[go: up one dir, main page]

WO2020105636A1 - Dispositif d'entraînement de véhicule - Google Patents

Dispositif d'entraînement de véhicule

Info

Publication number
WO2020105636A1
WO2020105636A1 PCT/JP2019/045280 JP2019045280W WO2020105636A1 WO 2020105636 A1 WO2020105636 A1 WO 2020105636A1 JP 2019045280 W JP2019045280 W JP 2019045280W WO 2020105636 A1 WO2020105636 A1 WO 2020105636A1
Authority
WO
WIPO (PCT)
Prior art keywords
engagement device
engagement
spline teeth
pair
friction
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/JP2019/045280
Other languages
English (en)
Japanese (ja)
Inventor
鳥居武史
岩瀬拓朗
中島啓甫
土井孝之
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 AW Co Ltd
Original Assignee
Aisin AW Co Ltd
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 AW Co Ltd filed Critical Aisin AW Co Ltd
Publication of WO2020105636A1 publication Critical patent/WO2020105636A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Images

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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • 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
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/08—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action
    • 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
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/12—Freewheels or freewheel clutches with hinged pawl co-operating with teeth, cogs, or the like
    • 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
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/10—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with one or more one-way clutches as an essential feature

Definitions

  • the present invention relates to a vehicle drive device.
  • Patent Document 1 discloses an example of a vehicle drive device having such a configuration.
  • the friction engagement device [brake] and the meshing engagement device [low one-way clutch 5] are arranged side by side in the axial direction.
  • One of the pair of friction plates [second friction plate 12] of the friction engagement device is supported by the tubular member [clutch drum 1], and the engagement portion [sprag or The roller] can be engaged with another member [inner race 7] connected to the tubular member.
  • the vehicle drive device An input member drivingly connected to the driving force source, An output member drivingly connected to the wheel, A frictional engagement device and a meshing engagement device provided in a power transmission path connecting the input member and the output member,
  • the friction engagement device has a pair of friction plates arranged side by side in the axial direction, and one of the pair of friction plates engages with a first spline tooth provided on the tubular member. Rotation is restricted by
  • the meshing type engagement device has an engagement portion, and the engagement portion is configured to engage and disengage with a second spline tooth provided on the tubular member, On the outer peripheral surface of the tubular member, the first spline teeth and the second spline teeth are integrally formed continuously in the axial direction.
  • the friction engagement device and the meshing engagement device each have a component that engages with the spline tooth (first spline tooth / second spline tooth), the outer peripheral surface of the tubular member is Only the spline teeth need be formed, there is no need to prepare separate parts. Therefore, the number of parts can be reduced.
  • the first spline teeth for the friction engagement device and the second spline teeth for the meshing engagement device are integrally formed continuously in the axial direction and shared, so that they are It can be collectively formed by processing. Therefore, the cost can be reduced.
  • rotary electric machine is used as a concept that includes both a motor (electric motor), a generator (generator), and a motor / generator that performs both functions of the motor and the generator as necessary.
  • drive connection means a state in which two rotating elements are connected so as to be able to transmit a driving force.
  • This concept includes a state in which two rotating elements are connected so as to rotate integrally, and 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 (shafts, gear mechanisms, belts, chains, etc.) that transmit rotation at the same speed or by changing speed, and a device that selectively transmits rotation and driving force (friction).
  • Engaging devices, intermeshing engaging devices, etc. may be included.
  • the vehicle drive device 1 of the present embodiment includes a rotating electric machine MG, and transmits the output torque of the rotating electric machine MG to the wheels W to drive the vehicle.
  • the rotary electric machine MG corresponds to the “driving force source”.
  • An internal combustion engine gasoline engine, diesel engine, or the like
  • the vehicle drive device 1 transmits the output torque of at least one of the internal combustion engine and the rotary electric machine MG to the wheels W to drive the vehicle. It may be.
  • both the internal combustion engine and the rotary electric machine MG correspond to the “driving force source”.
  • the vehicle drive device 1 includes a rotary electric machine MG, an output member O drivingly connected to the wheels W, a first planetary gear device PG1, and a second planetary gear device PG2.
  • the first planetary gear device PG1 and the second planetary gear device PG2 are provided in the order described in the power transmission path connecting the rotary electric machine MG and the output member O.
  • the vehicle drive device 1 includes a clutch C, a brake B, a first selectable one-way clutch (hereinafter, abbreviated as “first SOWC”) 60, a second selectable one-way clutch (similarly, “second SOWC”). It is abbreviated as ".”) 65.
  • the rotary electric machine MG, the output member O, the first planetary gear device PG1, the second planetary gear device PG2, the clutch C, the brake B, the first SOWC 60, and the second SOWC 65 are housed in the case 2 (see FIG. 5). ing.
  • the brake B corresponds to the “friction engagement device” and the clutch C corresponds to the “second friction engagement device”.
  • the rotary electric machine MG, the first planetary gear device PG1, the second planetary gear device PG2, and the output member O are arranged coaxially. Further, the rotary electric machine MG, the output member O, the second planetary gear device PG2, and the first planetary gear device PG1 are arranged side by side in the axial direction in the order described. Further, when the axis on which the rotary electric machine MG, the first planetary gear apparatus PG1, the second planetary gear apparatus PG2, and the output member O are arranged is the first axis, the second axis parallel to the first axis has the output differential. A dynamic gear device DF and an axle X are arranged. The output member O is drivably coupled to the pair of left and right wheels W via the output differential gear device DF and the pair of left and right axles X.
  • the rotary electric machine MG includes a stator St fixed to the case 2 and a rotor Ro rotatably supported with respect to the stator St.
  • the rotating electrical machine MG is electrically connected to a power storage device (not shown) such as a battery or a capacitor, and receives power from the power storage device to perform powering, or generate electric power generated by inertial force of a vehicle or the like.
  • the power is supplied to the power storage device and stored.
  • the rotor Ro is connected so as to rotate integrally with the rotor shaft 10.
  • the rotor shaft 10 corresponds to the “input member”.
  • the rotor shaft 10 is arranged so as to penetrate the output member O, the second planetary gear device PG2, and the first planetary gear device PG1 in the radial direction.
  • the first planetary gear device PG1 is composed of a single pinion type planetary gear mechanism.
  • the first planetary gear device PG1 includes a first sun gear S1, a first pinion gear P1, a first carrier CA1, and a first ring gear R1.
  • the order of the rotational speeds of the first sun gear S1, the first carrier CA1, and the first ring gear R1 is the order described.
  • the first sun gear S1 is selectively fixed to the case 2 by the brake B and the first SOWC 60.
  • the first ring gear R1 is drivingly connected to the rotary electric machine MG via the rotor shaft 10.
  • the first pinion gear P1 that meshes with both the first sun gear S1 and the first ring gear R1 is supported by the first carrier CA1.
  • the first carrier CA1 is drivingly connected to the output member O via the second planetary gear device PG2.
  • the first planetary gear device PG1 corresponds to the “planetary gear device”.
  • the first ring gear R1 corresponds to the "first rotating element”
  • the first carrier CA1 corresponds to the "second rotating element”
  • the first sun gear S1 corresponds to the "third rotating element”.
  • the second planetary gear device PG2 is composed of a single pinion type planetary gear mechanism.
  • the second planetary gear device PG2 includes a second sun gear S2, a second pinion gear P2, a second carrier CA2, and a second ring gear R2.
  • the order of rotation speeds of the second sun gear S2, the second carrier CA2, and the second ring gear R2 is the order described.
  • the second sun gear S2 is drivingly connected to the rotary electric machine MG via the first planetary gear device PG1.
  • the second ring gear R2 is selectively fixed to the case 2 by the second SOWC 65.
  • the second pinion gear P2 that meshes with both the second sun gear S2 and the second ring gear R2 is supported by the second carrier CA2.
  • the second carrier CA2 is drivingly connected to the output member O.
  • the sun gear forming member 31 on which the first sun gear S1 is formed is connected to the brake hub 56 via the sun gear connecting member 32.
  • the sun gear connecting member 32 is formed thicker than the brake hub 56.
  • the sun gear connecting member 32 corresponds to the “third rotating element connecting member”.
  • the sun gear forming member 31 is selectively fixed to the case 2 by the brake B supported by the brake hub 56 and the first SOWC 60.
  • the first carrier CA1 is coupled to the second sun gear S2 via the intermediate coupling member 33, and is drivingly coupled to the output member O via the second carrier CA2 and the carrier coupling member 34.
  • the ring gear forming member 35 on which the second ring gear R2 is formed is connected to the ring gear connecting member 40, and is selectively fixed to the case 2 by the second SOWC 65 supported by the ring gear connecting member 40.
  • the clutch C has a cylindrical clutch hub 51, a friction plate 52, and a piston 53.
  • the brake hub 56 of the brake B is also used as the clutch drum of the clutch C.
  • the clutch hub 51 is connected to the first carrier CA1.
  • the friction plates 52 include inner friction plates 52A and outer friction plates 52B that are paired and are alternately arranged in the axial direction.
  • the inner friction plate 52A is supported by the clutch hub 51.
  • the inner friction plate 52A has its inner peripheral portion engaged with the spline teeth 91 formed on the outer peripheral surface of the clutch hub 51, whereby rotation is restricted and the inner friction plate 52A is supported in a slidable manner in the axial direction.
  • the outer friction plate 52B is supported by a brake hub 56 that also serves as a clutch drum.
  • the outer friction plate 52B is supported in a state in which its rotation is regulated and axially slidable by engaging the outer peripheral portion thereof with the spline teeth 92 formed on the inner peripheral surface of the brake hub 56.
  • the piston 53 is driven by hydraulic pressure, presses the pair of friction plates 52 (the inner friction plate 52A and the outer friction plate 52B) into pressure contact, and integrally rotates the first sun gear S1 and the first carrier CA1.
  • the friction plate 52 corresponds to the “second friction plate”.
  • the spline teeth 92 correspond to "third spline teeth”.
  • the brake B has a cylindrical brake hub 56, a friction plate 57, and a piston 58.
  • the cylindrical surface portion 22 formed on the peripheral wall 21 of the case 2 functions as the brake drum of the brake B.
  • the brake hub 56 that also serves as a clutch drum is connected to the sun gear forming member 31.
  • the friction plates 57 include inner friction plates 57A and outer friction plates 57B that are paired and are alternately arranged in the axial direction.
  • the brake hub 56 corresponds to the “cylindrical member”.
  • the inner friction plate 57A is supported by the brake hub 56.
  • the inner friction plate 57A is supported in a state in which its rotation is restricted and axially slidable by engaging the inner peripheral portion thereof with the spline teeth 93 formed on the outer peripheral surface of the brake hub 56.
  • the outer friction plate 57B is supported by the cylindrical surface portion 22 that functions as a brake drum.
  • the outer friction plate 57B is supported in a state in which rotation is restricted and axially slidable by engaging the outer peripheral portion with the spline teeth 94 formed on the cylindrical surface portion 22.
  • the piston 58 is driven by hydraulic pressure, presses a pair of friction plates 57 (the inner friction plate 57A and the outer friction plate 57B) into pressure contact, and fixes the first sun gear S1 to the case 2.
  • the spline teeth 93 correspond to “first spline teeth”
  • the spline teeth 94 correspond to “fifth spline teeth”.
  • the first SOWC 60 has an outer race 61 and an engagement piece 62.
  • the engagement piece 62 corresponds to the “engagement portion”.
  • the outer race 61 includes a cylindrical main body 61A and an outer engagement portion 61B that projects radially outward from the main body 61A.
  • the outer race 61 also includes a holding portion 61C that holds the engagement piece 62 swingably.
  • the engagement piece 62 has a first engagement piece 62A and a second engagement piece 62B.
  • the first engaging piece 62A and the second engaging piece 62B forming a pair are provided so as to be inclined in opposite directions.
  • the first engagement piece 62A and the second engagement piece 62B are configured to be swingable in the radial direction around the base end portion held by the holding portion 61C by operating the switching lever 63 by the actuator. ing.
  • the outer race 61 of the first SOWC 60 is supported by the cylindrical surface portion 22 of the peripheral wall 21 of the case 2.
  • the outer race 61 is supported in a state in which its rotation is restricted by the outer engagement portion 61B on the outer peripheral portion thereof engaging with the spline teeth 95 formed on the cylindrical surface portion 22.
  • the spline tooth 95 corresponds to the “fourth spline tooth”.
  • the outer race 61 (holding portion 61C) is supported by the brake hub 56 from the inside in the radial direction.
  • Each of the pair of engagement pieces 62 (first engagement piece 62A and second engagement piece 62B) is in a state in which the whole is accommodated radially outside the innermost peripheral surface of the holding portion 61C (storage state; in FIG. 2).
  • the state of the second engaging piece 62B) and the state in which the tip portion projects radially inward from the innermost peripheral surface of the holding portion 61C (projected state; state of the first engaging piece 62A in FIG. 2) It is possible.
  • the pair of engagement pieces 62 (first engagement piece 62A and second engagement piece 62B) are in a protruding state with respect to each other in the circumferential direction with respect to the spline teeth 96 formed on the outer peripheral surface of the brake hub 56. It can be engaged from the opposite side.
  • the spline tooth 96 corresponds to the “second spline tooth”. Since the pair of engagement pieces 62 can directly engage with the spline teeth 96 formed on the brake hub 56 as described above, the first SOWC 60 is not provided with an inner race.
  • the first SOWC 60 has a lock state that prevents rotation of the first sun gear S1 and a free state that allows the first sun gear S1 to rotate bidirectionally depending on the presence or absence of mechanical engagement between the engagement piece 62 and the spline tooth 96. It is a kind of "interlocking type engagement device" capable of at least switching to the state.
  • the first SOWC 60 of the present embodiment can be further switched to a one-way state, and can be switched to a free state (upper stage in FIG. 4), a one-way state (middle stage in FIG. 4) and a locked state (lower stage in FIG. 4). ..
  • the free state is realized by disengaging both the pair of engaging pieces 62A and 62B from the spline teeth 96.
  • one of the pair of engagement pieces 62A and 62B (the engagement piece 62A in the illustrated example, but the engagement piece 62B may be used depending on the rotation direction to be regulated) is attached to the spline teeth 96. It is realized by engaging from one side in the circumferential direction.
  • the locked state is realized by the pair of engagement pieces 62A and 62B engaging with the spline teeth 96 from both sides in the circumferential direction.
  • the first SOWC 60 corresponds to the “mesh engagement device”.
  • the second SOWC 65 has an outer race 66 and an engagement piece 67.
  • the engagement piece 67 corresponds to the “engagement portion”.
  • the outer race 66 includes a cylindrical main body portion 66A and an outer engagement portion 66B protruding radially outward from the main body portion 66A.
  • the outer race 66 also includes a holding portion 66C that holds the engagement piece 67 in a swingable manner.
  • the engagement piece 67 has a first engagement piece 67A and a second engagement piece 67B.
  • the first engagement piece 67A and the second engagement piece 67B forming a pair are provided so as to be inclined in opposite directions.
  • the first engagement piece 67A and the second engagement piece 67B are configured to be swingable in the radial direction around the base end portion held by the holding portion 66C by operating the switching lever 68 by the actuator. ing.
  • the outer race 66 of the second SOWC 65 is supported by the cylindrical portion 27 of the intermediate support wall 26 of the case 2.
  • the outer race 66 is supported in a state where its rotation is restricted by the outer engagement portion 66B on the outer periphery thereof engaging the spline teeth 97 formed on the cylindrical portion 27.
  • the outer race 66 (holding portion 66C) is supported from the inside in the radial direction by the support portion 42 of the ring gear connecting member 40 described later.
  • the pair of engaging pieces 67 (the first engaging piece 67A and the second engaging piece 67B) are respectively in a state of being entirely housed outside in the radial direction with respect to the innermost peripheral surface of the holding portion 66C (stored state; in FIG. 3).
  • the state of the second engaging piece 67B) and the state in which the tip portion projects radially inward from the innermost peripheral surface of the holding portion 66C (projected state; state of the first engaging piece 67A in FIG. 3) It is possible.
  • the pair of engaging pieces 67 (the first engaging piece 67A and the second engaging piece 67B) are in a protruding state with respect to the spline teeth 98 formed on the intermediate cylindrical portion 45 of the ring gear connecting member 40. Engagement is possible from opposite sides in the circumferential direction. Since the pair of engaging pieces 67 can directly engage the spline teeth 98 formed on the intermediate cylindrical portion 45 in the protruding state as described above, the second SOWC 65 is not provided with the inner race.
  • the second SOWC 65 is a free state that allows the second ring gear R2 to rotate in both directions and a lock that blocks the rotation of the second ring gear R2 depending on the presence or absence of mechanical engagement between the engagement piece 67 and the spline teeth 98. It is a kind of "interlocking type engagement device" capable of at least switching to the state. Like the first SOWC 60, the second SOWC 65 of the present embodiment can be switched to the one-way state, and can be switched to the free state, the one-way state, and the locked state. The free state is realized by disengaging both the pair of engaging pieces 67 from the spline teeth 98.
  • the one-way state is realized by engaging one of the pair of engaging pieces 67 with the spline tooth 98 from one side in the circumferential direction.
  • the locked state is realized by the pair of engagement pieces 67 engaging the spline teeth 98 from both sides in the circumferential direction.
  • the first planetary gear device PG1 decelerates the rotation of the rotary electric machine MG that is input to the first ring gear R1 and outputs the rotation from the first carrier CA1 when the brake B is in the engaged state or the first SOWC 60 is in the one-way state or the locked state. (Deceleration stage). Further, the first planetary gear device PG1 outputs the rotation of the rotary electric machine MG input to the first ring gear R1 at the rotation speed as it is from the first carrier CA1 when the clutch C is engaged (direct connection stage). In this way, the first planetary gear device PG1 of the present embodiment is configured to be able to switch between a plurality of shift speeds (direct connection speed / reduction speed).
  • the second planetary gear device PG2 decelerates the rotation input from the first carrier CA1 to the second sun gear S2 via the intermediate coupling member 33 in the one-way state or the locked state of the second SOWC 65, and outputs it from the output member O. To do. Further, the second planetary gear device PG2 disconnects the wheel W from each component on the upstream side (rotary electric machine MG side) of the second planetary gear device PG2 in the power transmission path in the free state of the second SOWC 65.
  • the rotary electric machine MG, the output member O, the first planetary gear device PG1, the second planetary gear device PG2, the clutch C, the brake B, the first SOWC 60, and the second SOWC 65 are housed in the case 2.
  • the case 2 has a peripheral wall 21, an end support wall 24, and an intermediate support wall 26.
  • the peripheral wall 21 is formed in a tubular shape that covers the outer periphery of the rotary electric machine MG, the output member O, the first planetary gear device PG1, the second planetary gear device PG2, the brake B, and the first SOWC 60.
  • a cylindrical surface portion 22 having a cylindrical inner peripheral surface is formed in an end region on one side of the peripheral wall 21 in the axial direction.
  • the spline teeth 94 and the spline teeth 95 are formed on the cylindrical surface portion 22.
  • the spline teeth 94 and the spline teeth 95 are continuously and integrally formed in the axial direction.
  • the cylindrical surface portion 22 of the peripheral wall 21 is formed with “second shared spline teeth” that function as both the spline teeth 94 and the spline teeth 95.
  • the outer race 61 of the first SOWC 60 and the outer friction plate 57B of the brake B are commonly supported by the second shared spline teeth in a state of being aligned in the axial direction.
  • the end support wall 24 is formed in a plate shape that covers one end of the peripheral wall 21 in the axial direction (the side opposite to the rotary electric machine MG).
  • the case 2 also includes a second end support wall (not shown) that covers the other end (rotary electric machine MG side) of the peripheral wall 21 in the axial direction.
  • the intermediate support wall 26 is formed so as to extend radially between the output member O and the second planetary gear device PG2 in the axial direction as a whole.
  • the intermediate support wall 26 has a cylindrical cylindrical portion 27 protruding in the axial direction.
  • the cylindrical portion 27 is formed so as to project from the intermediate support wall 26 toward the second planetary gear device PG2 side.
  • the output member O, the second SOWC 65, the second planetary gear device PG2, the first planetary gear device PG1, the first SOWC 60, the clutch C, and the brake B are coaxially arranged. These are arranged side by side in the axial direction in the order described. As shown in FIGS. 5 and 6, on the end support wall 24 side of the first planetary gear device PG1 and the second planetary gear device PG2, the first SOWC 60 and the brake B are arranged side by side in the axial direction, and the clutch It is arranged radially outside of C.
  • the clutch C is arranged on the radially inner side of the brake hub 56 also serving as the clutch drum, and the first SOWC 60 and the brake B are arranged on the radially outer side of the brake hub 56.
  • the spline teeth 93 and the spline teeth 96 are integrally formed continuously on the outer peripheral surface of the brake hub 56 in the axial direction.
  • first shared spline teeth that function as both the spline teeth 93 and the spline teeth 96 are formed.
  • the outer race 61 of the first SOWC 60 and the outer friction plate 57B of the brake B are commonly supported by the first shared spline teeth in a state of being aligned in the axial direction, and the engagement piece 62 of the first SOWC 60 swings. Then, when they are in a protruding state, they can be engaged.
  • the second carrier CA is connected to the output member O via the carrier connecting member 34 on the intermediate support wall 26 side of the first planetary gear device PG1 and the second planetary gear device PG2. ing.
  • the carrier connecting member 34 is formed as a hollow shaft having a larger diameter than the rotor shaft 10, and the rotor shaft 10 penetrates the inside thereof.
  • the output member O is formed as a hollow shaft having a diameter larger than that of the carrier connecting member 34, the rotor shaft 10 passes through the inside thereof, and one end of the carrier connecting member 34 is inserted therein.
  • the output member O has a cylindrical main body portion 71 on which an output gear 72 is formed, and a cylindrical cylindrical portion 73 projecting in the axial direction from the main body portion 71.
  • the output gear 72 is formed in the central region of the outer peripheral surface of the main body 71.
  • the cylindrical portion 73 is formed so as to project from the main body portion 71 toward the second planetary gear device PG2 side in the axial direction.
  • the cylindrical portion 73 is formed to have a smaller diameter than the main body portion 71.
  • the output member O is formed in a stepped cylindrical shape in which the diameter gradually decreases from the central region where the output gear 72 is formed toward the distal end side of the cylindrical portion 73.
  • the output member O is supported in the radial direction in a rotatable state with respect to the case 2 (intermediate support wall 26) by bearings 81 fitted to the outer peripheral surface of the main body 71 on both sides of the output gear 72.
  • the ring gear forming member 35 on which the second ring gear R2 is formed is connected to the ring gear connecting member 40.
  • the ring gear forming member 35 is supported by the intermediate support wall 26 via at least the ring gear connecting member 40.
  • the ring gear connecting member 40 is connected to the ring gear forming member 35 and rotates integrally with the ring gear forming member 35 (and the second ring gear R2).
  • the ring gear connecting member 40 has a radially extending portion 41 and a supporting portion 42.
  • the radially extending portion 41 is formed so as to extend in the radial direction from the ring gear forming member 35.
  • the radial extending portion 41 is generally formed in a stepped disc shape in which the diameter gradually decreases from the second planetary gear device PG2 side toward the output member O side.
  • the radially extending portion 41 includes an outer cylindrical portion 43, an outer annular plate portion 44, an intermediate cylindrical portion 45, an intermediate annular plate portion 46, an inner cylindrical portion 47, and an inner annular portion. And a plate-shaped portion 48. These are integrally formed.
  • the outer cylindrical portion 43 is formed in a cylindrical shape, and is connected to the ring gear forming member 35 so as to rotate integrally with the ring gear forming member 35 at the end portion on the second planetary gear device PG2 side.
  • the outer annular plate-shaped portion 44 is formed in an annular plate shape, and extends downward from the end of the outer cylindrical portion 43 on the side of the intermediate support wall 26.
  • the intermediate cylindrical portion 45 is formed in a cylindrical shape, and extends from the lower end portion of the outer annular plate portion 44 toward the intermediate support wall 26 side in the axial direction.
  • the intermediate annular plate-shaped portion 46 is formed in an annular plate shape, and extends downward from the end of the intermediate cylindrical portion 45 on the intermediate support wall 26 side.
  • the inner cylindrical portion 47 is formed in a cylindrical shape, and extends from the lower end of the intermediate annular plate portion 46 to both sides in the axial direction.
  • the inner cylindrical portion 47 projects to both the output member O side and the second planetary gear device PG2 side in the axial direction.
  • the inner annular plate-shaped portion 48 is formed in an annular plate shape and extends downward from the vicinity of the end portion of the inner cylindrical portion 47 on the second planetary gear device PG2 side.
  • the ring gear connecting member 40 (and the ring gear forming member 35 and the second ring gear R2) is supported by the bearing 82 in the radial direction in a rotatable state with respect to the output member O.
  • the ring gear coupling member 40 and the output member O have a portion that overlaps when viewed in the radial direction, and the bearing 82 is arranged between the overlapping portions in the radial direction.
  • the inner cylindrical portion 47 of the ring gear coupling member 40 and the cylindrical portion 73 of the output member O are arranged so as to overlap with each other when viewed in the radial direction, and the inner peripheral surface of the inner cylindrical portion 47 and the cylinder.
  • the bearing 82 is arranged between the outer peripheral surface of the shaped portion 73 and the outer peripheral surface.
  • the ring gear coupling member 40 is radially supported by the bearing 82 in a rotatable state with respect to the output member O.
  • the bearing 82 is arranged on the second planetary gear device PG2 side in the axial direction with respect to the main body 71 of the output member O. Further, the bearing 82 is arranged on the side of the second planetary gear device PG2 in the axial direction with respect to the bearing 81 that rotatably supports the output member O with respect to the case 2 (the intermediate support wall 26). Further, the bearing 82 is arranged radially inward of the bearing 81.
  • the ring gear coupling member 40 is axially supported by the bearing 83 in a rotatable state with respect to the case 2 (intermediate support wall 26).
  • the bearing 83 is arranged between the radially inner end of the intermediate support wall 26 and the intermediate annular plate-shaped portion 46 of the ring gear coupling member 40 in the axial direction.
  • the bearing 83 is arranged at a position overlapping the output gear 72 and the bearing 81 when viewed in the axial direction.
  • the bearing 83 is arranged at a position overlapping the inner cylindrical portion 47, the bearing 82, and the cylindrical portion 73 when viewed in the radial direction.
  • a bearing 84 is arranged axially between the inner ring-shaped plate portion 48 of the ring gear connecting member 40 and the flange portion of the carrier connecting member 34.
  • the support portion 42 provided on the ring gear coupling member 40 is a portion that supports the second SOWC 65.
  • the support portion 42 is provided on the outer surface of the intermediate cylindrical portion 45 of the radial extension portion 41 that constitutes the ring gear coupling member 40.
  • the support portion 42 is arranged radially inward of the inner peripheral surface of the second ring gear R2.
  • the support surface of the second SOWC 65 in the support portion 42 is arranged radially inward of the outer peripheral surface of the second carrier CA2.
  • the cylindrical portion 27 is arranged outside the intermediate cylindrical portion 45 in the radial direction and at a position overlapping the intermediate cylindrical portion 45 in the radial direction.
  • the cylindrical portion 27 has a diameter slightly larger than that of the ring gear forming member 35, and the spline teeth 97 formed on the inner peripheral surface thereof overlap the ring gear forming member 35 in the axial direction.
  • the second SOWC 65 is supported on the inner surface of the cylindrical portion 27.
  • the outer engagement portion 66B of the outer race 66 engages with the spline teeth 97 formed on the inner peripheral surface of the cylindrical portion 27, and the holding portion 66C of the outer race 66 is formed on the intermediate cylindrical portion 45.
  • the spline teeth 98 are arranged so as to be supported by the spline teeth 98.
  • first SOWC 60 and the second SOWC 65 are switchable between the free state, the one-way state, and the locked state.
  • at least one of the first SOWC 60 and the second SOWC 65 may be configured to be able to switch only two states of the free state, the one-way state, and the locked state. ..
  • the first SOWC 60 and the second SOWC 65 are described as an example in which the outer races 61 and 66 and the pair of swingable engagement pieces 62 and 67 are provided.
  • the invention is not limited to such a configuration, and instead of at least one of the first SOWC 60 and the second SOWC 65, another type of meshing engagement device such as a dog clutch may be used.
  • the brake hub 56 of the brake B is also used as the clutch drum of the clutch C as an example.
  • the configuration is not limited to such a configuration, and the clutch drum and the brake hub 56 may be provided separately.
  • the configuration in which the first planetary gear device PG1 that can switch between the direct coupling stage and the reduction stage as the plurality of shift stages is provided as an example.
  • the first planetary gear device PG1 may be capable of switching between the direct coupling stage and the speed increasing stage as a plurality of shift stages.
  • the first planetary gear device PG1 may be capable of switching the shift speed to three or more.
  • the first planetary gear device PG1 may be a transmission device with a fixed transmission ratio.
  • the first planetary gear device PG1 may not be provided.
  • the spline teeth 94 and the spline teeth 95 are integrally formed on the cylindrical surface portion 22 of the peripheral wall 21 of the case 2 continuously in the axial direction as an example.
  • the spline teeth 94 and the spline teeth 95 may be formed separately.
  • the ring gear coupling member 40 is described as an example in which the bearing 82 supports the ring gear coupling member 40 in the radial direction with respect to the output member O.
  • the ring gear coupling member 40 may be supported in the radial direction with respect to the case 2 (the intermediate support wall 26) without being limited to such a configuration.
  • the configuration in which the support portion 42 provided on the ring gear coupling member 40 is arranged radially inward of the inner peripheral surface of the second ring gear R2 has been described as an example.
  • the support portion 42 may be arranged at the same radial position as the inner peripheral surface of the second ring gear R2, or may have a diameter larger than that of the inner peripheral surface of the second ring gear R2. It may be arranged outside in the direction.
  • the pair of engagement pieces 62 for switching the state of the first SOWC 60 (free state / one-way state / locked state) is swingable in the radial direction as an example.
  • the first SOWC 60 having a configuration in which the pair of engaging pieces 62 can swing in the axial direction may be used.
  • the sun gear connecting member 32 is formed thicker than the brake hub 56, and the brake hub 56 is supported by the case 2 via the thick sun gear connecting member 32 as an example. explained. However, without being limited to such a configuration, the sun gear connecting member 32 may be formed to have the same thickness as the brake hub 56, or the sun gear connecting member 32 may be formed to be thinner than the brake hub 56. Is also good.
  • the vehicle drive device preferably includes the following components.
  • a vehicle drive device (1) comprising: An input member (10) drivingly connected to a driving force source (MG); An output member (O) drivingly connected to the wheel (W), A friction engagement device (B) and a meshing engagement device (60) provided in a power transmission path connecting the input member (10) and the output member (O),
  • the friction engagement device (B) has a pair of friction plates (57) arranged side by side in the axial direction, and one of the pair of friction plates (57) is a tubular member (56). Rotation is restricted by engaging the provided first spline teeth (93),
  • the meshing type engagement device (60) has an engagement portion (62), and the engagement portion (62) with respect to the second spline tooth (96) provided on the tubular member (56). Configured to engage and disengage,
  • the first spline tooth (93) and the second spline tooth (96) are integrally formed on the outer peripheral surface of the tubular member (56) continuously in the axial direction.
  • both the friction engagement device (B) and the meshing engagement device (60) engage the spline teeth (first spline teeth (93) / second spline teeth (96)). Since it has parts, it is only necessary to form spline teeth on the outer peripheral surface of the tubular member (56), and it is not necessary to prepare separate parts. Therefore, the number of parts can be reduced. Moreover, the first spline teeth (93) for the friction engagement device (B) and the second spline teeth (96) for the meshing engagement device (60) are integrally formed continuously in the axial direction. Since they are shared and shared, they can be collectively formed by a single processing. Therefore, the processing cost can be kept low and the cost can be reduced.
  • the engagement portion (62) has a pair of engagement pieces (62) engageable with the second spline tooth (96) from opposite sides in the circumferential direction
  • the meshing type engagement device (60) has a locked state realized by a pair of the engagement pieces (62) engaged with the second spline tooth (96) from both sides in the circumferential direction, and a pair of engagement states.
  • a one-way state in which one of the engagement pieces (62) is engaged with the second spline tooth (96) from one side in the circumferential direction, and a pair of the engagement pieces (62). It is preferable that at least two states of a free state, which is realized by disengaging both of them from the second spline teeth (96), can be switched.
  • the locked state at least two of the locked state, the one-way state, and the free state can be easily achieved by simply controlling the postures of the pair of engagement pieces (62) of the meshing engagement device (60).
  • the rotating members on both sides of the meshing engagement device (60) rotate at the same speed
  • the rotating members on both sides of the meshing engagement device (60) rotate at their relative rotational speeds.
  • the rotary members rotate at the same speed or rotate relative to each other
  • the free state the rotary members on both sides of the meshing type engagement device (60) rotate relative to each other.
  • the engagement type engagement device (60) is preferably a selectable one-way clutch.
  • a pair of the engagement pieces (62) swing in the radial direction to switch between engagement and non-engagement with the second spline teeth (96).
  • a second friction engagement device (C) different from the friction engagement device (B) provided in the power transmission path has a pair of second friction plates (52) arranged side by side in the axial direction, and one of the pair of second friction plates (52) is the third. Rotation is restricted by engaging the spline teeth (92), The third spline teeth (92) are preferably formed on the inner peripheral surface of the tubular member (56).
  • the third spline tooth (92) for the second friction engagement device (C) is the same as the shared first spline tooth (93) and second spline tooth (96), and is a cylinder. Formed into a strip-shaped member (56). Although it is divided into an outer peripheral surface and an inner peripheral surface, it can be formed by continuous processing of a single cylindrical member (56). For example, compared to a configuration in which the third spline tooth (92) is formed as a member different from the tubular member (56), the structure can be simplified and the processing cost can be kept low.
  • the meshing engagement device (60) has an outer race (61), and an outer peripheral portion of the outer race (61) is configured to engage with the fourth spline tooth (95).
  • Rotation is restricted by engaging the other of the pair of friction plates (57) of the friction engagement device (B) with the fifth spline tooth (94),
  • the fourth spline tooth (95) and the fifth spline tooth (94) are integrally formed on the cylindrical surface portion (22) formed on the inner surface of the case (2) continuously in the axial direction.
  • the friction engagement device (B) and the meshing engagement device (60) both engage the spline teeth (the fourth spline teeth (95) / the fifth spline teeth (94)). Since it has components, it is only necessary to form spline teeth on the cylindrical surface portion (22) formed on the inner surface of the case (2), and it is not necessary to separately prepare a separate component for either one. Therefore, the number of parts can be reduced. Moreover, the fourth spline tooth (95) for the friction engagement device (B) and the fifth spline tooth (94) for the meshing type engagement device (60) are integrally formed continuously in the axial direction. Since they are shared and shared, they can be collectively formed by a single processing. Therefore, the processing cost can be kept low and the cost can be reduced.
  • a case (2) accommodating the friction engagement device (B) and the meshing engagement device (60); A first rotating element (R1) drivingly connected to the input member (10), a second rotating element (CA1) drivingly connected to the output member (0), the friction engagement device (B) and the A planetary gear device (PG1) having a third rotating element (S1) selectively fixed to the case (2) by at least one of the meshing engagement devices (60); A third rotating element connecting member (32) which is connected to the third rotating element (S1) and integrally rotates with the third rotating element (S1), It is preferable that the tubular member (56) is supported by the case (2) via the third rotary element connecting member (32) that is thicker than the tubular member (56). ..
  • the tubular member (56) can be stably supported via the thick third rotating element connecting member (32).
  • the friction engagement device (B) and the meshing engagement device (60) can be properly supported.
  • the vehicle drive device according to the present disclosure may have at least one of the effects described above.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Hybrid Electric Vehicles (AREA)

Abstract

Dans un dispositif d'entraînement de véhicule (1), un dispositif de mise en prise par frottement (B) et un dispositif de mise en prise de type à engrènement (60) sont disposés dans un trajet de transmission de puissance motrice qui relie une source de puissance d'entraînement et des roues de véhicule. Une plaque (57A) d'une paire de plaques de frottement (57) du dispositif de mise en prise par frottement (B) vient en prise avec des premières dents cannelées (93) d'un élément cylindrique (56), et une partie de mise en prise du dispositif de mise en prise de type à engrènement (60) vient en prise avec des secondes dents cannelées (96) de l'élément cylindrique (56) et se sépare de celles-ci. Les premières dents cannelées (93) et les secondes dents cannelées (96) sont formées d'un seul tenant dans la surface périphérique externe de l'élément cylindrique (56) de façon continue dans la direction axiale.
PCT/JP2019/045280 2018-11-19 2019-11-19 Dispositif d'entraînement de véhicule Ceased WO2020105636A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2018-216718 2018-11-19
JP2018216718 2018-11-19

Publications (1)

Publication Number Publication Date
WO2020105636A1 true WO2020105636A1 (fr) 2020-05-28

Family

ID=70774522

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2019/045280 Ceased WO2020105636A1 (fr) 2018-11-19 2019-11-19 Dispositif d'entraînement de véhicule

Country Status (1)

Country Link
WO (1) WO2020105636A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023135870A1 (fr) * 2022-01-13 2023-07-20 日本精工株式会社 Dispositif de commutation de chemin de transmission de puissance et transmission à deux rapports
JPWO2023166802A1 (fr) * 2022-03-01 2023-09-07

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02138255U (fr) * 1989-04-24 1990-11-19
JPH07197949A (ja) * 1993-12-28 1995-08-01 Dainatsukusu:Kk 一方向クラッチ機能を具えた摩擦係合装置
JP2002039224A (ja) * 2000-07-31 2002-02-06 Honda Motor Co Ltd ワンウェイクラッチ
JP2006250351A (ja) * 2005-03-10 2006-09-21 Ford Global Technologies Llc 変速機の遊星歯車装置用キャリア組立体
JP2009542990A (ja) * 2006-07-07 2009-12-03 ボーグワーナー・インコーポレーテッド ２つのバッキングプレートを備える、ローラ、スプラグまたはラチェット型一方向クラッチ
JP2012219950A (ja) * 2011-04-12 2012-11-12 Nsk Ltd 無段変速装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02138255U (fr) * 1989-04-24 1990-11-19
JPH07197949A (ja) * 1993-12-28 1995-08-01 Dainatsukusu:Kk 一方向クラッチ機能を具えた摩擦係合装置
JP2002039224A (ja) * 2000-07-31 2002-02-06 Honda Motor Co Ltd ワンウェイクラッチ
JP2006250351A (ja) * 2005-03-10 2006-09-21 Ford Global Technologies Llc 変速機の遊星歯車装置用キャリア組立体
JP2009542990A (ja) * 2006-07-07 2009-12-03 ボーグワーナー・インコーポレーテッド ２つのバッキングプレートを備える、ローラ、スプラグまたはラチェット型一方向クラッチ
JP2012219950A (ja) * 2011-04-12 2012-11-12 Nsk Ltd 無段変速装置

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023135870A1 (fr) * 2022-01-13 2023-07-20 日本精工株式会社 Dispositif de commutation de chemin de transmission de puissance et transmission à deux rapports
JP7384319B1 (ja) * 2022-01-13 2023-11-21 日本精工株式会社 動力伝達経路切換装置および２段変速機
JPWO2023166802A1 (fr) * 2022-03-01 2023-09-07
WO2023166802A1 (fr) * 2022-03-01 2023-09-07 ジヤトコ株式会社 Dispositif
JP7551272B2 (ja) 2022-03-01 2024-09-17 ジヤトコ株式会社 装置

Similar Documents

Publication Publication Date Title
WO2020105635A1 (fr) Appareil d'entraînement de véhicule
JP5842998B2 (ja) 車両用変速機
US20150011347A1 (en) Vehicle drive device
US7998011B2 (en) Speed change apparatus
JP7019280B2 (ja) 動力伝達装置
JP2015066993A (ja) ハイブリッド駆動装置
WO2020105636A1 (fr) Dispositif d'entraînement de véhicule
JPWO2015105165A1 (ja) 自動変速機
JP2021162052A (ja) 車両用駆動伝達装置
CN108603573A (zh) 动力传递装置
JP7218732B2 (ja) 動力伝達装置
WO2018181557A1 (fr) Dispositif d'entraînement pour véhicule
JP2020085052A (ja) 車両用駆動装置
JP7619480B2 (ja) 係合装置
CN116194688A (zh) 车用驱动装置
JP2022169076A (ja) 車両用動力伝達装置
JP7708326B2 (ja) 変速機、及びそれを備えた車両用駆動伝達装置
JP2019049320A (ja) 車両用駆動装置
JP2021109581A (ja) 動力伝達装置
JP2024043033A (ja) 車両用駆動伝達装置
WO2024157852A1 (fr) Dispositif de mise en prise et dispositif d'entraînement de véhicule le comprenant
WO2025220730A1 (fr) Transmission à deux étages et dispositif d'entraînement de véhicule électrique
JP2024010429A (ja) 車両用駆動伝達装置
JP2025153080A (ja) 車両用駆動装置
JP2024050213A (ja) 車両用駆動伝達装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 19887702

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 19887702

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: JP