portion 13 in the axial direction, a seal member 34 such as an O-ring is provided between the outer peripheral surface of the axial end portion 31 of the input shaft I and the inner peripheral surface of the axial hole portion 32. Is arranged. The space defined by the surface of the axial end portion 31 (outer peripheral surface and one axial end surface), the surface of the axial hole portion 32 (inner peripheral surface and axial bottom surface 32b), and the seal member 34 is a liquid-tight space. This space is a displacement mechanism hydraulic oil chamber R1. In other words, the displacement mechanism hydraulic oil chamber R <b> 1 is formed in the gap between the surface of the axial end portion 31 and the surface of the axial hole portion 32.

  In the present embodiment, the input shaft I and the output side rotating member 12 are spline connected and drivingly connected in the displacement mechanism hydraulic oil chamber R1. That is, in the displacement mechanism hydraulic oil chamber R1, a spline tooth portion 31a formed on the outer peripheral surface of the axial end portion 31 of the input shaft I and a spline tooth portion 32a formed on the inner peripheral surface of the axial hole portion 32. Are in spline engagement. In the present embodiment, such spline teeth 31a and 32a are provided in the displacement mechanism hydraulic oil chamber R1, so that the oil supplied to the displacement mechanism hydraulic oil chamber R1 is used to make the spline teeth 31a. , 32a is lubricated. Therefore, it is possible to suppress wear of the spline tooth portions 31a and 32a. The spline tooth portions 31a and 32a are each formed to have a shape extending in the axial direction, and are relatively movable along the axial direction. Therefore, these spline tooth portions 31a and 32a constituting the spline connecting portion also function as a “guide portion GP” that guides the output side rotary member 12 so as to be movable in the axial direction with respect to the input shaft I. In the present embodiment, the spline connecting portion (31a, 32a) as the guide portion GP, the urging member 24, and the displacement mechanism hydraulic oil chamber R1 cooperate to constitute the “displacement mechanism DM” in the present invention. ing.

  Further, the displacement mechanism hydraulic oil chamber R1 communicates with the hydraulic pressure supply circuit SC. In the present embodiment, the hydraulic pressure supply circuit SC has an in-shaft oil passage L1 formed in the inner periphery of the input shaft I as a part thereof. The in-shaft oil passage L <b> 1 extends in the input shaft I in the axial direction and opens on the end surface on one axial side of the input shaft I. Thereby, the displacement mechanism hydraulic oil chamber R1 communicates with the hydraulic pressure supply circuit SC through the opening. Oil discharged from an oil pump MP that rotates at a speed proportional to the rotational speed of the input shaft I (internal combustion engine E) is supplied to the hydraulic pressure supply circuit SC. Therefore, when the internal combustion engine E is stopped, the hydraulic pressure supplied from the hydraulic pressure supply circuit SC is basically zero. On the other hand, when the input shaft I (internal combustion engine E) rotates at a predetermined rotational speed or higher after the start of the internal combustion engine E is completed, the hydraulic pressure supplied from the hydraulic pressure supply circuit SC rises to a predetermined hydraulic pressure or higher. Thus, in the present embodiment, the hydraulic pressure that rises from zero in the stopped state to a predetermined hydraulic pressure or higher in the steady operation is basically supplied to the displacement mechanism hydraulic oil chamber R1 in accordance with the driving state of the internal combustion engine E. The

  The predetermined hydraulic pressure supplied to the displacement mechanism hydraulic oil chamber R1 acts on the axial bottom surface 32b of the axial hole portion 32 and tries to move the entire output side rotating member 12 to one side in the axial direction. On the other hand, the urging member 24 tries to move the entire output side rotating member 12 to the other side in the axial direction via the second sliding member 22. In the hysteresis torque variable mechanism HV according to the present embodiment, the magnitude relationship between the magnitude of the hydraulic pressure supplied to the displacement mechanism hydraulic chamber R1 and the magnitude of the biasing force of the biasing member 24 in conjunction with the driving state of the internal combustion engine E. By switching, the magnitude of hysteresis torque is switched.

  In a state where the internal combustion engine E is stopped and the hydraulic pressure supplied from the hydraulic pressure supply circuit SC is zero, the biasing force by the biasing member 24 is superior to the hydraulic pressure supplied to the displacement mechanism hydraulic oil chamber R1. Further, even after the start of the engine, when the rotational speed of the internal combustion engine E is relatively low and the hydraulic pressure supplied from the hydraulic pressure supply circuit SC is also relatively low, the hydraulic pressure supplied to the displacement mechanism hydraulic oil chamber R1 is reduced. Therefore, the urging force by the urging member 24 is dominant. In these cases, as shown in FIG. 2, both the first sliding member 21 and the second sliding member 22 are pressed toward the output-side rotating member 12 by the urging force of the urging member 24, and a large first Hysteresis torque H1 and second hysteresis torque H2 are generated. Therefore, the hysteresis torque as a whole of the damper device DA is large (here, this is referred to as a large hysteresis torque Hh).

  When the hydraulic pressure supplied from the hydraulic pressure supply circuit SC is relatively low (the first reference hydraulic pressure P1 or lower in FIG. 4) (hereinafter referred to as “low pressure supply state”), the hysteresis torque of the damper device DA is large (high). Hysteresis torque Hh) is maintained. In the present embodiment, such a first reference hydraulic pressure P1 is set to a value greater than the rotational speed (indicated as Nr in FIG. 4) in the resonance region when the internal combustion engine E is started and stopped. It is set as a hydraulic pressure corresponding to the rotational speed N1. Thereby, in this embodiment, when the internal combustion engine E passes through the resonance region when starting and stopping, the hysteresis torque of the damper device DA is maintained in a large state (large hysteresis torque Hh). Therefore, it is possible to effectively attenuate the large torsional vibration of the internal combustion engine E when passing through the resonance region without depending on the relative rotation angle between the input side rotating member 11 and the output side rotating member 12 of the damper device DA. it can. Therefore, it is possible to effectively suppress the occurrence of shock during the starting operation of the internal combustion engine E.

  On the other hand, when the supply oil pressure from the oil pressure supply circuit SC rises to a predetermined oil pressure during the steady operation of the internal combustion engine E, the oil pressure supplied to the displacement mechanism hydraulic oil chamber R1 is superior to the urging force of the urging member 24. In this case, the relative positional relationship between the input side rotating member 11 and the output side rotating member 12 is changed by the supply hydraulic pressure supplied from the hydraulic pressure supply circuit SC to the displacement mechanism hydraulic oil chamber R1. More specifically, as shown in FIG. 3, the output-side rotating member 12 is separated from the first input-side rotating member 11 a and the first sliding member 21 against the urging force of the urging member 24. Move in one direction. Thereby, compared with the case of a low pressure supply state, the surface pressure between the 1st sliding member 21 and the output side rotation member 12 falls significantly. Therefore, the frictional resistance generated by the first sliding member 21 between the first input side rotating member 11a and the output side rotating member 12 and the accompanying first hysteresis torque H1 are larger than those in the low pressure supply state. descend.

  At this time, the output-side rotating member 12 has the second sliding member 22, the urging member 24, and the second input-side rotating member by the supply hydraulic pressure supplied from the hydraulic pressure supply circuit SC to the displacement mechanism hydraulic oil chamber R1. It moves to one side in the axial direction so as to be close to 11b. Thereby, the surface pressure between the 2nd sliding member 22 and the output side rotation member 12 rises compared with the case of a low pressure supply state. Therefore, the second hysteresis torque H2 generated between the second input side rotating member 11b and the output side rotating member 12 by the second sliding member 22 increases as compared with the low pressure supply state. However, in the present embodiment, the second friction coefficient μ2 that serves as a reference for the magnitude of the second hysteresis torque H2 is smaller than the first friction coefficient μ1 that serves as a reference for the magnitude of the first hysteresis torque H1 (μ2 < μ1) value is set. Therefore, the decrease degree of the first hysteresis torque H1 is larger than the increase degree of the second hysteresis torque H2, and the hysteresis torque of the damper device DA as a whole decreases compared to the low pressure supply state (here, This is a small hysteresis torque Hl (Hl <Hh).) In this respect, the hysteresis torque variable mechanism HV according to the present embodiment functions as a “hysteresis torque reduction mechanism”.

  When the internal combustion engine E completes explosion and reaches a steady state at least equal to or higher than the idling speed (indicated as Ni in FIG. 4), the supply hydraulic pressure from the hydraulic supply circuit SC is relatively high (second reference hydraulic pressure P2 or higher in FIG. 4) (Hereinafter referred to as “high pressure supply state”). In the high pressure supply state, the hysteresis torque of the damper device DA is maintained in a small state (small hysteresis torque Hl). Therefore, the small torsional vibration of the internal combustion engine E during the steady operation of the internal combustion engine E can be effectively damped without depending on the relative rotation angle between the input side rotation member 11 and the output side rotation member 12 of the damper device DA. Can do. Therefore, it is possible to effectively suppress the occurrence of rattling noise during the steady operation of the internal combustion engine E.

  When the fuel injection is stopped and the rotational speed of the internal combustion engine E gradually decreases to reach the first reference rotational speed N1, the hydraulic pressure supplied from the hydraulic pressure supply circuit SC also decreases below the first reference hydraulic pressure P1. A low pressure supply state is established. Then, the urging force by the urging member 24 becomes dominant again with respect to the hydraulic pressure supplied to the displacement mechanism hydraulic oil chamber R1, and the hysteresis torque of the damper device DA increases as compared with the high pressure supply state ( Large hysteresis torque Hh). In this respect, the hysteresis torque variable mechanism HV according to the present embodiment also functions as a “hysteresis torque increasing mechanism”.

  The specific switching point of the magnitude of the hysteresis torque of the damper device DA according to the hydraulic pressure supplied from the hydraulic pressure supply circuit SC depends on the elastic coefficient of the urging member 24 and the cylindrical portion 13 of the output side rotating member 12. It can be adjusted by appropriately changing the setting of the area (pressure receiving area) of the axial bottom surface 32b.

  Thus, the hysteresis torque variable mechanism HV according to the present embodiment is driven by the hydraulic pressure supplied from the hydraulic pressure supply circuit SC to increase or decrease the hysteresis torque of the damper device DA. At this time, the hydraulic pressure generated by the oil pump MP rotating at a speed proportional to the rotational speed of the input shaft I (internal combustion engine E) is supplied from the hydraulic pressure supply circuit SC. The hysteresis torque variable mechanism HV maintains the hysteresis torque of the damper device DA at the large hysteresis torque Hh in the low pressure supply state, and maintains the hysteresis torque of the damper device DA at the small hysteresis torque Hl in the high pressure supply state. Therefore, when the internal combustion engine E is started and stopped in a low pressure supply state, the occurrence of shock can be effectively suppressed by setting the large hysteresis torque Hh. Further, during the steady operation of the internal combustion engine E that is in a high pressure supply state, the occurrence of rattling noise can be effectively suppressed by setting the small hysteresis torque Hl. Thus, the hysteresis torque variable mechanism HV according to the present embodiment is linked to the driving state of the internal combustion engine E so that the damper device has an appropriate size that is desired according to the driving state of the internal combustion engine E. There is also a great advantage in that the hysteresis torque of DA can be switched.

2. Second Embodiment A second embodiment of the hybrid drive device according to the present invention will be described with reference to the drawings. FIG. 5 is a skeleton diagram showing the configuration of the hybrid drive apparatus H according to the present embodiment. The hybrid drive device H is configured as a so-called 1-motor parallel type hybrid drive device. In the hybrid drive device H according to the present embodiment, the specific configuration of the drive transmission system is different from that of the first embodiment, so that the configuration of the hydraulic pressure supply circuit SC and the hysteresis torque variable mechanism HV are compared. The hydraulic pressure supplied from the hydraulic pressure supply circuit SC is also partially different from that of the first embodiment. 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 specified are the same as those in the first embodiment.

  As shown in FIG. 5, the hybrid drive device H according to the present embodiment includes an input shaft I that is drivingly connected to the internal combustion engine E via the damper device DA, an output shaft O ′ that is drivingly connected to the wheels W, A rotary electric machine MG provided on the output shaft O ′ side with respect to the damper device DA on the power transmission path, and a transmission device TM are provided. Each of these components is housed in a case 2 (see FIG. 6) that is fixed to the vehicle body.

  The input shaft I is drivingly connected to the internal combustion engine E. In the present embodiment, the input shaft I is drivingly connected to the intermediate shaft M via the input clutch CT. Here, the input clutch CT is provided between the internal combustion engine E and the rotating electrical machine MG so as to be able to switch between transmission and interruption of the driving force between the internal combustion engine E and the rotating electrical machine MG. The input clutch CT operates according to the hydraulic pressure and selectively drives and connects the input shaft I and the intermediate shaft M. As such an input clutch CT, for example, a wet multi-plate clutch or a dry single-plate clutch is preferably used. In the present embodiment, the input clutch CT corresponds to the “friction engagement device” according to the present invention. Further, the input shaft I corresponds to the “connecting member” in the present invention.

  The rotating electrical machine MG includes a stator St fixed to the case 2 and a rotor Ro that is rotatably supported on the radially inner side of the stator St. The rotor Ro of the rotating electrical machine MG is drivingly connected so as to rotate integrally with the intermediate shaft M. The rotating electrical machine MG can perform a function as a motor (electric motor) that generates power by receiving power supply and a function (generator) that generates power by receiving power supply. Yes. When rotating electric machine MG functions as a generator, it generates electric power by the torque of internal combustion engine E or the inertial force of the vehicle to charge the battery. On the other hand, when the rotating electrical machine MG functions as a motor, the rotating electrical machine MG receives power supplied from the battery and performs powering.

  The transmission device TM is a device that changes the rotational speed of the intermediate shaft M at a predetermined speed ratio and transmits it to the output shaft O ′. Examples of such a transmission TM include an automatic or manual stepped transmission that can switch between a plurality of shift stages having different transmission ratios, an automatic continuously variable transmission that can change the transmission ratio steplessly, and the like. Can be used. The transmission TM shifts the rotational speed of the intermediate shaft M at a predetermined speed ratio at each time point, converts torque, and transmits the torque to the output shaft O ′. The torque transmitted from the transmission device TM to the output shaft O 'is distributed and transmitted to the two left and right wheels W via the output differential gear mechanism DF. In the present embodiment, the output shaft O ′ corresponds to the “output member” in the present invention.

  In the present embodiment, an oil pump MP is disposed between the rotating electrical machine MG and the transmission device TM in the axial direction. The oil pump MP is an inscribed gear pump having an inner rotor and an outer rotor. The inner rotor of the oil pump MP is drivingly connected so as to rotate integrally with the intermediate shaft M. Note that it is also preferable to use a circumscribed gear pump, vane pump, or the like as the oil pump MP. Further, the hybrid drive device H according to the present embodiment is electrically driven by an electric motor (not shown) independently of the oil pump MP, regardless of the internal combustion engine E and the rotating electrical machine MG as the driving force source of the vehicle. An oil pump EP is provided. The oil discharged by the oil pump MP and the electric oil pump EP is adjusted to a predetermined oil pressure by the oil pressure control device VB, and then passed through oil passages formed in the case 2 of the hybrid drive device H, various rotating shafts, and the like. , Supplied to each part of the hybrid drive device H. In the present embodiment, the hydraulic pressure supply circuit AC is a hydraulic pressure supply circuit from the hydraulic pressure control device VB to the input clutch CT.

  In the present embodiment, as shown in FIG. 5, a hydraulic pressure supply circuit SC that communicates with the displacement mechanism hydraulic oil chamber R1 is branched from the hydraulic pressure supply circuit AC to the input clutch CT. More specifically, as shown in FIG. 6, an in-shaft oil passage L2 that constitutes a part of the operating hydraulic pressure supply circuit AC is formed so as to extend in the intermediate shaft M in the axial direction. The in-shaft oil passage L2 communicates with the hydraulic oil chamber R2 of the input clutch CT through an oil hole 44 extending in the radial direction in the intermediate shaft M. When hydraulic oil pressure adjusted to a predetermined pressure is supplied to the hydraulic oil chamber R2 via the hydraulic pressure control device VB, the piston 42 moves to one side in the axial direction, and the plurality of friction plates 41 are engaged with each other. As shown in FIG. 6, in the present embodiment, the input clutch CT is disposed on the radially inner side of the rotating electrical machine MG. The input clutch CT is housed inside a rotor support member 46 having a substantially Ω-shaped cross section that supports the rotor Ro of the rotating electrical machine MG. A space formed between the input shaft I and the intermediate shaft M and the rotor support member 46 is an oil-tight space.

  The in-shaft oil passage L <b> 2 extends in the intermediate shaft M in the axial direction and opens on an end surface on one axial side of the intermediate shaft M. Further, the end portion 51 on one side in the axial direction of the intermediate shaft M is inserted into a hole portion 52 formed on the inner peripheral portion of the input shaft I and opening on the other side in the axial direction. The in-shaft oil passage L1 extending in the axial direction on the inner peripheral portion of the input shaft I is open on both end surfaces of the input shaft I in the axial direction. In this way, the hydraulic pressure supply according to the present embodiment is achieved by the portion of the in-shaft oil passage L2 in the intermediate shaft M on the one side in the axial direction from the oil hole 44 and the in-shaft oil passage L1 in the input shaft I. A circuit SC is formed. Accordingly, the hydraulic pressure supplied to the hydraulic oil chamber R2 of the input clutch CT is also supplied to the displacement mechanism hydraulic oil chamber R1.

  The hybrid drive device H according to the present embodiment includes a plurality of travel modes including a parallel mode and an electric travel mode that can be switched. For example, when the mode is switched from the electric travel mode to the parallel mode, the input clutch CT that has been released in the electric travel mode is engaged, and the rotational speed and torque of the rotating electrical machine MG are increased. The rotational speed of the internal combustion engine E is increased via the input clutch CT in the engaged state. After the rotational speed of the internal combustion engine E increases and eventually reaches a predetermined ignition start rotational speed, fuel injection is started and spark ignition is performed to start the internal combustion engine E. Thus, the hybrid drive device H according to the present embodiment is configured to be able to start the internal combustion engine E by the torque of the rotating electrical machine MG. At the time of steady operation after the start of the internal combustion engine E, the hydraulic pressure adjusted to the complete engagement pressure is supplied to the hydraulic oil chamber R2 via the hydraulic pressure supply circuit AC, and the input clutch CT is brought into the complete engagement state. The

  That is, the hydraulic pressure supplied from the hydraulic pressure supply circuit AC is basically zero because the input clutch CT is released when the internal combustion engine E is stopped. On the other hand, the supply hydraulic pressure from the operating hydraulic pressure supply circuit AC is basically set to a complete engagement pressure equal to or higher than a predetermined pressure in order to bring the input clutch CT into a completely engaged state during the steady operation of the internal combustion engine E. Thus, the hydraulic pressure supplied from the operating hydraulic pressure supply circuit AC is higher after the start of the internal combustion engine E is completed than when the internal combustion engine E is started. Accordingly, the hydraulic pressure supplied from the hydraulic pressure supply circuit SC formed by branching from the hydraulic pressure supply circuit AC is higher after the completion of the start of the internal combustion engine E than when the start operation of the internal combustion engine E is started. Then, such supply hydraulic pressure is supplied to the displacement mechanism hydraulic oil chamber R1.

  The configuration of the damper device DA (including the hysteresis torque variable mechanism HV) provided in the hybrid drive device H according to the present embodiment is basically the same as that of the first embodiment. Therefore, even in the configuration of the present embodiment, the hysteresis torque variable mechanism HV is interlocked with the driving state of the internal combustion engine E so that the damper device has a desired appropriate size according to the driving state of the internal combustion engine E. The hysteresis torque of DA can be switched. That is, when the internal combustion engine E is started and stopped in a low pressure supply state, the occurrence of shock can be effectively suppressed by setting the large hysteresis torque Hh. Further, during the steady operation of the internal combustion engine E that is in a high pressure supply state, the occurrence of rattling noise can be effectively suppressed by setting the small hysteresis torque Hl.

3. Other Embodiments Finally, other embodiments of the hybrid drive device according to the present invention will be described. Note that the feature configurations disclosed in each of the following embodiments are not applied only in that embodiment, and should be applied in combination with the feature configurations disclosed in the other embodiments unless a contradiction arises. Is also possible.

(1) In each of the above embodiments, the output-side rotating member 12 is biased by the biasing member 24 by the displacement mechanism DM in accordance with the hydraulic pressure supplied from the hydraulic pressure supply circuit SC to the displacement mechanism hydraulic oil chamber R1. As an example, the case where the first input side rotating member 11a and the first sliding member 21 are moved away from each other in the axial direction has been described. However, the embodiment of the present invention is not limited to this. In other words, any mechanism may be adopted as the displacement mechanism DM as long as the relative positional relationship between the input side rotating member 11 and the output side rotating member 12 is changed so as to reduce the first hysteresis torque H1. Can do. Further, any mechanism can be used as long as it reduces the hysteresis torque in accordance with the hydraulic pressure supplied from the hydraulic pressure supply circuit SC that is configured so that the hydraulic pressure becomes higher after completion of the startup than when the startup operation of the internal combustion engine E is started. It can be employed as a hysteresis torque variable mechanism HV.

(2) In each of the above embodiments, the case where the second sliding member 22 is provided between the second input side rotating member 11b and the output side rotating member 12 in the axial direction has been described as an example. However, the embodiment of the present invention is not limited to this. That is, the damper device DA includes only the input-side rotating member 11, the output-side rotating member 12, the coil spring 16, and the first sliding member 21 as main components without having the second input-side rotating member 11b. It is also one of the preferred embodiments of the present invention to have a configuration. In this case, the first hysteresis torque H1 due to the frictional resistance based on the first friction coefficient μ1 between the first sliding member 21 and the output side rotating member 12 becomes the entire hysteresis torque of the damper device DA as it is. Then, the hysteresis torque variable mechanism HV having the same configuration as that of each of the above embodiments increases or decreases the hysteresis torque (here, the first hysteresis torque H1) of the damper device DA according to the hydraulic pressure supplied from the hydraulic pressure supply circuit SC. Can be made.

(3) In each of the above embodiments, the supply hydraulic pressure from the hydraulic supply circuit SC is set to zero when the internal combustion engine E is stopped and when the start operation is started, and increases to a predetermined hydraulic pressure after the start of the internal combustion engine E is completed. The case where it is configured has been described as an example. However, the embodiment of the present invention is not limited to this. That is, the supply hydraulic pressure from the hydraulic pressure supply circuit SC only needs to be configured to be higher after the completion of the start than at the start of the start operation of the internal combustion engine E. For example, as in the second embodiment, the input clutch CT And the oil pump MP that rotates asynchronously with the internal combustion engine E, the hydraulic pressure supplied from the operating hydraulic pressure supply circuit AC and the hydraulic pressure supply circuit SC when the internal combustion engine E is stopped is not necessarily zero. Also good. In this case, when the internal combustion engine E is stopped, a configuration can be adopted in which a predetermined pressure equal to or lower than the stroke end pressure of the input clutch CT is supplied to the operating hydraulic pressure supply circuit AC and the hydraulic pressure supply circuit SC.

(4) In the first embodiment, in the two-motor split type hybrid drive device H, the hydraulic pressure generated by the oil pump MP that rotates in synchronization with the input shaft I (internal combustion engine E) is supplied to the hydraulic pressure supply circuit SC. The case where this is done has been described as an example. In the second embodiment, the case where the hydraulic pressure supply circuit SC is formed by branching from the hydraulic pressure supply circuit AC to the input clutch CT in the one-motor parallel type hybrid drive apparatus H will be described as an example. did. However, embodiments of the present invention are not limited to these. That is, for example, when the two-motor split type hybrid drive device H includes a friction engagement device that is completely engaged after the start of the internal combustion engine E, the hydraulic pressure supply circuit SC supplies the hydraulic pressure to the friction engagement device. One of the preferred embodiments of the present invention is a structure formed by branching from a circuit. Alternatively, in the one-motor parallel type hybrid drive device H, the hydraulic pressure generated by the oil pump MP rotating at a speed proportional to the rotational speed of the input shaft I (internal combustion engine E) is supplied to the hydraulic pressure supply circuit SC. This is also a preferred embodiment of the present invention.

(5) Regarding other configurations as well, the embodiments disclosed herein are illustrative in all respects, and embodiments of the present invention are not limited thereto. That is, as long as the configuration described in the claims of the present application and a configuration equivalent thereto are provided, a configuration obtained by appropriately modifying a part of the configuration not described in the claims is naturally also included in the present invention. Belongs to the technical scope.

  The present invention includes a connecting member that is drivingly connected to an internal combustion engine via a damper device, an output member that is drivingly connected to a wheel, and a rotating electrical machine provided on the output member side of the damper device on a power transmission path. And a hybrid drive device configured to be able to start the internal combustion engine by the torque of the rotating electrical machine.

H hybrid drive device E internal combustion engine MG rotating electrical machine MG1 first rotating electrical machine DA damper device DG differential gear device S sun gear (first rotating element)
CA carrier (second rotating element)
R ring gear (third rotating element)
MP Oil pump CT Input clutch (friction engagement device)
W Wheel I Input shaft (connecting member)
O Output gear (output member)
O 'Output shaft (output member)
HV Hysteresis torque variable mechanism DM Displacement mechanism GP Guide portion R1 Displacement mechanism hydraulic oil chamber 11 Input side rotating member 12 Output side rotating member 21 First sliding member (sliding member)
22 Second sliding member 24 Biasing member 31 Axial end portion 31a Spline tooth portion (spline connecting portion)
32 Axial hole 32a Spline teeth (spline connecting part)

Claims (8)

A connecting member that is drivingly connected to the internal combustion engine via the damper device, an output member that is drivingly connected to the wheel, and a rotating electrical machine provided on the output member side of the damper device on the power transmission path, A hybrid drive device configured to be able to start the internal combustion engine with the torque of the rotating electrical machine,
The damper device includes a hysteresis torque reduction mechanism that reduces the hysteresis torque according to the hydraulic pressure supplied from the hydraulic pressure supply circuit,
A hybrid drive device configured such that a hydraulic pressure supplied from the hydraulic pressure supply circuit is higher after the start of the internal combustion engine than when a start operation of the internal combustion engine is started. The damper device includes an input-side rotating member that is drivingly connected to the internal combustion engine and an output-side rotating member that is drivingly connected to the connecting member,
The hysteresis torque reduction mechanism is
A sliding member that generates a hysteresis torque due to frictional resistance between the input side rotating member and the output side rotating member;
The input-side rotating member via the sliding member so as to reduce the frictional resistance between the input-side rotating member and the output-side rotating member by the sliding member by the hydraulic pressure supplied from the hydraulic pressure supply circuit. And a displacement mechanism that changes a relative positional relationship between the output side rotation member and the output side rotation member;
The hybrid drive device according to claim 1, comprising: The displacement mechanism includes a guide portion that guides the output-side rotating member so as to be movable in the axial direction, and a biasing member that biases the output-side rotating member so as to press the sliding member in the axial direction. A displacement mechanism hydraulic fluid chamber formed between the connecting member and the output-side rotating member and communicating with the hydraulic pressure supply circuit;
In accordance with the hydraulic pressure supplied to the displacement mechanism hydraulic fluid chamber, the output side rotating member moves in the axial direction so as to be separated from the input side rotating member and the sliding member against the biasing force of the biasing member. The hybrid drive device according to claim 2.   The hybrid drive device according to claim 3, wherein the connecting member and the output-side rotating member are spline-connected in the displacement mechanism hydraulic oil chamber. The damper device includes an input-side rotating member that is drivingly connected to the internal combustion engine and an output-side rotating member that is drivingly connected to the connecting member,
The hysteresis torque reduction mechanism is
A first sliding member provided between the input-side rotating member and the output-side rotating member, and generating a frictional resistance based on a first friction coefficient between the output-side rotating member;
A second sliding member provided between the input-side rotating member and the output-side rotating member and generating a frictional resistance based on a second friction coefficient smaller than the first friction coefficient between the output-side rotating member. When,
A spline connecting portion for drivingly connecting the connecting member and the output-side rotating member, and for guiding the output-side rotating member to be movable in the axial direction with respect to the connecting member;
A biasing member that biases the output-side rotating member so as to press the first-side sliding member in the axial direction;
A displacement mechanism hydraulic fluid chamber communicating with the hydraulic pressure supply circuit,
The first sliding member, the output side rotating member, the second sliding member, and the biasing member are arranged in this order in the axial direction,
An axial end of the connecting member on the second sliding member side is inserted into an axial hole formed in the output-side rotating member and closed in the axial direction on the second sliding member side, 5. The hybrid drive device according to claim 1, wherein the displacement mechanism hydraulic fluid chamber is formed in a gap between a surface of the axial end portion and a surface of the axial hole portion.   The hydraulic pressure supply circuit includes hydraulic pressure generated by an oil pump that rotates at a speed proportional to the rotational speed of the connecting member, or hydraulic pressure that is supplied to a friction engagement device that is completely engaged after the start of the internal combustion engine. The hybrid drive device according to any one of claims 1 to 5, wherein A differential gear device having three rotating elements which are a first rotating element, a second rotating element, and a third rotating element in the order of rotational speed;
The rotating electrical machine is drivingly connected to the first rotating element of the differential gear device, the connecting member is drivingly connected to the second rotating element, and the output member is drivingly connected to the third rotating element,
The hybrid drive device according to any one of claims 1 to 6, wherein the hydraulic pressure supply circuit is formed as a hydraulic pressure supply circuit generated by an oil pump that rotates at a speed proportional to the rotational speed of the connecting member. Between the internal combustion engine and the rotating electrical machine, provided with a friction engagement device that operates according to oil pressure and can switch between transmission and interruption of driving force,
The hybrid drive device according to any one of claims 1 to 6, wherein the hydraulic pressure supply circuit is formed to branch from a hydraulic pressure supply circuit to the friction engagement device.

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