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WO2024157852A1 - Dispositif de mise en prise et dispositif d'entraînement de véhicule le comprenant - Google Patents

Dispositif de mise en prise et dispositif d'entraînement de véhicule le comprenant Download PDF

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Publication number
WO2024157852A1
WO2024157852A1 PCT/JP2024/001081 JP2024001081W WO2024157852A1 WO 2024157852 A1 WO2024157852 A1 WO 2024157852A1 JP 2024001081 W JP2024001081 W JP 2024001081W WO 2024157852 A1 WO2024157852 A1 WO 2024157852A1
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WO
WIPO (PCT)
Prior art keywords
engagement
engaged
rotating element
engaging
gear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2024/001081
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English (en)
Japanese (ja)
Inventor
平賀俊郎
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aisin Corp
Original Assignee
Aisin Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Aisin Corp filed Critical Aisin Corp
Publication of WO2024157852A1 publication Critical patent/WO2024157852A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D11/00—Clutches in which the members have interengaging parts
    • F16D11/08—Clutches in which the members have interengaging parts actuated by moving a non-rotating part axially
    • F16D11/10—Clutches in which the members have interengaging parts actuated by moving a non-rotating part axially with clutching members movable only axially

Definitions

  • the present invention relates to an engagement device that includes a first engagement mechanism and a second engagement mechanism of a meshing type, and a drive device that drives them, and to a vehicle drive device that includes the same.
  • Patent Document 1 An example of such technology is disclosed in Patent Document 1 below.
  • the reference symbols in Patent Document 1 are quoted in parentheses.
  • the first engagement mechanism of the engagement device disclosed in Patent Document 1 comprises a first engaged member and a first engagement member (C2) that moves between a first engagement position where the first engaged member engages with the first engaged member and a first release position where the engagement with the first engaged member is released.
  • the second engagement mechanism of the engagement device disclosed in Patent Document 1 comprises a second engaged member and a second engagement member (C3) that moves between a second engagement position where the second engaged member engages with the second engaged member and a second release position where the engagement with the second engaged member is released.
  • the drive device of the engagement device disclosed in Patent Document 1 includes a shift drum (32a) that is rotationally driven by a drive source (32b), a first cam mechanism (d2, 32c) that converts the rotational motion of the shift drum (32a) into linear motion and transmits it to the first engagement member (C2), and a second cam mechanism (d3, 32d) that converts the rotational motion of the shift drum (32a) into linear motion and transmits it to the second engagement member (C3).
  • the characteristic configuration of the engagement device is as follows: A first engagement mechanism of an interlocking type; A meshing type second engagement mechanism; a drive device that drives the first engagement mechanism and the second engagement mechanism, the first engagement mechanism includes a first engaged member and a first engaging member that moves between a first engagement position where the first engaged member engages with the first engaged member and a first release position where the first engaging member is released from engagement with the first engaged member; the second engagement mechanism includes a second engaged member and a second engaging member that moves between a second engagement position where the second engaged member engages with the second engaged member and a second release position where the second engaging member is released from engagement with the second engaged member;
  • the drive device is A shift drum that is rotationally driven by a drive source; A first cam mechanism that converts a rotational motion of the shift drum into a linear motion and transmits the linear motion to the first engagement member; A second cam mechanism that converts the rotational motion of the shift drum into a linear motion and transmits the linear motion to the second engagement member, The first cam mechanism and the
  • the rotation of the shift drum causes the first engagement member of the first engagement mechanism to move between the first engagement position and the first release position via the first cam mechanism, and the second engagement member of the second engagement mechanism to move between the second engagement position and the second release position via the second cam mechanism.
  • the timing at which the first engagement member moves from the first release position to the first engagement position and the timing at which the second engagement member moves from the second release position to the second engagement position are shifted from each other.
  • the characteristic configuration of the vehicle drive device is as follows:
  • the engagement device an input member drivingly connected to the internal combustion engine;
  • An output member drivingly connected to the wheels;
  • a rotating electric machine having a rotor;
  • a distribution differential gear mechanism including a first distribution rotating element, a second distribution rotating element, and a third distribution rotating element, the first distribution rotating element being drivingly connected to the input member, and the third distribution rotating element being drivingly connected to the rotor;
  • a vehicle drive device including a power transmission mechanism that transmits a driving force between a specific rotating member and the output member,
  • the first engagement mechanism is configured to connect and disconnect power transmission between the second distribution rotating element and the specific rotating member,
  • the second engagement mechanism is configured to connect and disconnect the power transmission between the first distribution rotating element and the specific rotating member, a rotational resistance of the first distribution rotating element and a rotating element that rotates integrally with the first distribution rotating element is greater than a rotational resistance of the second distribution rotating element and a rotating element that rotates integrally with the second distribution rotating
  • the rotational resistance of the first distribution rotating element and the rotating element rotating integrally therewith is greater than the rotational resistance of the second distribution rotating element and the rotating element rotating integrally therewith, so the first engaging member and the first engaged member that rotate relatively due to the rotation of the second distribution rotating element tend to be more easily rotated than the second engaging member and the second engaged member that rotate relatively due to the rotation of the first distribution rotating element. Therefore, when both the first engaging mechanism and the second engaging mechanism are not in an engaged state, the driving force of the rotating electric machine input to the third distribution rotating element can be used to appropriately rotate the first engaging member and the first engaged member of the first engaging mechanism that is first engaged, thereby eliminating the misengagement state.
  • the driving force of the rotating electric machine input to the third distribution rotating element can be used to appropriately rotate the second engaging member and the second engaged member of the second engaging mechanism, thereby eliminating the misengagement state. Therefore, with this characteristic configuration, processing can be appropriately performed to eliminate the misengagement state for both the first engagement mechanism and the second engagement mechanism.
  • FIG. 1 is a skeleton diagram of a vehicle drive device according to an embodiment of the present invention
  • FIG. 1 is a diagram showing a state of an engagement mechanism in each operation mode of a vehicle drive device according to an embodiment
  • FIG. 1 is a diagram showing a drive device provided in an engagement device according to an embodiment
  • FIG. 2 is a diagram showing the configuration of a first cam groove and a second cam groove; A time chart in which the first engagement member moves from the first release position to the first engagement position and the second engagement member moves from the second release position to the second engagement position.
  • FIG. 2 is a partially enlarged cross-sectional view of the vehicle drive device according to the embodiment taken along an axial direction;
  • the vehicle drive device 100 includes an input member I, an output member O, a rotating electric machine MG, a distribution differential gear mechanism SP, a power transmission mechanism TM, and an engagement device 10.
  • the vehicle drive device 100 further includes an output differential gear mechanism DF.
  • the input member I is drivingly connected to the internal combustion engine EG.
  • the input member I is drivingly connected to the output shaft of the internal combustion engine EG via a damper device DP that dampens fluctuations in the transmitted torque.
  • the internal combustion engine EG functions as a driving force source for the wheels W.
  • the internal combustion engine EG is a prime mover (gasoline engine, diesel engine, etc.) that is driven by the combustion of fuel to extract power.
  • driving connection refers to a state in which two rotating elements are connected so as to be able to transmit a driving force, and includes a state in which the two rotating elements are connected so as to rotate integrally, or a state in which the two rotating elements are connected so as to be able to transmit a driving force via one or more transmission members.
  • Such transmission members include various members that transmit rotation at the same speed or at a variable speed, such as shafts, gear mechanisms, belts, chains, etc.
  • transmission members may also include engagement devices that selectively transmit rotation and driving force, such as friction engagement devices and meshing engagement devices.
  • driving connection refers to a state in which multiple rotating elements in the planetary gear mechanism are connected to each other without going through other rotating elements.
  • the direction along the first axis X1 which is the rotational axis of the input member I, is referred to as the "axial direction L".
  • One side of the axial direction L is referred to as the “first axial side L1”, and the other side is referred to as the “second axial side L2".
  • the direction perpendicular to the rotational axis of a rotating member such as the input member I is referred to as the "radial direction R" based on each rotational axis. Note that when there is no need to distinguish which rotational axis is used as the reference or when it is clear which rotational axis is used as the reference, it may simply be referred to as the "radial direction R".
  • the input member I is a shaft member extending along the axial direction L.
  • the input member I is disposed on the first axial side L1 relative to the internal combustion engine EG.
  • the rotating electric machine MG functions as a driving force source for the wheels W.
  • the rotating electric machine MG has a function as a motor (electric motor) that receives a supply of electric power to generate power, and a function as a generator (electric power generator) that receives a supply of power to generate electric power.
  • the rotating electric machine MG is electrically connected to an electric storage device such as a battery or a capacitor (not shown) so as to exchange electric power with the electric storage device.
  • the rotating electric machine MG generates driving force by running using the electric power stored in the electric storage device.
  • the rotating electric machine MG also generates electric power using the driving force of the internal combustion engine EG or the driving force transmitted from the output member O that is drivingly connected to the wheels W, thereby charging the electric storage device.
  • the rotating electric machine MG includes a stator ST and a rotor RT.
  • the rotating electric machine MG is arranged on a second axis X2 that is separate from the first axis X1 and parallel to the first axis X1.
  • the stator ST is fixed to a non-rotating member (for example, the case CS described below).
  • the rotor RT is supported so as to be freely rotatable relative to the stator ST.
  • the rotor RT is connected to a first gear G1 so as to rotate integrally with the first gear G1.
  • the first gear G1 is an externally toothed gear arranged on the second axis X2.
  • the first gear G1 is arranged on the first axial side L1 relative to the rotating electric machine MG.
  • the distribution differential gear mechanism SP includes a first distribution rotating element E1, a second distribution rotating element E2, and a third distribution rotating element E3.
  • the distribution differential gear mechanism SP is disposed on a first axis X1.
  • the first distribution rotating element E1 is drivingly connected to the input member I.
  • the third distribution rotating element E3 is drivingly connected to the rotor RT.
  • the second distribution rotating element E2 is drivingly connected to the output member O via a power transmission mechanism TM.
  • the order of rotational speeds of the rotating elements of the distribution differential gear mechanism SP is first distribution rotating element E1, second distribution rotating element E2, and third distribution rotating element E3.
  • order of rotational speeds refers to the order of rotational speeds in the rotational state of each rotating element.
  • the rotational speeds of each rotating element change depending on the rotational state of the differential gear mechanism (here, the planetary gear mechanism), but the order of high and low rotational speeds of each rotating element is constant because it is determined by the structure of the differential gear mechanism.
  • the distribution differential gear mechanism SP is a planetary gear mechanism including a sun gear SG, a carrier CR, and a ring gear RG.
  • the first distribution rotating element E1 is the sun gear SG.
  • the second distribution rotating element E2 is the carrier CR.
  • the third distribution rotating element E3 is the ring gear RG.
  • the distribution differential gear mechanism SP is a single-pinion type planetary gear mechanism including a carrier CR that supports a pinion gear PG, a sun gear SG that meshes with the pinion gear PG, and a ring gear RG that is disposed radially outward of the sun gear SG in the R direction and meshes with the pinion gear PG.
  • the ring gear RG is connected to the second gear G2 so as to rotate integrally with it.
  • the second gear G2 is an externally toothed gear located on the first axis X1 and on the outside of the ring gear RG in the radial direction R.
  • the second gear G2 is drivingly connected to the first gear G1 via an idler gear IG located on the third axis X3.
  • the first gear G1 and the second gear G2 mesh with the idler gear IG at different positions in the circumferential direction of the idler gear IG.
  • the third axis X3 is a separate axis from the first axis X1 and the second axis X2, and is parallel to them.
  • the sun gear SG is connected to the transmission shaft member TS so as to rotate integrally with it.
  • the transmission shaft member TS is formed to extend along the axial direction L.
  • the transmission shaft member TS is disposed on the first axis X1.
  • the transmission shaft member TS is formed to extend from the sun gear SG toward the second axial side L2.
  • the power transmission mechanism TM is configured to transmit driving force between a specific rotating member RS and an output member O.
  • the power transmission mechanism TM is a transmission that changes the speed of the rotation from the distribution differential gear mechanism SP and transmits it to the output member O.
  • the power transmission mechanism TM includes a third gear G3, a fourth gear G4, a fifth gear G5, a sixth gear G6, a seventh gear G7, and an eighth gear G8.
  • the third gear G3 and the fourth gear G4 are arranged on the first axis X1.
  • the third gear G3 and the fourth gear G4 are supported so as to be rotatable relative to the transmission shaft member TS.
  • the fourth gear G4 is formed with a larger diameter than the third gear G3.
  • the fourth gear G4 is arranged on the second axial side L2 of the third gear G3.
  • the third gear G3 corresponds to the specific rotating member RS.
  • the fifth gear G5, sixth gear G6, and seventh gear G7 are arranged on a fourth axis X4 that is parallel to the first axis X1 to the third axis X3.
  • the fifth gear G5, sixth gear G6, and seventh gear G7 are connected to rotate integrally with each other.
  • the fifth gear G5 meshes with the third gear G3.
  • the sixth gear G6 meshes with the fourth gear G4.
  • the sixth gear G6 is formed with a smaller diameter than the fifth gear G5.
  • the seventh gear G7 is formed with a smaller diameter than the sixth gear G6.
  • the fifth gear G5, seventh gear G7, and sixth gear G6 are arranged in the order described from the first axial side L1 toward the second axial side L2.
  • the eighth gear G8 is disposed on a fifth axis X5 that is parallel to the first axis X1 to the fourth axis X4.
  • the eighth gear G8 meshes with the seventh gear G7.
  • the eighth gear G8 is formed with a larger diameter than the seventh gear G7.
  • the eighth gear G8 corresponds to the output member O.
  • the first power transmission path between the third gear G3 and the output member O (here, the eighth gear G8) and the second power transmission path between the fourth gear G4 and the output member O have different gear ratios.
  • the fifth gear G5 is formed with a larger diameter than the third gear G3.
  • the sixth gear G6 is formed with a smaller diameter than the fourth gear G4. Therefore, in this embodiment, the first power transmission path has a larger gear ratio than the second power transmission path.
  • the output differential gear mechanism DF is configured to distribute the rotation of the output member O to a pair of wheels W.
  • the output differential gear mechanism DF is disposed on the fifth axis X5.
  • the output differential gear mechanism DF is a bevel gear type differential gear mechanism.
  • the output differential gear mechanism DF includes a hollow differential case, a differential pinion shaft supported so as to rotate integrally with the differential case, a differential pinion gear supported rotatably relative to the differential pinion shaft, and a pair of differential side gears that mesh with the differential pinion gear.
  • the differential pinion gear and the pair of differential side gears are housed in a differential case.
  • the differential pinion shaft is fixed to the differential case.
  • the differential case is connected to the eighth gear G8 as the output member O so as to rotate integrally.
  • each of the pair of differential side gears is connected to a drive shaft DS that is drivingly connected to the wheels W so as to rotate integrally.
  • the engagement device 10 includes a first engagement mechanism C1 and a second engagement mechanism C2.
  • the engagement device 10 further includes a third engagement mechanism C3, a fourth engagement mechanism C4, and a disconnection engagement mechanism K0.
  • the first engagement mechanism C1 is disposed on the first axis A1.
  • the first axis A1 coincides with the first axis X1. Therefore, the direction along the first axis A1, which is the axis on which the first engagement mechanism C1 is disposed, is the axial direction L.
  • the first engagement mechanism C1, the second engagement mechanism C2, the third engagement mechanism C3, the fourth engagement mechanism C4, and the disconnection engagement mechanism K0 are disposed coaxially. Then, from the first axial side L1 toward the second axial side L2, the third engagement mechanism C3, the first engagement mechanism C1, the second engagement mechanism C2, the fourth engagement mechanism C4, and the disconnection engagement mechanism K0 are disposed in the order described above.
  • the first engagement mechanism C1 includes a first engaged member 11 and a first engaging member 12.
  • the first engaging member 12 is configured to be movable between a first engaging position P11 where the first engaged member 11 engages with the first engaged member 12 and a first disengaging position P12 where the engagement with the first engaged member 11 is disengaged.
  • the first engaging member 12 is supported by a first support member 121 so as to be movable in the axial direction L.
  • the first support member 121 is connected to the carrier CR so as to rotate integrally therewith.
  • the first support member 121 is connected to the carrier CR so as to rotate integrally therewith via a connecting member CM formed in a cylindrical shape with the first axis A1 as its axis.
  • the connecting member CM is arranged to cover the transmission shaft member TS from the outside in the radial direction R.
  • the first engaged member 11 is disposed adjacent to the first support member 121 on the second axial side L2. Also, in this embodiment, the first engaged member 11 is disposed adjacent to the third gear G3 on the first axial side L1. The first engaged member 11 is connected to the third gear G3 so as to rotate integrally with it.
  • the first engaging member 12 is formed in a cylindrical shape with the first axis A1 as its axis. Internal teeth are formed on the inner circumference of the first engaging member 12, and external teeth corresponding to the internal teeth are formed on the first support member 121. These internal teeth and external teeth are engaged with each other so as to be movable relative to each other in the axial direction L, but unable to rotate relative to each other in the circumferential direction. In this way, the first engaging member 12 rotates integrally with the first support member 121, and is supported so as to slide relative to the first support member 121 in the axial direction L.
  • the first engaged member 11 is formed in a cylindrical shape with the first axis A1 as its axis.
  • the outer periphery of the first engaged member 11 is formed with external teeth that are movable relative to the internal teeth of the first engaging member 12 in the axial direction L and cannot rotate relative to the internal teeth in the circumferential direction.
  • the internal teeth of the first engaging member 12 are engaged with both the external teeth of the first supporting member 121 and the external teeth of the first engaged member 11.
  • the carrier CR connected to the first supporting member 121 and the third gear G3 connected to the first engaged member 11 are connected to rotate integrally with each other.
  • the carrier CR connected to the first support member 121 and the third gear G3 connected to the first engaged member 11 are able to rotate relative to each other.
  • the second engagement mechanism C2 includes a second engaged member 21 and a second engaging member 22.
  • the second engaging member 22 is configured to be movable between a second engagement position P21 where it engages with the second engaged member 21, and a second release position P22 where it is disengaged from the second engaged member 21.
  • the second engaging member 22 is supported by a second support member 221 so as to be movable in the axial direction L.
  • the second support member 221 is connected to the sun gear SG via the transmission shaft member TS so as to rotate integrally with the sun gear SG.
  • the second engaged member 21 is disposed adjacent to the second support member 221 on the first axial side L1. Also, in this embodiment, the second engaged member 21 is disposed adjacent to the third gear G3 on the second axial side L2.
  • the second engaged member 21 is connected to rotate integrally with the third gear G3. That is, in this embodiment, the first engaged member 11 and the second engaged member 21 are disposed on opposite sides of the third gear G3 and are configured to rotate integrally with the third gear G3. In this way, in this embodiment, the first engaged member 11 and the second engaged member 21 are configured to rotate integrally with each other.
  • the third gear G3 corresponds to the target gear Gt.
  • the second engagement member 22 is formed in a cylindrical shape with the first axis A1 as its axis. Internal teeth are formed on the inner circumference of the second engagement member 22, and external teeth corresponding to these internal teeth are formed on the second support member 221. These internal teeth and external teeth are engaged with each other so as to be movable relative to each other in the axial direction L, but not rotatable relative to each other in the circumferential direction. In this way, the second engagement member 22 rotates integrally with the second support member 221, and is supported so as to slide relative to the second support member 221 in the axial direction L.
  • the second engaged member 21 is formed in a cylindrical shape with the first axis A1 as its axis.
  • the outer periphery of the second engaged member 21 is formed with external teeth that are movable relative to the internal teeth of the second engaging member 22 in the axial direction L and cannot rotate relative to the internal teeth in the circumferential direction.
  • the sun gear SG connected to the second supporting member 221 and the third gear G3 connected to the second engaged member 21 are connected to rotate integrally with each other.
  • the third engagement mechanism C3 includes a third engaged member 31.
  • the first engagement member 12 is shared between the first engagement mechanism C1 and the third engagement mechanism C3. Therefore, in this embodiment, the first engagement member 12 is configured to be movable to a third engagement position P31 where it engages with the third engaged member 31, in addition to the first engagement position P11 and the first release position P12.
  • the first engagement mechanism C1 and the third engagement mechanism C3 constitute a first dog clutch DG1 that exclusively switches their engagement state by the first engagement member 12.
  • the third engaged member 31 is disposed adjacent to the first axial side L1 of the first support member 121.
  • the third engaged member 31 is connected to the ring gear RG so as to rotate integrally with the ring gear RG.
  • the third engaged member 31 is formed in a cylindrical shape with the first axis A1 as its axis.
  • the outer periphery of the third engaged member 31 is formed with external teeth that are movable relative to the internal teeth of the first engaging member 12 in the axial direction L and cannot rotate relative to the internal teeth in the circumferential direction.
  • the internal teeth of the first engaging member 12 are engaged with both the external teeth of the first supporting member 121 and the external teeth of the third engaged member 31.
  • the carrier CR connected to the first supporting member 121 and the ring gear RG connected to the third engaged member 31 are connected to rotate integrally with each other.
  • the carrier CR connected to the first support member 121 and the ring gear RG connected to the third engaged member 31 are able to rotate relative to each other.
  • the fourth engagement mechanism C4 includes a fourth engaged member 41.
  • the second engagement mechanism C2 and the fourth engagement mechanism C4 share the second engagement member 22. Therefore, in this embodiment, the second engagement member 22 is configured to be movable to the fourth engagement position P41 where it engages with the fourth engaged member 41, in addition to the second engagement position P21 and the second release position P22.
  • the second engagement mechanism C2 and the fourth engagement mechanism C4 constitute a second dog clutch DG2 that exclusively switches their engagement state by the second engagement member 22.
  • the fourth engaged member 41 is disposed adjacent to the second axial side L2 of the second support member 221.
  • the fourth engaged member 41 is connected to the fourth gear G4 so as to rotate integrally with it.
  • the fourth engaged member 41 is formed in a cylindrical shape with the first axis A1 as its axis.
  • the outer periphery of the fourth engaged member 41 is formed with external teeth that are movable relative to the internal teeth of the second engaging member 22 in the axial direction L and cannot rotate relative to the internal teeth in the circumferential direction.
  • the internal teeth of the second engaging member 22 are engaged with both the external teeth of the second supporting member 221 and the external teeth of the fourth engaged member 41.
  • the sun gear SG connected to the second supporting member 221 and the fourth gear G4 connected to the fourth engaged member 41 are connected to rotate integrally with each other.
  • the disengagement engagement mechanism K0 is configured to connect and disconnect the power transmission between the input member I and the distribution differential gear mechanism SP.
  • the disengagement engagement mechanism K0 includes an engaged member 51 and an engaging member 52.
  • the engaging member 52 is configured to be movable between a connection position P51 where it engages with the engaged member 51 and a disengagement position P52 where it is disengaged from the engaged member 51.
  • the engaging member 52 is supported by a support member 521 so as to be movable in the axial direction L.
  • the support member 521 is connected to the sun gear SG via the transmission shaft member TS so as to rotate integrally with the sun gear SG.
  • the engaged member 51 is disposed adjacent to the support member 521 on the second axial side L2.
  • the engaged member 51 is connected to the input member I so as to rotate integrally with the input member I.
  • the engaging member 52 is formed in a cylindrical shape with the first axis A1 as its axis. Internal teeth are formed on the inner circumference of the engaging member 52, and external teeth corresponding to the internal teeth are formed on the support member 521. These internal teeth and external teeth are engaged with each other so as to be movable relative to each other in the axial direction L, but unable to rotate relative to each other in the circumferential direction. In this way, the engaging member 52 rotates integrally with the support member 521, and is supported so as to slide relative to the support member 521 in the axial direction L.
  • the engaged member 51 is formed in a cylindrical shape with the first axis A1 as its axis.
  • the outer periphery of the engaged member 51 is formed with external teeth that are movable relative to the internal teeth of the engaging member 52 in the axial direction L and engage with the internal teeth of the engaging member 52 so as not to rotate relative to the internal teeth in the circumferential direction.
  • the internal teeth of the engaging member 52 are engaged with both the external teeth of the support member 521 and the external teeth of the engaged member 51.
  • the sun gear SG connected to the support member 521 and the input member I connected to the engaged member 51 are connected so as to rotate integrally with each other.
  • the vehicle drive device 100 has the following operating modes: a first EV mode (EV1), a second EV mode (EV2), a reverse mode (REV), a first HV mode (HV1), a second HV mode (HV2), an eTC mode (eTC), and a charging mode (PC).
  • a first EV mode EV1
  • a second EV mode EV2
  • a reverse mode REV
  • HV1 first HV mode
  • HV2 second HV mode
  • eTC eTC
  • PC charging mode
  • Figure 2 shows the state of the engagement mechanisms in each operating mode of the vehicle drive device 100.
  • "ON” indicates that the target engagement mechanism is in an engaged state
  • “-” indicates that the target engagement mechanism is in a released state.
  • “L” indicates that, of the two engagement mechanisms constituting the target dog clutch, the one located on the first axial side L1 (left side in Figure 1) is in an engaged state.
  • “R” indicates that, of the two engagement mechanisms constituting the target dog clutch, the one located on the second axial side L2 (right side in Figure 1) is in an engaged state.
  • the first EV mode and the second EV mode are modes in which the vehicle is driven by the torque of only the rotating electric machine MG, out of the internal combustion engine EG and the rotating electric machine MG.
  • the disconnecting engagement mechanism K0 is released, and power transmission between the internal combustion engine EG and the distribution differential gear mechanism SP is interrupted.
  • the first engagement mechanism C1 of the first dog clutch DG1 is engaged, and the second engagement mechanism C2 of the second dog clutch DG2 is engaged.
  • the carrier CR and the sun gear SG are connected, and the three rotating elements E1 to E3 of the distribution differential gear mechanism SP rotate integrally with one another.
  • the third gear G3 is connected to rotate integrally with the carrier CR and the sun gear SG.
  • the rotation transmitted to the third gear G3 is then changed in speed in the first power transmission path, which has a relatively large gear ratio, and transmitted to the output member O side.
  • the third engagement mechanism C3 of the first dog clutch DG1 is engaged, and the fourth engagement mechanism C4 of the second dog clutch DG2 is engaged.
  • the ring gear RG and the carrier CR are connected, and the three rotating elements E1 to E3 of the distribution differential gear mechanism SP rotate integrally with one another.
  • the fourth gear G4 is connected to the sun gear SG so as to rotate integrally.
  • the rotation input from the rotating electric machine MG to the distribution differential gear mechanism SP is transmitted as is to the fourth gear G4.
  • the rotation transmitted to the fourth gear G4 is then changed in speed in the second power transmission path, which has a relatively small gear ratio, and transmitted to the output member O.
  • the reverse mode is a mode in which the vehicle moves backward.
  • the disconnection engagement mechanism K0 is released, and power transmission between the internal combustion engine EG and the distribution differential gear mechanism SP is interrupted.
  • the first HV mode and the second HV mode are modes in which the vehicle is driven by at least the torque of the internal combustion engine EG and the rotating electric machine MG.
  • the disconnection engagement mechanism K0 is engaged, enabling power transmission between the internal combustion engine EG and the distribution differential gear mechanism SP.
  • rotation from the internal combustion engine EG is input to the sun gear SG.
  • the engagement state of the first dog clutch DG1 and the second dog clutch DG2 is the same as in the first EV mode and the second EV mode, so a detailed description of the power transmission between the rotating electric machine MG and the output member O will be omitted.
  • the eTC mode is a mode in which the distribution differential gear mechanism SP amplifies the torque of the internal combustion engine EG using the torque of the rotating electric machine MG as a reaction force and transmits it to the output member O, thereby propelling the vehicle.
  • the eTC mode is known as an electric torque converter mode, since it can amplify the torque of the internal combustion engine EG and transmit it to the output member O.
  • the disconnecting engagement mechanism K0 is engaged, enabling power transmission between the internal combustion engine EG and the distribution differential gear mechanism SP. As a result, rotation from the internal combustion engine EG is input to the sun gear SG.
  • the first engagement mechanism C1 of the first dog clutch DG1 is engaged, and the second dog clutch DG2 is released (both the second engagement mechanism C2 and the fourth engagement mechanism C4 are released).
  • the rotating electric machine MG generates a reaction torque of the torque transmitted from the internal combustion engine EG to the sun gear SG, and transmits it to the ring gear RG.
  • the torque of the internal combustion engine EG and the torque of the rotating electric machine MG are combined and transmitted to the carrier CR, and then transmitted from the carrier CR to the output member O.
  • the charging mode is a mode in which the rotating electric machine MG generates electricity using the torque of the internal combustion engine EG to charge the above-mentioned power storage device.
  • the disconnecting engagement mechanism K0 is engaged.
  • the third engagement mechanism C3 of the first dog clutch DG1 is engaged, and the second dog clutch DG2 is released (both the second engagement mechanism C2 and the fourth engagement mechanism C4 are released).
  • the internal combustion engine EG outputs torque, and the rotating electric machine MG is controlled to generate electricity by outputting torque in the opposite direction to the rotational direction of the rotor RT, which is rotated by the torque of the internal combustion engine EG.
  • the engagement device 10 further includes a drive device D that drives the first engagement mechanism C1 and the second engagement mechanism C2.
  • the drive device D includes a shift drum 6, a first cam mechanism 7, and a second cam mechanism 8.
  • the shift drum 6 is a member that is rotationally driven by the drive source 9.
  • the shift drum 6 is formed in a cylindrical shape.
  • the second axis A2, which is the rotation axis of the shift drum 6, is arranged parallel to the first axis A1 (see FIG. 1).
  • an electric motor such as an AC rotating electric machine driven by multiple-phase AC power can be used as the drive source 9.
  • the first cam mechanism 7 is configured to convert the rotational motion of the shift drum 6 into linear motion and transmit it to the first engagement member 12.
  • the first cam mechanism 7 includes a first cam groove 71, a first cam follower 72, and a first connecting member 73.
  • the first cam groove 71 is provided on the outer peripheral surface of the shift drum 6.
  • the first cam groove 71 is formed so that the position in the axial direction L changes depending on the position in the circumferential direction C on the outer peripheral surface of the shift drum 6.
  • the circumferential direction C is the direction that circles around the second axis A2.
  • the first cam follower 72 is disposed within the first cam groove 71 so as to be guided by the first cam groove 71.
  • the first cam follower 72 is disposed at a fixed position in the circumferential direction C. As the shift drum 6 rotates, the first cam follower 72 moves in the axial direction L according to the shape of the first cam groove 71.
  • the first connecting member 73 is connected to the first cam follower 72 so as to move integrally therewith.
  • the first connecting member 73 also holds the first engaging member 12 in a state in which relative movement in the axial direction L with respect to the first engaging member 12 is restricted. In this way, the first connecting member 73 moves in the axial direction L integrally with the first cam follower 72, and accordingly moves the first engaging member 12 in the axial direction L. In this way, the first connecting member 73 links the movement of the first cam follower 72 in the axial direction L with the movement of the first engaging member 12 in the axial direction L.
  • the second cam mechanism 8 is configured to convert the rotational motion of the shift drum 6 into linear motion and transmit it to the second engagement member 22.
  • the second cam mechanism 8 includes a second cam groove 81, a second cam follower 82, and a second connecting member 83.
  • the second cam groove 81 is provided on the outer peripheral surface of the shift drum 6.
  • the second cam groove 81 is formed so that its position in the axial direction L changes depending on its position in the circumferential direction C.
  • the second cam follower 82 is disposed within the second cam groove 81 so as to be guided by the second cam groove 81.
  • the second cam follower 82 is disposed at a fixed position in the circumferential direction C. As the shift drum 6 rotates, the second cam follower 82 moves in the axial direction L according to the shape of the second cam groove 81.
  • the second connecting member 83 is connected to the second cam follower 82 so as to move integrally therewith.
  • the second connecting member 83 also holds the second engaging member 22 in a state in which relative movement in the axial direction L with respect to the second engaging member 22 is restricted. In this way, the second connecting member 83 moves in the axial direction L integrally with the second cam follower 82, thereby moving the second engaging member 22 in the axial direction L. In this way, the second connecting member 83 links the movement of the second cam follower 82 in the axial direction L with the movement of the second engaging member 22 in the axial direction L.
  • FIG. 4 is a diagram showing an example of the first cam groove 71 and the second cam groove 81 expanded on a plane along the circumferential direction C.
  • phases ⁇ 0 to ⁇ 12 are the positions of the first cam groove 71 and the second cam groove 81 in the circumferential direction C, and the first cam follower 72 and the second cam follower 82 pass through them in the order shown as the shift drum 6 rotates.
  • the first engagement position P11, the first release position P12, and the third engagement position P31 which indicate the position in the axial direction L of the first engagement member 12, are shown corresponding to the position in the axial direction L of the first cam groove 71.
  • the second engagement position P21, the second release position P22, and the fourth engagement position P41 which indicate the position in the axial direction L of the second engagement member 22, are shown corresponding to the position in the axial direction L of the second cam groove 81.
  • the first engagement member 12 corresponding to the first cam groove 71 is located at the third engagement position P31 at phase ⁇ 0.
  • the first engagement member 12 moves from the third engagement position P31 toward the first release position P12 as the phase moves from ⁇ 0 to phase ⁇ 1, and is located at the first release position P12 at phase ⁇ 1.
  • the first engagement member 12 moves from the first release position P12 toward the first engagement position P11 as the phase moves from ⁇ 1 to phase ⁇ 2, and is located at the first engagement position P11 at phase ⁇ 3.
  • the first engagement member 12 does not move in the axial direction L from phase ⁇ 3 to phase ⁇ 9 while maintaining the first engagement position P11.
  • the first engagement member 12 moves from the first engagement position P11 toward the first release position P12 as it moves from phase ⁇ 9 to phase ⁇ 10, and is located at the first release position P12 at phase ⁇ 10. From phase ⁇ 10 to phase ⁇ 11, the first engagement member 12 does not move in the axial direction L while maintaining the first release position P12.
  • the first engagement member 12 moves from the first release position P12 toward the third engagement position P31 as it moves from phase ⁇ 11 to phase ⁇ 12, and is located at the third engagement position P31 at phase ⁇ 12.
  • the first engagement member 12 does not move in the axial direction L while maintaining the third engagement position P31 until it returns from phase ⁇ 12 to phase ⁇ 0.
  • the second engagement member 22 corresponding to the second cam groove 81 is located at the second release position P22 at phase ⁇ 0. From phase ⁇ 0 to phase ⁇ 2, the second engagement member 22 does not move in the axial direction L while maintaining the second release position P22. The second engagement member 22 moves from the second release position P22 toward the second engagement position P21 from phase ⁇ 2 to phase ⁇ 3, and is located at the second engagement position P21 at phase ⁇ 4.
  • the second engagement member 22 does not move in the axial direction L while maintaining the second engagement position P21 from phase ⁇ 4 to phase ⁇ 5.
  • the second engagement member 22 moves from the second engagement position P21 toward the second release position P22 as it moves from phase ⁇ 5 to phase ⁇ 6, and is located at the second release position P22 at phase ⁇ 6.
  • the second engagement member 22 does not move in the axial direction L while maintaining the second release position P22 from phase ⁇ 6 to phase ⁇ 7.
  • the second engagement member 22 moves from the second release position P22 toward the fourth engagement position P41 as it moves from phase ⁇ 7 to phase ⁇ 8, and is located at the fourth engagement position P41 at phase ⁇ 8.
  • the second engagement member 22 does not move in the axial direction L while maintaining the fourth engagement position P41 from phase ⁇ 8 to phase ⁇ 12.
  • the second engagement member 22 moves from the fourth engagement position P41 toward the second release position P22 until it returns from phase ⁇ 12 to phase ⁇ 0.
  • the first cam mechanism 7 and the second cam mechanism 8 are configured to move one of the first engaging member 12 and the second engaging member 22 later than the other when moving the first engaging member 12 from the first release position P12 to the first engaging position P11 and moving the second engaging member 22 from the second release position P22 to the second engaging position P21.
  • the first engaging member 12 starts moving toward the first engaging position P11 at phase ⁇ 1
  • the second engaging member 22 starts moving toward the second engaging position P21 at phase ⁇ 2, which is a phase delayed from phase ⁇ 1.
  • the first engaging member 12 reaches the first engaging position P11 at phase ⁇ 3
  • the second engaging member 22 reaches the second engaging position P21 at phase ⁇ 4, which is a phase delayed from phase ⁇ 3.
  • first cam mechanism 7 and the second cam mechanism 8 are configured to move the first engaging member 12 from the first release position P12 to the first engaging position P11 and to move the second engaging member 22 from the second release position P22 to the second engaging position P21, such that the second engaging member 22 moves slower than the first engaging member 12.
  • the movement path of the first engaging member 12 from the first release position P12 to the first engaging position P11 (in this embodiment, the movement path along the axial direction L, the same below) is defined as the first movement path, and the ratio of the movement distance of the first engaging member 12 from the first release position P12 along the first movement path to the entire length of the first movement path is defined as the movement progress of the first engaging member 12.
  • the movement path of the second engaging member 22 from the second release position P22 to the second engaging position P21 is defined as the second movement path, and the ratio of the movement distance of the second engaging member 22 from the second release position P22 along the second movement path to the entire length of the second movement path is defined as the movement progress of the second engaging member 22.
  • the second engaging member 22 moves slower than the first engaging member 12 so that the degree of movement of the second engaging member 22 is smaller than the degree of movement of the first engaging member 12 at each point in time.
  • the first engagement member 12 moves from the first release position P12 to the first engagement position P11 between phase ⁇ 1 and phase ⁇ 3, and the second engagement member 22 moves from the second release position P22 to the second engagement position P21 between phase ⁇ 2 and phase ⁇ 4.
  • the first period during which the first engagement member 12 moves from the first release position P12 to the first engagement position P11 overlaps with the second period during which the second engagement member 22 moves from the second release position P22 to the second engagement position P21.
  • the first period and the second period overlap such that the first period starts earlier than the second period and ends earlier than the second period.
  • the first cam follower 72 guided by the first cam groove 71 and the second cam follower 82 guided by the second cam groove 81 are at the same position in the circumferential direction C (see FIG. 3). Therefore, the section for moving the first engaging member 12 in the first cam groove 71 from the first release position P12 to the first engaging position P11 (here, the section corresponding to the phases ⁇ 1 to ⁇ 3 in the first cam groove 71) is misaligned in the circumferential direction C from the section for moving the second engaging member 22 in the second cam groove 81 from the second release position P22 to the second engaging position P21 (here, the section corresponding to the phases ⁇ 2 to ⁇ 4 in the second cam groove 81).
  • the operation mode of the vehicle drive device 100 is the charging mode (PC).
  • the operation mode of the vehicle drive device 100 is the first EV mode (EV1) or the first HV mode (HV1) depending on the engagement state of the disconnection engagement mechanism K0.
  • the operation mode of the vehicle drive device 100 is the eTC mode (eTC).
  • the operation mode of the vehicle drive device 100 is the reverse mode (REV).
  • the operation mode of the vehicle drive device 100 is the second EV mode (EV2) or the second HV mode (HV2) depending on the engagement state of the disconnection engagement mechanism K0.
  • FIG. 5 is a time chart showing the case where the first engagement member 12 moves from the first release position P12 to the first engagement position P11 and the second engagement member 22 moves from the second release position P22 to the second engagement position P21.
  • the time chart in FIG. 5 shows the changes over time in the output torque of the rotating electric machine MG (see “rotating electric torque” in FIG. 5), the rotational position of the shift drum 6 based on the circumferential direction C positions of the first cam groove 71 and the second cam groove 81 (see “shift drum phase” in FIG. 5), the axial direction L position of the first engagement member 12 (see “first engagement member stroke position” in FIG. 5), and the axial direction L position of the second engagement member 22 (see “second engagement member stroke position” in FIG. 5) when the shift drum 6 rotates in a range corresponding to the phase ⁇ 0 to the phase ⁇ 4.
  • the output torque of the rotating electric machine MG is zero.
  • the shift drum 6 is in a rotational position corresponding to the phase ⁇ 0.
  • the first engagement member 12 is in the third engagement position P31, and the second engagement member 22 is in the second release position P22.
  • the shift drum 6 starts to rotate.
  • the first engagement member 12 moves from the third engagement position P31 toward the first release position P12.
  • the first engagement member 12 reaches the first release position P12.
  • the first engagement failure region A11 is a region where the first engagement member 12 cannot move to the first engagement position P11 due to getting caught or the like, and the first engagement mechanism C1 may enter a state of engagement failure.
  • the shift drum 6 stops rotating. Accordingly, between time t4 and time t5, the first engagement member 12 is maintained at a constant position within the first engagement failure region A11, and the second engagement member 22 is maintained at a constant position.
  • the shift drum 6 starts rotating again. Accordingly, the first engaging member 12 moves again toward the first engaging position P11, and the second engaging member 22 moves again toward the second engaging position P21. Then, at time t6, the first engaging member 12 moves out of the first engagement failure region A11 and into the first engagement region A12. Also, at time t6, the second engaging member 22 is in the second engagement failure region A21.
  • the first engagement region A12 is a region that includes the first engagement position P11 and a position near the first engagement position P11, and is a region where torque transmission is properly performed between the first engaged member 11 and the first engaging member 12.
  • the second engagement failure region A21 is a region where the second engaging member 22 cannot move to the second engagement position P21 due to being caught or the like, and the second engagement mechanism C2 may be in a state of engagement failure.
  • the shift drum 6 rotates further, the first engagement member 12 moves further toward the first engagement position P11, and the second engagement member 22 moves further toward the second engagement position P21. Thereafter, the shift drum 6 stops rotating between time t7 and time t8. Accordingly, between time t7 and time t8, the first engagement member 12 is maintained at a fixed position within the first engagement region A12, and the second engagement member 22 is maintained at a fixed position within the second engagement failure region A21.
  • the shift drum 6 starts rotating again. Accordingly, the first engaging member 12 moves again toward the first engaging position P11, and the second engaging member 22 moves again toward the second engaging position P21. Then, at time t9, the first engaging member 12 reaches the first engaging position P11. Also, at time t9, the second engaging member 22 moves out of the second engagement failure region A21 and into the second engagement region A22. At this time, the shift drum 6 is in a rotational position corresponding to the phase ⁇ 3.
  • the second engagement region A22 is a region that includes the second engaging position P21 and a position near the second engaging position P21, and is a region in which torque is appropriately transmitted between the second engaged member 21 and the second engaging member 22.
  • the shift drum 6 rotates further, the first engagement member 12 is maintained at the first engagement position P11, and the second engagement member 22 moves further toward the second engagement position P21. Then, at time t10, the second engagement member 22 reaches the second engagement position P21. Also, at time t10, the shift drum 6 stops rotating.
  • the rotating electric machine MG is controlled to alternately output positive torque and negative torque.
  • This control is executed to rotate the first engaging member 12 relative to the first engaged member 11 by the output torque of the rotating electric machine MG to eliminate the misengagement state when the first engaging mechanism C1 is in a misengagement state, and to rotate the second engaging member 22 relative to the second engaged member 21 by the output torque of the rotating electric machine MG to eliminate the misengagement state when the second engaging mechanism C2 is in a misengagement state.
  • the engagement device 10 has the following features: A first engagement mechanism C1 of a meshing type; A meshing type second engagement mechanism C2; A drive device D that drives the first engagement mechanism C1 and the second engagement mechanism C2,
  • the first engagement mechanism C1 includes a first engaged member 11, and a first engaging member 12 that moves between a first engagement position P11 where the first engaged member 11 is engaged and a first release position P12 where the engagement with the first engaged member 11 is released
  • the second engagement mechanism C2 includes a second engaged member 21, and a second engaging member 22 that moves between a second engagement position P21 where the second engaged member 21 engages with the second engaged member 21 and a second release position P22 where the engagement with the second engaged member 21 is released
  • the driving device D is A shift drum 6 that is rotationally driven by a drive source 9; a first cam mechanism 7 that converts the rotational motion of the shift drum 6 into linear motion and transmits the linear motion to a first engagement member 12;
  • a second cam mechanism 8 that converts the rotational motion of the shift drum 6 into linear
  • the first engagement member 12 of the first engagement mechanism C1 moves between the first engagement position P11 and the first release position P12 via the first cam mechanism 7
  • the second engagement member 22 of the second engagement mechanism C2 moves between the second engagement position P21 and the second release position P22 via the second cam mechanism 8.
  • the timing at which the first engagement member 12 moves from the first release position P12 to the first engagement position P11 and the timing at which the second engagement member 22 moves from the second release position P22 to the second engagement position P21 are shifted from each other.
  • the first engagement member 12 and the second engagement member 22 are configured to be movable in the axial direction L.
  • the shift drum 6 is formed in a cylindrical shape.
  • the second axis A2, which is the rotation axis of the shift drum 6, is arranged parallel to the first axis A1, which is the axis on which the first engagement mechanism C1 is arranged,
  • the first cam mechanism 7 includes a first cam groove 71 provided on the outer peripheral surface of the shift drum 6, the position of which in the axial direction L changes depending on the position of the outer peripheral surface in the circumferential direction C, a first cam follower 72 guided by the first cam groove 71, and a first connecting member 73 that links the movement of the first cam follower 72 in the axial direction L with the movement of the first engagement member 12 in the axial direction L.
  • the second cam mechanism 8 includes a second cam groove 81 provided on the outer peripheral surface, the position of which in the axial direction L changes depending on the position in the circumferential direction C, a second cam follower 82 guided by the second cam groove 81, and a second connecting member 83 that links the movement of the second cam follower 82 in the axial direction L with the movement of the second engagement member 22 in the axial direction L,
  • the section for moving the first engaging member 12 in the first cam groove 71 from the first release position P12 to the first engagement position P11 and the section for moving the second engaging member 22 in the second cam groove 81 from the second release position P22 to the second engagement position P21 are misaligned in the circumferential direction C.
  • This configuration makes it possible to appropriately realize a configuration in which one of the first engaging member 12 and the second engaging member 22 moves slower than the other when the first engaging member 12 is moved from the first release position P12 to the first engaging position P11 and the second engaging member 22 is moved from the second release position P22 to the second engaging position P21.
  • the first engaged member 11 and the second engaged member 21 are configured to rotate integrally with each other.
  • the first engaged member 11, which is the engagement target of the first engaging member 12, and the second engaged member 21, which is the engagement target of the second engaging member 22, are in the same rotational position. This makes it easy for the first engaging mechanism C1 and the second engaging mechanism C2 to enter a state of poor engagement. Therefore, when moving the first engaging member 12 from the first release position P12 to the first engagement position P11 and moving the second engaging member 22 from the second release position P22 to the second engagement position P21, the above configuration in which one of the first engaging member 12 and the second engaging member 22 moves later than the other is effective.
  • the first engaged member 11 and the second engaged member 21 are disposed on opposite sides of one target gear Gt (here, the third gear G3) and are configured to rotate integrally with the target gear Gt.
  • This configuration makes it easier to make the diameters of the first engaged member 11 and the second engaged member 21 closer together. Therefore, it makes it easier to make the driving force for moving the first engaging member 12 that engages with the first engaged member 11 closer to the driving force for moving the second engaging member 22 that engages with the second engaged member 21.
  • the transmission shaft member TS which rotates integrally with the first distribution rotating element E1 (here, the sun gear SG) of the distribution differential gear mechanism SP, is rotatably supported by the case CS that houses the distribution differential gear mechanism SP via the first bearing B11.
  • the transmission shaft member TS is rotatably supported by the input member I via the second bearing B12.
  • the transmission shaft member TS is rotatably supported by the third gear G3 via the third bearing B13.
  • the transmission shaft member TS is rotatably supported by the fourth gear G4 via the fourth bearing B14.
  • the first bearing B11 and the second bearing B12 are ball bearings that receive a radial load.
  • the third bearing B13 and the fourth bearing B14 are needle roller bearings that receive a radial load.
  • the connecting member CM which rotates integrally with the second distribution rotating element E2 (here, the carrier CR) of the distribution differential gear mechanism SP, is rotatably supported by the third distribution rotating element E3 (here, the ring gear RG) of the distribution differential gear mechanism SP via the fifth bearing B2.
  • the fifth bearing B2 is a needle roller bearing that receives a radial load.
  • the number of bearings that support the first distribution rotating element E1 and the rotating element that rotates integrally with the first distribution rotating element E1 (here, the transmission shaft member TS) in the radial direction R is greater than the number of bearings that support the second distribution rotating element E2 and the rotating element that rotates integrally with the second distribution rotating element E2 (here, the connecting member CM) in the radial direction R.
  • the rotational resistance of the first distribution rotating element E1 and the rotating element that rotates integrally with the first distribution rotating element E1 is greater than the rotational resistance of the second distribution rotating element E2 and the rotating element that rotates integrally with the second distribution rotating element E2 (here, the connecting member CM).
  • the rotational resistance of a rotating element depends not only on the number of bearings that support the target rotating element as described above, but also on the number of other rotating elements against which the target rotating element slides.
  • the vehicle drive device 100 has The engagement device 10, An input member I drivingly connected to an internal combustion engine EG; An output member O drivingly connected to a wheel W; A rotating electric machine MG including a rotor RT; a distribution differential gear mechanism SP including a first distribution rotating element E1, a second distribution rotating element E2, and a third distribution rotating element E3, the first distribution rotating element E1 being drivingly connected to an input member I, and the third distribution rotating element E3 being drivingly connected to a rotor RT; A vehicle drive device 100 including a power transmission mechanism TM that transmits a driving force between a specific rotating member RS (here, a third gear G3) and an output member O,
  • the first engagement mechanism C1 is configured to connect and disconnect the power transmission between the second distribution rotating element E2 and the specific rotating member RS
  • the second engagement mechanism C2 is configured to connect and disconnect the power transmission between the first distribution rotating element E1 and the specific rotating member RS, the rotational resistance of the first distribution rotating element E1 and the rotating element (here, the
  • the rotational resistance of the first distribution rotating element E1 and the rotating elements rotating integrally therewith is greater than the rotational resistance of the second distribution rotating element E2 and the rotating elements rotating integrally therewith, so the first engaging member 12 and the first engaged member 11, which rotate relatively due to the rotation of the second distribution rotating element E2, tend to be configured to rotate more easily than the second engaging member 22 and the second engaged member 21, which rotate relatively due to the rotation of the first distribution rotating element E1.
  • both the first engagement mechanism C1 and the second engagement mechanism C2 are not in an engaged state, it is easy to appropriately execute a process to eliminate the poor engagement state by relatively rotating the first engaging member 12 and the first engaged member 11 of the first engagement mechanism C1, which is first to be engaged, using the driving force of the rotating electric machine MG input to the third distribution rotating element E3.
  • the driving force of the rotating electric machine MG input to the third distribution rotating element E3 rotates the second engagement member 22 and the second engaged member 21 of the second engagement mechanism C2 relative to each other, making it easier to properly execute a process to eliminate the misengagement state. Therefore, with this configuration, it is possible to properly execute a process to eliminate the misengagement state for both the first engagement mechanism C1 and the second engagement mechanism C2.
  • the first cam mechanism 7 is described as having the first cam groove 71, the first cam follower 72, and the first connecting member 73.
  • the present invention is not limited to such a configuration, and may be configured, for example, such that the outer peripheral surface of the shift drum 6 has irregularities instead of the first cam groove 71.
  • the second axis A2 which is the rotation axis of the shift drum 6, is arranged to intersect (for example, perpendicular to) the first axis A1, and the first cam follower 72 moves in a direction intersecting the second axis A2 (for example, in the axial direction L) in response to the irregularities.
  • the second cam mechanism 8 is described as having the first cam groove 71, the first cam follower 72, and the first connecting member 73.
  • the present invention is not limited to such a configuration, and may be configured, for example, such that the outer peripheral surface of the shift drum 6 has irregularities instead of the first cam groove 71.
  • the second axis A2 which is the rotation axis of the
  • the distribution differential gear mechanism SP is a single pinion type planetary gear mechanism
  • the first distribution rotating element E1 is a sun gear SG
  • the second distribution rotating element E2 is a carrier CR
  • the third distribution rotating element E3 is a ring gear RG.
  • the first distribution rotating element E1 may be a ring gear RG
  • the second distribution rotating element E2 is a carrier CR
  • the third distribution rotating element E3 is a sun gear SG.
  • the distribution differential gear mechanism SP may be a double pinion type planetary gear mechanism.
  • the first distribution rotating element E1 may be the sun gear SG
  • the second distribution rotating element E2 may be the ring gear RG
  • the third distribution rotating element E3 may be the carrier CR
  • the first distribution rotating element E1 may be the carrier CR
  • the second distribution rotating element E2 may be the ring gear RG
  • the third distribution rotating element E3 may be the sun gear SG.
  • the engagement device (10) comprises: A first engagement mechanism (C1) of an interlocking type; A second engagement mechanism (C2) of an interlocking type; An engagement device (10) comprising: a drive device (D) that drives the first engagement mechanism (C1) and the second engagement mechanism (C2),
  • the first engagement mechanism (C1) comprises a first engaged member (11), and a first engaging member (12) that moves between a first engagement position (P11) in which the first engaged member (11) engages with the first engaged member (11) and a first release position (P12) in which the engagement with the first engaged member (11) is released
  • the second engagement mechanism (C2) comprises a second engaged member (21), and a second engaging member (22) that moves between a second engagement position (P21) in which the second engaged member (21) engages with the second engaged member (21) and a second release position (P22) in which the engagement with the second engaged member (21) is released
  • the driving device (D) A shift drum (6) that is rotationally driven by a drive source (9); a first cam mechanism
  • the rotation of the shift drum (6) causes the first engagement member (12) of the first engagement mechanism (C1) to move between the first engagement position (P11) and the first release position (P12) via the first cam mechanism (7), and the second engagement member (22) of the second engagement mechanism (C2) to move between the second engagement position (P21) and the second release position (P22) via the second cam mechanism (8).
  • the timing at which the first engagement member (12) moves from the first release position (P12) to the first engagement position (P11) and the timing at which the second engagement member (22) moves from the second release position (P22) to the second engagement position (P21) are mutually shifted.
  • the first cam mechanism (7) includes a first cam groove (71) provided on an outer peripheral surface of the shift drum (6) and whose position in the axial direction (L) changes depending on the position of the outer peripheral surface in the circumferential direction (C), a first cam follower (72) guided by the first cam groove (71), and a first connecting member (73) that links a movement of the first cam follower (72) in the axial direction (L) with a movement of the first engagement member (12) in the axial direction (L), the second cam mechanism (8) comprises a second cam groove (8
  • This configuration makes it possible to appropriately realize a configuration in which one of the first engaging member (12) and the second engaging member (22) moves slower than the other when the first engaging member (12) is moved from the first release position (P12) to the first engaging position (P11) and the second engaging member (22) is moved from the second release position (P22) to the second engaging position (P21).
  • first engaged member (11) and the second engaged member (21) are configured to rotate integrally with each other.
  • the first engaged member (11), which is the engagement object of the first engaging member (12), and the second engaged member (21), which is the engagement object of the second engaging member (22), are in the same rotational position. Therefore, the first engaging mechanism (C1) and the second engaging mechanism (C2) are likely to be in a poorly engaged state. Therefore, when moving the first engaging member (12) from the first release position (P12) to the first engagement position (P11) and moving the second engaging member (22) from the second release position (P22) to the second engagement position (P21), the above configuration in which one of the first engaging member (12) and the second engaging member (22) moves later than the other is effective.
  • first engaged member (11) and the second engaged member (21) are arranged on opposite sides of a single target gear (Gt) and are configured to rotate integrally with the target gear (Gt).
  • This configuration makes it easy to make the diameters of the first engaged member (11) and the second engaged member (21) closer together. Therefore, it makes it easy to make the driving force for moving the first engaging member (12) that engages with the first engaged member (11) closer to the driving force for moving the second engaging member (22) that engages with the second engaged member (21).
  • the vehicle drive device (100) further includes: The above engagement device (10), an input member (I) drivingly connected to an internal combustion engine (EG); An output member (O) drivingly connected to a wheel (W); a rotating electric machine (MG) having a rotor (RT); a distribution differential gear mechanism (SP) comprising a first distribution rotating element (E1), a second distribution rotating element (E2), and a third distribution rotating element (E3), the first distribution rotating element (E1) being drivingly connected to the input member (I) and the third distribution rotating element (E3) being drivingly connected to the rotor (RT);
  • a vehicle drive device (100) including a power transmission mechanism (TM) that transmits a driving force between a specific rotating member (RS) and the output member (O),
  • the first engagement mechanism (C1) is configured to connect and disconnect power transmission between the second distribution rotating element (E2) and the specific rotating member (RS),
  • the second engagement mechanism (C2) is configured to connect and disconnect the power transmission between the first distribution rotating element (E1) and the specific rotating
  • the rotational resistance of the first distribution rotating element (E1) and the rotating elements rotating integrally therewith is greater than the rotational resistance of the second distribution rotating element (E2) and the rotating elements rotating integrally therewith, so the first engaging member (12) and the first engaged member (11), which rotate relatively due to the rotation of the second distribution rotating element (E2), tend to be configured to rotate more easily than the second engaging member (22) and the second engaged member (21), which rotate relatively due to the rotation of the first distribution rotating element (E1).
  • both the first engagement mechanism (C1) and the second engagement mechanism (C2) are not in an engaged state, it is easy to appropriately perform a process of relatively rotating the first engaging member (12) and the first engaged member (11) of the first engagement mechanism (C1) that is first engaged by the driving force of the rotating electric machine (MG) input to the third distribution rotating element (E3) to eliminate the poor engagement state.
  • the driving force of the rotating electric machine (MG) input to the third distribution rotating element (E3) rotates the second engagement member (22) and the second engaged member (21) of the second engagement mechanism (C2) relative to each other, making it easier to properly execute a process to eliminate the misengagement state. Therefore, with this configuration, it is possible to properly execute a process to eliminate the misengagement state for both the first engagement mechanism (C1) and the second engagement mechanism (C2).
  • the technology disclosed herein can be used in an engagement device that includes a first and second interlocking engagement mechanism and a drive device that drives them, and in a vehicle drive device that includes the same.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hybrid Electric Vehicles (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un dispositif d'entraînement, qui entraîne un premier mécanisme de mise en prise et un second mécanisme de mise en prise du type à engrènement, pourvu d'un tambour de changement de vitesse, d'un premier mécanisme de came qui convertit le mouvement de rotation du tambour de changement de vitesse en un mouvement linéaire et transmet le mouvement linéaire à un premier élément de mise en prise qui vient en prise avec un premier élément en prise et d'un second mécanisme de came qui convertit le mouvement de rotation du tambour de changement de vitesse en un mouvement linéaire et transmet le mouvement linéaire à un second élément de mise en prise qui vient en prise avec un second élément en prise. Le premier mécanisme de came et le second mécanisme de came sont conçus de telle sorte que, lorsque le premier élément de mise en prise est déplacé d'une première position de libération (P12) à une première position de mise en prise (P11) et que le second élément de mise en prise est déplacé d'une seconde position de libération (P22) à une seconde position de mise en prise (P21), l'un du premier élément de mise en prise et du second élément de mise en prise est déplacé plus tard que l'autre.
PCT/JP2024/001081 2023-01-27 2024-01-17 Dispositif de mise en prise et dispositif d'entraînement de véhicule le comprenant Ceased WO2024157852A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2023010905A JP2024106573A (ja) 2023-01-27 2023-01-27 係合装置、及びそれを備えた車両用駆動装置
JP2023-010905 2023-01-27

Publications (1)

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WO2024157852A1 true WO2024157852A1 (fr) 2024-08-02

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018154208A (ja) * 2017-03-16 2018-10-04 本田技研工業株式会社 ハイブリッド車両の駆動装置
WO2019111456A1 (fr) * 2017-12-04 2019-06-13 三菱自動車工業株式会社 Dispositif de commande de boîte-pont
JP2019173932A (ja) * 2018-03-29 2019-10-10 株式会社ユニバンス 変速機構

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018154208A (ja) * 2017-03-16 2018-10-04 本田技研工業株式会社 ハイブリッド車両の駆動装置
WO2019111456A1 (fr) * 2017-12-04 2019-06-13 三菱自動車工業株式会社 Dispositif de commande de boîte-pont
JP2019173932A (ja) * 2018-03-29 2019-10-10 株式会社ユニバンス 変速機構

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