WO2022113709A1 - 噛み合いクラッチ機構及び2段変速装置 - Google Patents
噛み合いクラッチ機構及び2段変速装置 Download PDFInfo
- Publication number
- WO2022113709A1 WO2022113709A1 PCT/JP2021/040922 JP2021040922W WO2022113709A1 WO 2022113709 A1 WO2022113709 A1 WO 2022113709A1 JP 2021040922 W JP2021040922 W JP 2021040922W WO 2022113709 A1 WO2022113709 A1 WO 2022113709A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- gear
- clutch
- meshing
- cam
- clutch mechanism
- Prior art date
Links
- 230000007246 mechanism Effects 0.000 title claims abstract description 212
- 230000005540 biological transmission Effects 0.000 title claims abstract description 136
- 230000008878 coupling Effects 0.000 claims abstract description 43
- 238000010168 coupling process Methods 0.000 claims abstract description 43
- 238000005859 coupling reaction Methods 0.000 claims abstract description 43
- 239000007787 solid Substances 0.000 abstract 1
- 238000011161 development Methods 0.000 description 15
- 230000009471 action Effects 0.000 description 9
- 238000006243 chemical reaction Methods 0.000 description 8
- 230000002093 peripheral effect Effects 0.000 description 8
- 238000005096 rolling process Methods 0.000 description 6
- 238000001514 detection method Methods 0.000 description 4
- 230000009467 reduction Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 239000003638 chemical reducing agent Substances 0.000 description 2
- 230000006837 decompression Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000001172 regenerating effect Effects 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000009194 climbing Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
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
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
- F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
-
- 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
- F16D11/14—Clutches in which the members have interengaging parts with clutching members movable only axially
-
- 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
- F16D13/00—Friction clutches
- F16D13/22—Friction clutches with axially-movable clutching members
- F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
-
- 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
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/46—Gearings having only two central gears, connected by orbital gears
-
- 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
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/64—Gearings having three or more central gears composed of a number of gear trains, the drive always passing through all the trains, each train having not more than one connection for driving another train
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K1/00—Arrangement or mounting of electrical propulsion units
- B60K2001/001—Arrangement or mounting of electrical propulsion units one motor mounted on a propulsion axle for rotating right and left wheels of this axle
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2200/00—Type of vehicle
- B60Y2200/90—Vehicles comprising electric prime movers
- B60Y2200/91—Electric vehicles
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2400/00—Special features of vehicle units
- B60Y2400/40—Actuators for moving a controlled member
- B60Y2400/405—Electric motors actuators
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2400/00—Special features of vehicle units
- B60Y2400/42—Clutches or brakes
- B60Y2400/424—Friction clutches
- B60Y2400/4244—Friction clutches of wet type, e.g. using 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
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
- F16D2023/123—Clutch actuation by cams, ramps or ball-screw mechanisms
-
- 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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H2061/2869—Cam or crank gearing
-
- 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
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H2063/3093—Final output elements, i.e. the final elements to establish gear ratio, e.g. dog clutches or other means establishing coupling to shaft
-
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0021—Transmissions for multiple ratios specially adapted for electric vehicles
-
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
-
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one sets of orbital gears
-
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
-
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2033—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with one engaging means
-
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means
-
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2064—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using at least one positive clutch, e.g. dog clutch
-
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2066—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using one freewheel mechanism
-
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2079—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches
- F16H2200/2082—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches one freewheel mechanisms
-
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2094—Transmissions using gears with orbital motion using positive clutches, e.g. dog clutches
-
- 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
- F16H3/087—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 characterised by the disposition of the gears
- F16H3/089—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 characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
-
- 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
-
- 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
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/46—Gearings having only two central gears, connected by orbital gears
- F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
- F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
- F16H3/54—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed
-
- 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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H61/32—Electric motors actuators or related electrical control means therefor
Definitions
- the present invention relates to a drive device, particularly a meshing clutch mechanism and a two-speed transmission.
- a two-speed transmission as shown in the conventional patent document 1 has been proposed.
- the planetary gear unit reduces or maintains the rotational speed of the motor at a constant speed.
- torque shortage occurs because it is necessary to temporarily remove the driving force in shifting.
- Patent Document 2 a two-speed transmission as shown in Patent Document 2 has been proposed.
- This two-speed transmission enhances power consumption efficiency by allocating a low-speed stage and a high-speed stage by de-energizing and energizing the electromagnetic coil.
- the one-way clutch is installed to prevent torque loss during shifting and to reduce the shifting shock that the driver can perceive.
- this two-speed transmission since a one-way clutch is installed, there is a problem that torque in the reverse direction at a low speed cannot be transmitted.
- the problem to be solved is that torque is cut off during shifting, while in a two-speed transmission that uses a one-way clutch in the low-speed stage to prevent torque running out, torque in the reverse direction at low-speed speed (hereinafter referred to as coast torque). It is a point that cannot be transmitted.
- the meshing clutch mechanism of the present invention makes it possible to easily switch between the one-way clutch function and the two-way clutch function of the first and second meshing clutches, so that the tooth surface for transmitting positive torque and the tooth for transmitting negative torque can be easily switched.
- the tooth surface having a surface and transmitting the negative torque meshes with the rotatably supported rotating body provided with a first meshing clutch having an inclination for disengaging by the negative torque and the first meshing clutch.
- a sleeve provided with a second meshing clutch and a first cam for the meshing, which is urged to release the meshing and is rotationally engaged and axially movably supported by a clutch hub fixed to the case side.
- a holding member that urges the sleeve to hold the release position of the first and second meshing clutches, and a second cam that engages with the first cam are provided by the cooperation of the first and second cams. It is characterized by being provided with a cam ring that converts a movement in a rotational direction into an axial movement and transmits it to the sleeve to lock the meshing so that it can be disengaged by a rotational drive, and a cam actuator that rotationally drives the cam ring.
- the present invention is a two-speed transmission device using the meshing clutch mechanism in order to suppress torque loss during shifting and to be able to transmit torque in the reverse direction at low speeds, and a sun gear that receives rotation input. It is provided with an internal gear that meshes with the sun gear via a planet pinion and a drive pinion for output while being rotatably supported by the internal gear and rotatably supporting the planet pinion.
- the friction clutch mechanism is interposed between the planet carrier and the internal gear and the planet carrier to adjust the coupling between the internal gear and the planet carrier by fastening, and the friction clutch mechanism is fastened to adjust the coupling. It is characterized by being equipped with a clutch actuator that adjusts the friction torque of the coupling.
- the meshing clutch mechanism of the present invention can easily switch between the one-way clutch function and the two-way clutch function of the first and second meshing clutches.
- the two-speed transmission of the present invention is capable of transmitting torque in both the drive and coast directions at low speeds.
- reverse torque transmission is possible when moving backward and when regenerating energy.
- the one-way clutch function With the one-way clutch function, there is no torque loss when shifting to the upper stage. Smooth shifting is possible.
- the meshing clutch mechanism in the low speed stage does not generate a loss due to drag torque unlike a friction clutch, and the efficiency increases.
- FIG. 3 is a schematic cross-sectional view of a skeleton according to the first embodiment, in which a part of the meshing clutch mechanism is omitted.
- FIG. 1 is a development cross-sectional view of a main part of the first and second meshing clutches in the circumferential direction according to the first embodiment.
- FIG. 1 is a development cross-sectional view of a main part in the circumferential direction in a state where the first and second meshing clutches are separated according to the first embodiment.
- FIG. 1 is a development cross-sectional view of a main part of the first and second cams in the circumferential direction according to the first embodiment.
- FIG. 1 is a development cross-sectional view of a main part in the circumferential direction when the first and second cams are operated according to the first embodiment.
- FIG. 1 is a development cross-sectional view of a main part in the circumferential direction of the first and second cams configured by the ball cam according to the first embodiment. According to the first embodiment, it is a development cross-sectional view of a main part in the circumferential direction at the time of operation of the first and second cams composed of ball cams.
- FIG. 2 is a schematic cross-sectional view of a skeleton according to a second embodiment, in which a part of the meshing clutch mechanism is omitted.
- FIG. 3 is a schematic cross-sectional view of a skeleton according to a third embodiment, in which a part of the two-speed transmission is omitted.
- FIG. 4 is a schematic cross-sectional view of a skeleton according to a fourth embodiment, in which a part of the two-speed transmission is omitted.
- FIG. 5 is a schematic cross-sectional view of a skeleton according to a fifth embodiment, in which a part of the two-speed transmission is omitted.
- FIG. 6 is a schematic cross-sectional view of a skeleton according to a sixth embodiment, in which a part of the two-speed transmission is omitted.
- FIG. 7 is a schematic cross-sectional view of a skeleton according to a seventh embodiment, in which a part of the two-speed transmission is omitted.
- FIG. 8 is a schematic cross-sectional view of a skeleton according to the eighth embodiment, in which a part of the two-speed transmission is omitted.
- 9 is a schematic cross-sectional view of a skeleton according to a ninth embodiment, in which a part of the two-speed transmission is omitted.
- the meshing clutch mechanism of the present invention has been realized as follows in order to make it possible to easily switch between the one-way clutch function and the two-way clutch function of the first and second meshing clutches.
- the tooth surface having a tooth surface for transmitting positive torque and a tooth surface for transmitting negative torque, and the tooth surface for transmitting negative torque is provided with a first meshing clutch having an inclination for disengaging by the negative torque and is rotatably supported.
- the rotating body is provided with a second meshing clutch that meshes with the first meshing clutch and a first cam for the meshing, and the clutch hub is urged to release the meshing and is fixed in the rotation direction to the case side.
- a cam ring provided with a cam, which converts rotational movement into axial movement by the cooperation of the first and second cams, transmits the clutch to the sleeve, and locks the mesh so that the clutch can be disengaged by rotational drive, and the cam ring is rotated. It was realized with a cam actuator to drive.
- the tooth surface having a tooth surface for transmitting positive torque and a tooth surface for transmitting negative torque, and the tooth surface for transmitting negative torque is provided with a clutch hub having a first meshing clutch having an inclination to disengage due to the negative torque.
- a rotating body that is rotatably fitted and supported by the torque transmission shaft and a second meshing clutch that meshes with the first meshing clutch are provided and urged to release the meshing and engages with the clutch hub in the rotational direction.
- a cam member that is movably supported in the axial direction has a first cam for the meshing, is arranged adjacent to the sleeve so as to be relatively rotatable and axial force can be transmitted, and is non-rotatably engaged with the case side, and the first cam member.
- a second cam that engages with one cam is provided so as to face the cam member, is supported by the clutch hub so as to be relatively rotatable, and is prevented from moving away from the cam member in the axial direction.
- the two-speed transmission of the present invention is a two-speed transmission using the meshing clutch mechanism in order to suppress torque loss during shifting and to be able to transmit torque in the reverse direction at low speeds, and is a rotation input.
- the sun gear that receives the torque the internal gear that meshes with the sun gear via the planet pinion, and the internal gear that constitutes the rotating body, and the internal gear that is rotatably supported relative to the internal gear to rotatably support the planet pinion and for output.
- a friction clutch mechanism provided between a planet carrier provided with a drive pinion, a friction clutch mechanism interposed between the internal gear and the planet carrier, and adjusting the coupling between the internal gear and the planet carrier by fastening, and the friction clutch mechanism. It was realized by providing a clutch actuator that adjusts the friction torque of the coupling by adjusting the fastening.
- the two-speed transmission using the meshing clutch mechanism includes a sun gear that receives a rotational input by the sun gear shaft, a third sun gear that is rotatably supported by the sun gear shaft, and a drive pinion for output.
- a planet pinion integrally including a sun gear shaft, a first gear that meshes with the sun gear, and a second gear that meshes with the third sun gear, and the planet pinion are rotatably supported to form the rotating body.
- a friction clutch mechanism which is interposed between the planet carrier and the planet carrier and the third sun gear shaft and which adjusts the coupling between the planet carrier and the third sun gear shaft by fastening, and the friction clutch mechanism. It can also be realized by providing a clutch actuator that adjusts the friction torque of the coupling by fastening the coupling.
- the two-speed transmission using the meshing clutch mechanism can also realize the rotation input to the sun gear from the motor via the drive gear and the driven gear.
- the two-speed transmission using the meshing clutch mechanism is provided with a pressing force adjusting means for causing the engagement to be performed between the clutch actuator and the friction clutch mechanism, and the pressing force adjusting means is relatively rotatable.
- the first differential gear and the second differential gear that are supported by the clutch and have different numbers of teeth, the torque cam that converts the relative rotation between the first differential gear and the second differential gear into axial thrust, and the first differential. It can also be realized by providing a clutch pinion that engages with the gear and the second differential gear and receives a rotation input from the clutch actuator, and a pressing member that receives the axial thrust converted by the torque cam to perform the fastening.
- the two-speed transmission using the meshing clutch mechanism is provided with a pressing force adjusting means for causing the engagement to be performed between the clutch actuator and the friction clutch mechanism, and the pressing force adjusting means is relatively rotatable.
- the first differential gear and the second differential gear that are supported by the clutch and have different numbers of teeth, the torque cam that converts the relative rotation between the first differential gear and the second differential gear into axial thrust, and the first differential.
- the clutch pinion that engages with the gear and the second differential gear and receives the rotation input from the clutch actuator, the elastic body that generates the pressing force for fastening, and the pressing force of the elastic body are used to perform the engagement. It can also be realized by providing a pressing force adjusting member that receives the axial thrust converted by the torque cam and reduces the pressing force of the elastic body.
- the two-speed transmission using the meshing clutch mechanism includes an input shaft provided with a low-speed drive gear and a high-speed drive gear to receive rotational input, a low-speed driven gear that meshes with the low-speed drive gear, and a high-speed gear that meshes with the high-speed drive gear.
- the gear is fixed to the input shaft and is provided with a friction clutch mechanism for adjusting the coupling between the input shaft and the high-speed drive gear rotatably provided on the input shaft, or rotatably provided on the output shaft and the output shaft. It can also be realized in a form provided with a friction clutch mechanism for adjusting the coupling between the high-speed driven gears and a clutch actuator for adjusting the friction torque of the coupling by adjusting the engagement of the friction clutch mechanism.
- the two-speed transmission using the meshing clutch mechanism is provided with a pressing force adjusting means for causing the engagement to be performed between the clutch actuator and the friction clutch mechanism, and the pressing force adjusting means is the engaging. It is provided with an elastic body that generates a pressing force for the purpose, and a pressing force adjusting member that receives the pressing force of the elastic body to perform the fastening and is coupled to the clutch actuator, and the clutch actuator is the pressing force adjusting member. It can also be realized in the form of adjusting the pressing force of the elastic body by driving.
- the two-speed transmission using the meshing clutch mechanism can rotate relative to the sun gear that receives the rotation input, the internal gear that meshes with the sun gear via the planet pinion, and the internal gear that constitutes the rotating body.
- a friction clutch that is interposed between the internal gear and the planet carrier and adjusts the coupling between the internal gear and the planet carrier by fastening the planet carrier that is supported by the planet carrier and rotatably supports the planet pinion. It can also be realized in a form including a mechanism, a clutch actuator that adjusts the friction torque of the coupling by adjusting the engagement of the friction clutch mechanism, and an output shaft that is coupled to the planet carrier and is arranged so as to project to the outside.
- the two-speed transmission using the meshing clutch mechanism includes a sun gear that receives a rotation input, a third sun gear having an output shaft that is projected to the outside, a first gear that meshes with the sun gear, and the third sun gear.
- a planet pinion integrally provided with a second gear to be meshed, a planet carrier that rotatably supports the planet pinion to form the rotating body, and an interposition between the planet carrier and the sun gear are fastened. It can also be realized in a form including a friction clutch mechanism for adjusting the coupling between the planet carrier and the sun gear, and a clutch actuator for adjusting the friction torque of the coupling by fastening the friction clutch mechanism.
- the two-speed transmission using the meshing clutch mechanism can also be realized by including a sensor for detecting the slip of the friction clutch mechanism and a controller for controlling the clutch actuator according to the detected slip.
- FIG. 1 is a schematic cross-sectional view of a skeleton according to the first embodiment, in which a part of the meshing clutch mechanism is omitted.
- FIG. 2 is a development cross-sectional view of a main part of the first and second meshing clutches in the circumferential direction.
- FIG. 3 is a development cross-sectional view of a main part in the circumferential direction in a state where the first and second meshing clutches are separated.
- FIG. 4 is a development cross-sectional view of a main part of the first and second cams in the circumferential direction.
- FIG. 5 is a development cross-sectional view of a main part in the circumferential direction when the first and second cams are operated.
- FIG. 1 is a schematic cross-sectional view of a skeleton according to the first embodiment, in which a part of the meshing clutch mechanism is omitted.
- FIG. 2 is a development cross-sectional view of a main part of the first and second meshing
- FIG. 6 is a development cross-sectional view of a main part of the first and second cams composed of ball cams in the circumferential direction.
- FIG. 7 is a development cross-sectional view of a main part in the circumferential direction when the first and second cams composed of ball cams are operated.
- the first meshing clutch mechanism 1002 which is the meshing clutch mechanism shown in FIG. 1, includes a first rotating body 101 which is a rotating body, a first sleeve 121 which is a sleeve, a holding member 139, a cam ring 148, and a cam actuator 147. It is equipped with.
- the first meshing clutch mechanism 1002 includes a first clutch hub 133 as a clutch hub provided in the clutch holder 137, a first meshing clutch 117, and a second meshing clutch 119.
- the clutch holder 137 is fixed to the case 02a with fastening members 136 such as bolts and nuts.
- the base of the first clutch hub 133 is integrally coupled to the inner peripheral side of the clutch holder 137.
- the first clutch hub 133 extends axially toward the first rotating body 101.
- a spline is formed on the outer peripheral surface of the first clutch hub 133.
- the first meshing clutch 117 is fastened or integrally processed with the first rotating body 101.
- a first boss 142 extending in the axial direction is provided on the inner diameter portion of the first clutch hub 133.
- the first boss 142 is rotatably supported by an inner diameter portion of the first clutch hub 133 by a bearing 131 such as a ball bearing.
- the bearing 131 has an inner race fixed to the first boss 142 and an outer race fixed to the first clutch hub 133 in the axial direction. This positioning and fixing is performed by a boss fastening member 127 such as a stopper ring attached to the first boss 142 and the first clutch hub 133, and a hub fastening member 129.
- the first sleeve 121 includes a second meshing clutch 119 that meshes with the first meshing clutch 117 and a first cam 143 for the meshing.
- the first sleeve 121 is urged to release the engagement of the second engagement clutch 119 with respect to the first engagement clutch 117.
- the first sleeve 121 engages with the first clutch hub 133 as a clutch hub fixed to the case 02a side in the rotational direction and is supported so as to be movable in the axial direction.
- the second meshing clutch 119 is provided on one side surface of the first sleeve 121.
- the second meshing clutch 119 is arranged so as to be able to mesh with the first meshing clutch 117.
- the second meshing clutch 119 is spline-fitted to the outer periphery of the first clutch hub 133 together with the first sleeve 121.
- the first sleeve 121 is provided with a first cam 143 on the other side surface.
- the first sleeve 121 is supported on the case 02a side by a holding member 139 such as a tension coil spring.
- the holding member 139 functions to urge the first sleeve 121 and hold the first and second meshing clutches 117 and 119 to the positions where they are released as described above.
- the holding member 139 may have a structure using a check ball mechanism or the like.
- the cam ring 148 includes a second cam 145 that engages with the first cam 143.
- the cam ring 148 is rotatably supported on the outer periphery of the base of the clutch holder 137.
- a second cam 145 is provided on one side surface of the cam ring 148.
- the second cam 145 meshes with or faces the first cam 143.
- a bearing 141 is interposed between the clutch holder 137 and the other side surface of the cam ring 148. The bearing 141 receives the axial force generated by the cam ring 148 with respect to the clutch holder 137.
- a rotated means 149 such as a circular or fan-shaped gear is fixed to the outer peripheral portion of the cam ring 148.
- the rotated means 149 has an uneven groove or the like, which is a detected means.
- the groove or the like is detected by the side sensor 303, and the detection signal is input to the controller 301.
- the cam ring 148 is configured to be rotationally driven by a cam actuator 147 such as an electric motor.
- the cam actuator 147 is fastened and fixed to the case 02a with bolts, nuts and the like.
- a drive pinion 151 is attached to the output shaft of the cam actuator 147 in the case 02a.
- the drive pinion 151 meshes with the rotated means 149.
- the first and second meshing clutches 117 and 119 have a tooth surface for transmitting positive torque and a tooth surface for transmitting negative torque, and the tooth for transmitting negative torque.
- the surface has an inclination for disengaging due to the negative torque.
- the tooth surfaces 123 and 125 of the first and second meshing clutches 117 and 119 transmit positive torque, for example, drive torque, and the tooth surfaces 123 and 125 are substantially parallel to or slightly inclined along the rotation axis. Has horns.
- the tooth surfaces 120 and 122 of the first and second meshing clutches 117 and 119 transmit a negative torque, for example, a torque in the opposite direction to the drive torque (hereinafter referred to as a coast torque).
- the tooth surfaces 120 and 122 have a pressure angle (angle with respect to the rotation axis) larger than the friction angle.
- FIG. 4 is a sectional view of the main part of the first and second cams in the circumferential direction.
- FIG. 5 is a development cross-sectional view of a main part in the circumferential direction when the first and second cams are operated.
- FIG. 4 shows the case where the unevenness of the first cam 143 and the second cam 145 are engaged with each other
- FIG. 5 shows the case where the convex portion 126 of the first cam 143 is in contact with the convex portion plane 128 of the second cam 145. It is a figure.
- a cam action works as shown in FIG. That is, the first cam 143 and the second cam 145 separate along the cam slope.
- the convex portion 126 of the first cam 143 and the convex portion plane 128 of the second cam 145 come into contact with each other.
- This cam action works by controlling the cam actuator 147 with the controller 301 shown in FIG.
- the cam actuator 147 drives the drive pinion 151 under the control of the controller 301 to rotate the rotated means 149.
- the rotation of the rotated means 149 causes the cam ring 148 to rotate, and the cam action works.
- the cam actuator 147 is driven and controlled.
- the cam ring 148 is rotationally driven via the drive pinion 151 and the rotated means 149.
- the sensor 303 detects the phase of the rotated means 149 and transmits it to the controller 301. By this transmission, the cam ring 148 can obtain a predetermined phase.
- the first cam convex portion 126 is in contact with the second cam convex portion flat surface 128. Therefore, the first sleeve 121 cannot move in the separation direction. Further, the first rotating body 101 having the first meshing clutch 117 is also fixed in the axial direction by the bearing 131, the boss fastening member 127, and the hub fastening member 129, and cannot move in the axial direction.
- the meshing of the first and second meshing clutches 117 and 119 continues even when the coast torque is applied.
- the first meshing clutch mechanism 1002 can transmit torque in both the drive and coast directions as described above.
- this function is referred to as a 2-way clutch function.
- the first sleeve 121 moves on the first clutch hub 133 in the axial direction in which the first and second meshing clutches 117 and 119 are released. By this movement, the first and second meshing clutches 117 and 119 are disengaged.
- the holding member 139 holds the first sleeve 121 in the first and second meshing clutches 117 and 119 in the released position. In this way, the first meshing clutch mechanism 1002 has a one-way clutch function.
- FIG. 6 is a development cross-sectional view of a main part in the circumferential direction of the first and second cams composed of ball cams.
- FIG. 7 is a development cross-sectional view of a main part in the circumferential direction when the first and second cams composed of ball cams are operated.
- the first cam groove 2143 constituting the first cam is formed on the first cam member 121b, and the second cam groove 2145 constituting the second cam is formed on the cam ring 148b. is doing.
- a rolling element 2112 is engagedly arranged between the first cam groove 2143 and the second cam groove 2145.
- the rolling elements 2112 are held by the retainer 135.
- the rolling element 2112 constitutes the first cam together with the first cam groove 2143, and constitutes the second cam together with the second cam groove 2145.
- the cam ring 148b is rotated by the drive of the cam actuator 147, and the rolling elements 2112 ride on the first and second cam grooves 2143 and 2145 as shown in FIG. 6, and the same cam action as described above works.
- the rotation phases of the first and second cam grooves 2143 and 2145 are adjusted as shown in FIG. 5 by returning the rotation position of the cam ring 148b by driving the cam actuator 147, the first sleeve 121 moves in the axial direction due to the cam action. The restraint of is released.
- the tooth surfaces 123 and 125 that receive the drive torque of the first and second meshing clutches 117 and 119 can have the same pressure angle as the tooth surfaces 120 and 122 that receive the coast torque. That is, the pressure angles of the tooth surfaces 123 and 125 can be made equal to or larger than the friction angle with respect to the rotation axis. This is because the axial movement of the first sleeve 121 can be blocked by the cam action of the cam ring 148.
- the meshing clutch mechanism 1002 can be easily switched between the one-way clutch function and the two-way clutch function by a simple mechanism. Further, since a meshing clutch is used for torque transmission, torque transmission is reliable and a large torque capacity is provided.
- FIG. 8 is a schematic cross-sectional view of the skeleton according to the second embodiment, in which the meshing clutch mechanism is partially omitted.
- the same or corresponding components as those in the first embodiment are designated by the same reference numerals, and duplicated description will be omitted.
- the second meshing clutch mechanism 2002 which is the meshing clutch mechanism according to the second embodiment, includes a second rotating body 2101 which is a rotating body, a second sleeve 2121 which is a sleeve, and a cam member 2126.
- a second cam ring 2148, which is a cam ring, and a cam actuator 147 are provided.
- the second meshing clutch mechanism 2002 includes a second clutch hub 2133, and first and second meshing clutches 117 and 119.
- the second rotating body 2101 integrally includes a first meshing clutch 117.
- the second rotating body 2101 is configured to be rotatably fitted and supported on the torque transmission shaft 2102 via a bearing 2254.
- the torque transmission shaft 2102 includes a second clutch hub 2133, which is a clutch hub.
- the second sleeve 2121 includes a second meshing clutch 119 that meshes with the first meshing clutch 117.
- the second sleeve 2121 is urged by the holding member 2155 so as to release the meshing of the first and second meshing clutches 117 and 119, as in the first embodiment.
- the holding member 2155 of the second embodiment is configured to include a ball and a slope urged by a coil spring.
- the ball projected and urged by the coil spring is supported by the radial hole of the second clutch hub 2133.
- the slope is formed on the inner circumference of the second meshing clutch 119.
- the structure is such that the ball projected and urged by the coil spring comes into contact with the slope.
- the second sleeve 2121 is movably supported in the axial direction by engaging with the second clutch hub 2133 in the rotational direction by spline fitting or the like.
- the cam member 2126 includes a first cam 2123 for locking the mesh.
- the cam member 2126 is fitted to the second clutch hub 2133 so as to be relatively rotatable and supported so as to be movable in the axial direction.
- the cam member 2126 is arranged adjacent to the second sleeve 2121 so as to be relatively rotatable and axial force transferable via the bearing 2141.
- the outer diameter portion of the cam member 2126 has a cam member rotation preventing means 2151 that engages with the case 02b.
- the cam member rotation preventing means 2151 non-rotatably engages the cam member 2126 with the case 02b side so that the cam member 2126 can move only in the axial direction.
- the second cam ring 2148 includes a second cam 124 that engages with the first cam 2123.
- the structures of the first cam 2123 and the second cam 124 are the same as those of the first cam 143 and the second cam 145 of the first embodiment, and are configured as shown in FIGS. 4 to 7.
- the second cam ring 2148 is arranged to face the cam member 2126 and is rotatable relative to the second clutch hub 2133.
- the second cam ring 2148 is prevented from moving away from the cam member 2126 in the axial direction by the stopper ring 108 via the bearing 106.
- the stopper ring 108 is positioned on the second clutch hub 2133 by a second hub fastening member 110 such as a C clip.
- the stopper ring 108 can also be integrally molded with the second clutch hub 2133.
- the second cam ring 2148 cooperates with the first and second cams 2123 and 124 to convert the movement in the rotational direction into the movement in the axial direction. This converted axial movement is transmitted to the cam member 2126. This transmission causes the cam member 2126 to move and lock the meshing so that it can be released by rotational drive.
- the second cam ring 2148 is provided with the rotated means 2149 as in the first embodiment, and is configured to be interlocked with the cam actuator 147 via the drive pinion 151.
- the second cam ring 2148 is configured to be rotationally driven by the cam actuator 147.
- the torque transmission shaft 2102 is rotatably supported by bearings 2252 and 2255 on the case 02b.
- the second clutch hub 2133 is fixedly or integrally made to the torque transmission shaft 2102.
- the second rotating body 2101 is rotatably supported by a torque transmission shaft 2102 via a bearing 2254.
- the first clutch hub 133 of the first embodiment is fixed to the case 02a and is stationary.
- the second clutch hub 2133 of the second embodiment is fastened and fixed to the torque transmission shaft 2102 and rotates integrally.
- the second sleeve 2121 cannot move from the first meshing clutch 117 in the direction in which the second meshing clutch 119 is released. Further, since the end portion 183 of the second rotating body 2101 having the first meshing clutch 117 is also in contact with the transmission member 185 of the torque transmission shaft 2101, it cannot move in the axial direction. Therefore, the coupling of the first and second meshing clutches 117 and 119 is maintained.
- the first and second meshing clutches 117 and 119 are coasted.
- the holding member 2155 urges the second sleeve 2102 to hold the release position of the second meshing clutch 119.
- the cam actuator 147 is driven and the sensor 303 detects the phase of the second cam ring 2148. By transmitting this detection signal to the controller 301, the second cam ring 2148 can obtain a predetermined phase.
- FIG. 9 is a schematic cross-sectional view of the skeleton according to the third embodiment, in which a part of the two-speed transmission is omitted.
- the two-speed transmission is configured by using the first meshing clutch mechanism 1002 of the first embodiment. Therefore, the same or corresponding components as those in the first embodiment will be described with the same reference numerals, and duplicated description will be omitted.
- the two-speed transmission of the third embodiment inputs the power of the motor 005, which is a drive source, to the first sun gear 107, which is a sun gear, via the first sun gear shaft 105.
- the power after the shift is transmitted to the differential 001 which is another member by the first drive pinion 102 as the drive pinion for output.
- the other members are not particularly limited, and other than the differential 001 can be applied.
- This two-speed transmission is equipped with an internal gear 101 that can rotate relative to the case 02c.
- the internal gear 101 and the first planet carrier 113 are configured to adjust the friction torque coupled by the friction clutch mechanism.
- a first friction clutch mechanism 1004 or a second friction clutch mechanism 2004, which will be described later, is used as the friction clutch mechanism.
- the two-speed transmission according to the third embodiment includes the first meshing clutch mechanism 1002, the first sun gear 107 as a sun gear, the internal gear 101 and seven others, the first planet carrier 113 as a planet carrier, and a friction clutch mechanism.
- the first friction clutch mechanism 1004 or the second friction clutch mechanism 2004, the clutch actuator 159, and the like are provided.
- the first sun gear 107 is configured to receive a rotation input as described above.
- the internal gear 101 meshes with the first sun gear 107 via a first planet pinion 111 as a planet pinion, and corresponds to the first rotating body 101 of the first embodiment.
- the first planet carrier 113 is rotatably supported by the internal gear 101, and rotatably supports the first planet pinion 111.
- One side portion of the first planet carrier 113 is rotatably supported by the first boss portion 142 via a bearing 142a.
- the other side of the first planet carrier 113 is provided with a gear set support portion 113a and a hollow output shaft 1112.
- the output shaft 1112 is fitted to the first sun gear shaft 105 and is supported so as to be relatively rotatable.
- the output shaft 1112 is integrally provided with a first drive pinion 102, which is a drive pinion for output.
- the first friction clutch mechanism 1004 or the second friction clutch mechanism 2004 is interposed between the internal gear 101 and the first planet carrier 113, and by fastening the internal gear 101 and the first planet carrier 113. It is a configuration that regulates the bond between them.
- the clutch actuator 159 is configured to adjust the friction torque of the coupling of the friction clutch mechanism by adjusting the engagement of the first friction clutch mechanism 1004 or the second friction clutch mechanism 2004.
- first friction clutch mechanism 1004 will be described
- second friction clutch mechanism 2004 will be described in the fourth embodiment.
- the input to the two-speed transmission of the third embodiment shown in FIG. 9 is performed on the first sun gear shaft 105.
- One end of the first sun gear shaft 105 is connected to the motor shaft 007 of the motor 005 by a fastening member 103 such as a spline or a key.
- One end side of the first sun gear shaft 105 is supported by a bearing 114 in a shaft support housing on the case 02c side.
- a packing 116 seals between one end side of the first sun gear shaft 105 and the case 02c side.
- the first sun gear 107 is coupled to the other end side of the first sun gear shaft 105 by a fastening means 109 such as a spline or a key, or is integrally processed.
- the internal gear 101 has an internal gear 156 that meshes with the first planet pinion 111.
- a first planet pinion 111 is arranged between the internal gear 101 and the first sun gear 107 and meshes with both. Therefore, the torque transmitted to the first sun gear 107 is transmitted to the internal gear 101 via the first planet pinion 111.
- the first boss portion 142 is provided on one side portion of the internal gear 101.
- the other side of the internal gear 101 is provided with a first clutch housing 155 for the first friction clutch mechanism 1004.
- the torque transmitted to the internal gear 101 is amplified more than the input torque to the first sun gear 107 by the coupling of the first meshing clutch mechanism 1002.
- the amplified torque is transmitted to the first planet carrier 113 to drive the first drive pinion 102.
- the rotation of the first drive pinion 102 is decelerated with respect to the first sun gear 107, which is the input rotation, and the two-speed transmission becomes a low-speed stage.
- the rotations of the first sun gear 107 and the first drive pinion 102 are the same, and the two-speed transmission has a high-speed speed.
- the member responsible for the shifting function of the two-speed transmission according to the third embodiment is mainly realized by the first meshing clutch mechanism 1002 and the first friction clutch mechanism 1004. It was
- the first friction clutch mechanism 1004 includes the first clutch housing 155, the first friction clutch hub 140 provided on the first planet carrier 113, and the first and second friction members 153 and 154. And a pressing force adjusting means.
- the first friction member 153 has a configuration in which both sides or one side come into contact with the second friction member 154.
- the inner diameter of the first friction member 153 is engaged with the one friction clutch hub 140 in the rotational direction.
- the outer diameter portion of the second friction member 154 is engaged with the first clutch housing 155 in the rotational direction.
- the first clutch housing 155 has means for receiving the pressing force applied to the first and second friction members 153 and 154.
- the pressing force adjusting means includes a set of first differential gear set 0171 including a pressing member 175, first and second differential gears 171 and 169, and a torque cam 162.
- the pressing member 175 has an outer diameter portion that comes into contact with the first friction member 153 or the second friction member 154 and applies a pressing force to the first and second friction members 153 and 154.
- the inner diameter portion of the pressing member 175 is arranged so as to be relatively rotatable on the gear set support portion 113a included in the first planet carrier 113.
- Bearings 173, first and second differential gears 171 and 169, and bearings 167 are arranged in the axial direction on the gear set support portion 113a.
- Both the facing surfaces of the first and second differential gears 171 and 169 have a plurality of grooves whose depths are inclined in the circumferential direction.
- a rolling element 161 is engaged with each of the grooves to form a torque cam 162.
- the torque cam 162 has a function of converting the relative rotational torque of the first and second differential gears 171 and 169 into axial thrust.
- a first fixing member 165 is fastened and fixed to the gear set support portion 113a by a fastening member 168.
- the first fixing member 165 supports a bearing 167 that receives the thrust reaction force generated by the torque cam 162 of the second differential gear 169.
- the first differential gear set 0171 is driven by a clutch pinion 157 that meshes with the first and second differential gears 171 and 169.
- the clutch pinion 157 is configured to be rotationally driven by the clutch actuator 159.
- the clutch pinion 157 is attached to an output shaft of a clutch actuator 159 by an electric motor or the like.
- the clutch actuator 159 is fastened and fixed to the case 02c side.
- the first differential gear set 0171 is driven in a predetermined direction by the clutch actuator 159
- the first and second differential gears 171 and 169 rotate relative to each other while rotating. Due to this relative rotation, the rolling element 161 moves on the slope of the torque cam 162, and thrust in a direction away from each other is generated between the first and second differential gears 171 and 169. This thrust presses the first and second friction members 153 and 154 via the bearing 173 and the pressing member 175 to generate friction torque.
- the first friction clutch mechanism 1004 generates the friction torque for fastening the internal gear 101 and the first planet carrier 113.
- the friction torque causes the first sun gear 107, the internal gear 101, and the first planet carrier 113 to rotate together.
- the clutch pinion 157 is driven in the reverse rotation direction by the clutch actuator 159, the friction torque of the first friction clutch mechanism 1004 disappears.
- the first friction clutch mechanism 1004 is released, the internal gear 101 is coupled to the case 02c by the first meshing clutch mechanism 1002, and the first sun gear 107 is rotated in the positive direction by the motor 005.
- the first planet pinion 111 revolves together with the first planet carrier 113 at a slower angular velocity than the first sun gear 107 while rotating. Therefore, the first planet carrier 113 and the first drive pinion 102 rotate at a lower speed and higher torque than the first sun gear 107, and the two-speed transmission of the present embodiment is in a low-speed stage state.
- the tooth surface 123 (see FIGS. 2 and 3) of the first meshing clutch 117 is a tooth surface that receives torque in the reverse rotation direction with respect to the forward rotation torque of the first sun gear 107. Is set to. That is, the tooth surfaces 123 and 125 are set as drive tooth surfaces that receive drive torque with respect to the torque in the reverse rotation direction, and the tooth surfaces 120 and 122 are set as coast tooth surfaces that receive coast torque.
- the first meshing clutch mechanism 1002 is in the state of the one-way clutch function. That is, similarly to the first embodiment, the cam ring 148 is rotationally driven by the cam actuator 147. By this rotational drive, as shown in FIG. 4 of the first embodiment, the phase of the first cam convex portion 126 of the first sleeve 121 and the phase of the second cam concave portion plane 130 of the cam ring 148 are matched. This coincidence allows the sleeve 121 to move axially until the first cam convex portion 126 and the second cam concave flat surface 130 mesh with each other. As a result, the one-way clutch function of the first meshing clutch mechanism 1002 is exhibited.
- the clutch actuator 159 drives the first differential gear set 0171 in a predetermined direction to engage the first friction clutch mechanism 1004.
- the internal gear 101 and the first planet carrier 113 are frictionally coupled by the first friction clutch mechanism 1004.
- the first meshing clutch 117 starts to rotate in the same direction as the first sun gear 107.
- coast torque is applied to the coast tooth surfaces 120 and 122 of the first and second meshing clutches 117 and 119.
- the one-way clutch function of the first meshing clutch mechanism 1002 causes the second meshing clutch 119 to retract in the axial direction, and the coupling of the first and second meshing clutches 117 and 119 is automatically released.
- the two-speed transmission is smoothly shifted to the high-speed stage without interruption of the driving force.
- the downshift from the high speed stage to the low speed stage is performed by releasing the first friction clutch mechanism 1004. With this release, the rotation of the motor 005 is increased until the rotation of the internal gear 101 is almost stopped or slightly reversed. At this stage, the cam ring 148 is rotationally driven by the cam actuator 147. By this rotational drive, the first cam convex portion 126 escapes from the second cam concave portion plane 130. At the same time, the first cam convex portion 126 is in contact with the second cam convex portion plane 128. As a result, the two-speed transmission is downshifted to the low speed stage.
- the driving torque is maintained as follows. Seamless downshifting is possible.
- the friction torque of the first friction clutch mechanism 1004 is reduced until the first and second friction members 153 and 154 start minute slip, the drive of the clutch actuator 159 is stopped and the first friction clutch is stopped.
- the friction torque of the mechanism 1004 is fixed.
- the first friction clutch mechanism 1004 is fastened and driven in a direction of increasing the frictional force to the extent that the rotation increase of the motor 005 described later is not hindered.
- the rotation of the motor 005 is increased until the rotation of the internal gear 101 is stopped or slightly reversed.
- the first meshing clutch mechanism 1002 is engaged, and the first friction clutch mechanism 1004 is released at the same time as or after the engagement of the first engagement clutch mechanism 1002.
- the normal control of the first friction clutch mechanism 1004 is as follows.
- the clutch actuator 159 rotationally drives the first friction clutch mechanism 1004 in the direction of engaging from the released position. It is considered that the pressing of the first and second friction clutches 153 and 154 is started when the load is generated on the clutch actuator 159 by this rotational drive. It is considered that the first friction clutch mechanism 1004 is engaged by the rotation of ⁇ X from the start of this pressing. ⁇ X rotation is determined by confirming it by experiment in advance.
- the first friction clutch mechanism 1004 is released by rotating the clutch actuator 159 in the reverse direction by the above ⁇ X + ⁇ .
- the coupling of the first meshing clutch mechanism 1004 for carrying out the shift down needs to be performed when the rotation of the first meshing clutch 117 is stationary or when the rotation of the first meshing clutch 117 is minute reverse rotation. Therefore, the sensor 302 detects the rotation of the internal gear 101 and transmits it to the controller 301. Upon receiving this transmission, the controller 301 determines the rotation condition of the first meshing clutch 117. Based on this determination, the cam actuator 147 is driven in the direction in which the first meshing clutch mechanism 1002 is engaged. When carrying out the seamless shift down, it is essential to detect minute slips of the first and second friction clutches 153 and 154 as described above.
- Example 3 The effects of Example 3 are as follows. For shifting to a high speed, seamless and smooth shifting is possible by using the first meshing clutch mechanism 1002 as a one-way clutch function and engaging the first friction clutch mechanism 1004. Moreover, since the first meshing clutch mechanism 1002 has a two-way clutch function that locks the one-way clutch function, the regenerative mode of the drive motor 005 at a low speed stage or the torque in the direction opposite to the normal drive when the vehicle reverses. Communication is possible.
- the first friction clutch mechanism 1004 shown in FIG. 9 is replaced with the second and third friction clutch mechanisms 2004 and 3004 described in the fourth and eighth embodiments shown in FIGS. 10 and 14. It may be adopted.
- FIG. 10 is a schematic cross-sectional view of the skeleton according to the fourth embodiment, in which a part of the two-speed transmission is omitted.
- the two-speed transmission is configured by using the first meshing clutch mechanism 1002 of the first embodiment.
- the two-speed transmission of the fourth embodiment is similar to the two-speed transmission of the third embodiment. Therefore, the same or corresponding components as those in Examples 1 and 3 will be described with the same reference numerals, and duplicated description will be omitted.
- the main differences between the two-speed transmission of the fourth embodiment and the two-speed transmission of the third embodiment are as follows.
- the internal gear 101 of the third embodiment is not used.
- the second planet carrier 2113 and the case 02d are coupled and released by the first meshing clutch mechanism 1002.
- the second friction clutch mechanism 2004 has a configuration in which the second planet carrier 2113 and the third sun gear shaft 3105 are coupled and released.
- the two-speed transmission includes a second sun gear 2192 as a sun gear, a third sun gear shaft 3105, and a second planet pinion 2201 as a planet pinion. It includes a second planet carrier 2113 as a planet carrier, a second friction clutch mechanism 2004 as a friction clutch mechanism, and a clutch actuator 159.
- the second sun gear 2192 is configured to receive a rotation input from a motor 005 by a third sun gear shaft 3105 as a sun gear shaft.
- the third sun gear shaft 3105 is fitted to the second sun gear shaft 2105 as a sun gear shaft and is rotatably supported.
- the third sun gear shaft 3105 includes a third sun gear 2110 and a drive pinion 2164 for output.
- the second sun gear shaft 2105 corresponds to the first sun gear shaft 105 of the third embodiment.
- the second planet pinion 2201 integrally includes the first and second gears 2114 and 1226.
- the first gear 2114 meshes with the second sun gear 2192.
- the second gear 2116 meshes with the third sun gear 3105.
- the second gear 2116 is set to have a smaller number of teeth than the first gear 2114.
- the second planet carrier 2113 rotatably supports the second planet pinion 2201.
- the second planet carrier 2113 corresponds to the first rotating body 101 of the first embodiment.
- the second friction clutch mechanism 2004 is interposed between the second planet carrier 2113 and the third sun gear shaft 3105, and is fastened between the second planet carrier 2113 and the third sun gear shaft 3105. It is a configuration that regulates binding.
- the clutch actuator 159 is configured to adjust the friction torque of the coupling by adjusting the engagement of the second friction clutch mechanism 2004.
- the input to the two-speed transmission of the fourth embodiment shown in FIG. 10 is performed on the second sun gear shaft 2105.
- One end of the second sun gear shaft 2105 is coupled to the motor shaft 007 of the motor 005 in the same manner as in the third embodiment.
- the other end side of the second sun gear shaft 2105 is rotatably supported by the second boss 2214 of the second planet carrier 2113 via a bearing 115.
- the third sun gear shaft 3105 integrally includes a second friction clutch hub 140b.
- the second friction clutch hub 140b is configured to engage the inner diameter portion of the first friction member 153 in the rotational direction.
- the third sun gear shaft 3105 integrally includes a first drive pinion 102 as a drive pinion for output.
- the first drive pinion 102 is configured to drive other members such as the differential 001.
- the third sun gear shaft 3105 is supported on the outer periphery of the second sun gear shaft 2105 by bearings 2163 and 2164.
- the second planet pinion 2201 is rotatably supported by the second planet carrier 2113 via a bearing 191.
- the second planet carrier 2113 is provided with a second clutch housing 2187 on one side.
- the second clutch housing 2187 is configured to engage the outer diameter portion of the second friction member 154 in the rotational direction.
- the second clutch housing 2187 has means for receiving the pressing force applied to the first and second friction members 153 and 154.
- a second boss 2214 is integrally provided on the other side of the second planet carrier 2113.
- the second boss 2214 is rotatably supported by a bearing 131 on the inner diameter portion of the first clutch hub 133 of the clutch holder 137.
- the pressing force adjusting means includes a pressing member 175, first and second differential gears 171 and 169, and a torque cam 162. It is configured to include one differential gear set 0171.
- the torque cam 162 generates thrust by driving the clutch actuator 159, and the pressing member 175 presses the first and second friction members 153 and 154.
- the pressing force adjusting means is provided with an elastic body 177.
- the elastic body 177 is configured to apply a pressing force to the first and second friction members 153 and 154.
- the axial thrust generated by the torque cam 2271 cancels the pressing force of the elastic body 177, and reduces or eliminates the friction torque of the second friction clutch mechanism 2004.
- the second friction clutch mechanism 2004 engages and supports the outer periphery of the second friction member 154 in the second clutch housing 2187 in the rotational direction.
- the second clutch housing 2187 has means for receiving the pressing force of the first and second friction members 153 and 154.
- the outer peripheral portion of the second friction member 154 is engaged with the second clutch housing 2187 in the rotational direction.
- the first friction member 153 is in contact with the second friction member 154 on one side or both sides, and the inner diameter portion is engaged with the second friction clutch hub 140b in the rotational direction.
- the pressing force adjusting means applies or adjusts pressing force to the first and second friction members 153 and 154.
- This pressing force adjusting means includes a first pressing force adjusting member 2189 as a pressing force adjusting member.
- the first pressing force adjusting member 2189 is configured to be in contact with either the first or second friction member 153 or 154 to adjust the pressing force between the two friction members.
- the first push pressure adjusting member 2189 integrally includes a gear set support portion 2176 of a hollow shaft.
- a second differential gear set 0271 is arranged on the gear set support portion 2176.
- the second differential gear set 0271 corresponds to the first differential gear set 0171 of the third embodiment.
- the second differential gear set 0271 includes an elastic body 177.
- the elastic body 177 is in contact with the first pressing force adjusting member 2189.
- the elastic body 177 is configured to settle the first pressing force adjusting member 2189 and generate pressing force for fastening to the first and second friction members 153 and 154.
- the reaction force of the elastic body 177 is configured to be received by the reaction force member 2173.
- the reaction force member 2173 is fixed to the second clutch housing 2187 by the fastening member 2179.
- a bearing 2169 is in contact with the inner diameter portion of the reaction force member 2173, and the third and fourth differential gears 2171 and 2172 and the bearing 2170 are arranged in the axial direction.
- a torque cam 2271 is configured between the third and fourth differential gears 2171 and 2172 as in the third embodiment.
- the bearing 2170 has a configuration in which the axial force is received by the second fixing member 2168.
- the second fixing member 2168 is fixed to the gear set support portion 2176 by the fastening member 2165.
- the clutch actuator 159 drives the second differential gear set 0271 via the clutch pinion 157.
- the second differential gear set 0271 is driven in the thrust generation direction of the torque cam 2271, the generated axial thrust is transmitted to the gear set support portion 2176 of the first push pressure adjusting member 2189.
- the gear set support portion 2176 moves so as to separate the bearings 2170 and 2169.
- the first push pressure adjusting member 2189 moves.
- the pressing force of the elastic body 177 is reduced by moving the first pressing force adjusting member 2189. By this reduction, the friction torque of the second friction clutch mechanism 2004 is reduced or eliminated.
- the operation of the two-speed transmission of the fourth embodiment is basically the same as that of the two-speed transmission of the third embodiment.
- the rotation of the second planet carrier 2113 is fixed to the case 02d side by the first meshing clutch mechanism 1002 described above.
- the second planet pinion 2201 does not revolve but only rotates. Therefore, the rotation of the second sun gear 2192 is transmitted to the third sun gear 2110, which has a relatively large number of teeth. Therefore, the rotation speed of the third sun gear 2110 is lower than the rotation speed of the second sun gear 2192 that rotates at the input, and the first drive pinion 102 is driven at that speed.
- This drive state is a low speed stage.
- the second planet carrier 2113 receives torque in the opposite direction to the second sun gear 2192. Therefore, as described in the third embodiment, the meshing of the first and second meshing clutches 117 and 119 is the same as that in the third embodiment.
- the cam ring 148 is rotated by the cam actuator 147 as in the third embodiment.
- the first meshing clutch mechanism 1002 which fixes the rotation of the second planet carrier 2113 by this rotation, has a one-way clutch function.
- the clutch actuator 159 drives the first and second differential gear sets 0171 and 0271 via the clutch pinion 157.
- the second friction clutch mechanism 2004 couples the rotation between the second planet carrier 2113 and the third sun gear shaft 3105.
- the relative rotation of the second planet pinion 2201, the second sun gear 2192 having an input rotation speed, and the third sun gear 2110 is fixed.
- the rotation of the second sun gear 2192 is transmitted to the third sun gear shaft 3105 without being decelerated, and becomes a high-speed stage.
- the shift down from the high speed stage to the low speed stage is the same as in the third embodiment.
- the coupling between the third sun gear shaft 3105 and the second planet carrier 2113 is released by the operation of the second friction clutch mechanism 2004.
- the coupling force torque of the second friction clutch mechanism 2004 is weakened until the first and second friction members 153 and 154 start a minute slip.
- the rotation of the motor 005 is increased until the rotation of the second planet carrier 2113 is stopped or slightly reversed.
- the cam ring 148 is rotated to make the first cam convex portion 126 and the second cam convex portion flat surface 128 function. With this function, the first and second meshing clutches 117 and 119 of the first meshing clutch mechanism 1002 maintain the meshing.
- the second friction clutch mechanism 2004 of the fourth embodiment can be configured by the first friction clutch mechanism 1004 of the third embodiment.
- the second clutch housing 2187 is replaced with the first clutch housing 155 of the third embodiment shown in FIG.
- the pressing member 175 of the third embodiment is incorporated into the replaced first clutch housing 155.
- the pressing member 175 is configured to replace the first pressing pressure adjusting member 2189, the elastic body 177, and the reaction force member 2173.
- the first friction clutch mechanism 1004 having such an arrangement can also release the coupling between the second planet carrier 2113 and the third sun gear shaft 3105.
- Example 4 The differences in the effects of Example 4 with respect to Example 3 are as follows.
- the reduction ratio of the low speed stage becomes larger than 2, and it is difficult to approach 2.
- the reduction ratio including 2 can be freely selected. Furthermore, it is inexpensive without using an internal gear.
- FIG. 11 is a schematic cross-sectional view of the skeleton according to the fifth embodiment, in which a part of the two-speed transmission is omitted.
- the two-speed transmission is configured by using the first meshing clutch mechanism 1002 of the first embodiment.
- the means for receiving the power of the motor 005 of the third embodiment is changed, and the second friction clutch mechanism 2004 of the fourth embodiment is adopted as the friction clutch mechanism. Therefore, the same reference numerals are given to the main parts of the constituent parts that are the same as or corresponding to the first, third, and fourth embodiments, or the same reference numerals are given in the 4000 series, and duplicated explanations will be omitted.
- the two-speed transmission of the fifth embodiment differs from the two-speed transmission of the third embodiment in the following points.
- the two-speed transmission according to the fifth embodiment performs rotation input from the motor 005 to the first sun gear 107 as a sun gear by the drive gear 2103 of the motor shaft 007 and the driven gear 2104 of the fourth sun gear shaft 4105.
- the drive gear 2103 is fixed to the motor shaft 007.
- the drive gear 2103 meshes with a driven gear 2104 fixed to a fourth sun gear shaft 4105 as a sun gear shaft.
- the fourth sun gear shaft 4105 is rotatably supported by a bearing 114 on the case 02e side.
- the first sun gear 107 is engaged with the fourth sun gear shaft 4105 by a fastening means 4106 such as a spline, or is integrally formed.
- the internal gear 101 and the first planet carrier 113 are configured to be released by the second friction clutch mechanism 2004 of the fourth embodiment.
- the second friction clutch mechanism 2004 can be replaced with the first friction clutch mechanism 1004 of the third embodiment.
- Example 5 with respect to Examples 3 and 4 are as follows.
- a gear train including a drive gear 2103 and a driven gear 2104 is incorporated in the driving force input path with respect to the third and fourth embodiments.
- the input rotation to the first sun gear 107 can be freely changed by changing the deceleration or acceleration ratio of the gear train. Therefore, the selection of reduction ratios of the two-speed transmission according to the fifth embodiment is increased. Further, the distance between the motor shaft 007 and the differential 001 or the like is widened, and the degree of freedom in layout is increased.
- FIG. 12 is a schematic cross-sectional view of the skeleton according to the sixth embodiment, in which a part of the two-speed transmission is omitted.
- the two-speed transmission of the sixth embodiment adopts the input structure of the fifth embodiment as opposed to the structure of the fourth embodiment. Therefore, the main parts of the same or corresponding components as those of Examples 4 and 5 will be described with the same reference numerals, and duplicated description will be omitted.
- the rotation input structure from the motor 005 to the second sun gear shaft 2105 is a direct structure on the same axis, whereas in the sixth embodiment, it is configured in the same manner as in the fifth embodiment.
- the driven gear 2104 of the second sun gear shaft 2105 was meshed with the drive gear 2103 of the motor shaft 007 of the motor 005.
- the same effect as that of the fifth embodiment can be obtained for the structure of the fourth embodiment.
- FIG. 13 is a schematic cross-sectional view of the skeleton according to the seventh embodiment, in which a part of the two-speed transmission is omitted.
- the two-speed transmission was configured by using the second meshing clutch mechanism 2002 of the second embodiment. Therefore, the same or corresponding components as those in the second embodiment will be described with the same reference numerals, and duplicated description will be omitted.
- the two-speed transmission in addition to the second meshing clutch mechanism 2002, generally includes an input shaft 3203 and an output shaft 3205, low-speed and high-speed drive gears 199, 197, and low-speed and high-speed driven gears 3201 and 211.
- a third friction clutch mechanism 3004 as a friction clutch mechanism and a clutch actuator 2159 are provided.
- the input shaft 3203 is integrally provided with the low-speed drive gear 199 and the high-speed drive gear 197, and is configured to receive rotational input from the motor 005.
- the output shaft 3205 includes a low-speed driven gear 3201 that meshes with the low-speed drive gear 199, a high-speed driven gear 211 that meshes with the high-speed drive gear 197, and a second drive pinion 221 as a drive pinion for output. be.
- the output shaft 3205 constitutes the torque transmission shaft 2102 of the second embodiment.
- the input shaft 3203 may form a torque transmission shaft corresponding to the torque transmission shaft 2102.
- the torque transmission shaft means that the rotating body including the first meshing clutch 117 is rotatably fitted and supported and the second clutch hub 2133 is provided, and the output is not intended.
- the output shaft 3205 constitutes the torque transmission shaft 2102 of the second embodiment
- the low speed driven gear 3201 constitutes the second rotating body 2101 of the second embodiment
- the low speed drive gear 199 is the above. It is fixed to the input shaft 3203.
- the low speed drive gear 199 constitutes the second rotating body 2101 of the second embodiment
- the low speed driven gear 3201 is the output shaft. It will be fixed.
- the high-speed driven gear 211 is rotatably provided on the output shaft 3205.
- the third friction clutch mechanism 3004 is provided between the output shaft 3205 and the high-speed driven gear 211.
- the third friction clutch mechanism 3004 is configured to adjust the coupling between the output shaft 3205 and the high-speed driven gear 211.
- the high-speed drive gear 197 may be rotatably supported by the input shaft 3203, and a third friction clutch mechanism 3004 may be provided between the high-speed drive gear 197 and the input shaft 3203.
- the third friction clutch mechanism 3004 is configured to adjust the coupling between the input shaft 3203 and the high-speed drive gear 197.
- the clutch actuator 2159 engages and adjusts the third friction clutch mechanism 3004 by driving the clutch actuator 2159.
- the structure is such that the friction torque of the coupling is adjusted by this fastening adjustment.
- a pressing force adjusting means for causing the fastening is provided between the clutch actuator 2159 and the third friction clutch mechanism 3004.
- the pressing force adjusting means includes an elastic body 227 and a second pressing force adjusting member 231.
- the elastic body 227 is composed of, for example, a disc spring.
- the elastic body 227 is configured to generate a pressing force for engaging the third friction clutch mechanism 3004.
- the second pressing force adjusting member 231 receives the pressing force of the elastic body 227 to perform the fastening.
- the second pressing force adjusting member 231 is configured to be coupled to the clutch actuator 2159 side.
- the clutch actuator 2159 is configured to drive the second pressing force adjusting member 231 to adjust the pressing force of the elastic body 227.
- the clutch actuator 2159 is composed of, for example, a hydraulic cylinder, an air cylinder, a solenoid, or the like.
- the clutch actuator 2159 has a configuration in which an output shaft such as a piston rod is driven in the axial direction.
- an electric motor to rotate the ball screw to move the ball nut linearly.
- the input to the two-speed transmission according to the seventh embodiment shown in FIG. 13 is performed on the input shaft 3203.
- the input shaft 3203 is rotatably supported on the case 02f side.
- the input shaft 3203 is coaxially arranged and integrally coupled to the motor shaft 007 of the motor 005.
- the input shaft 3203 is integrally provided with a low-speed drive gear 199 and a high-speed drive gear 197.
- the output shaft 3205 is arranged parallel to the input shaft 3203.
- the output shaft 3205 is integrally provided with the second drive pinion 221.
- the second drive pinion 221 is configured to transmit the power after shifting to other members such as the differential 001.
- a low-speed driven gear 3201 and a high-speed driven gear 211 are rotatably supported on the output shaft 3205.
- the low speed driven gear 3201 is rotatably supported by the input shaft 3203.
- the low-speed driven gear 3201 meshes with the low-speed drive gear 199 of the input shaft 3203 to form a low-speed gear train.
- the low speed driven gear 3201 has a first meshing clutch 117 of a second meshing clutch mechanism 2002.
- the high-speed driven gear 211 meshes with the high-speed drive gear 197 of the input shaft 3203 to form a high-speed gear train.
- Two gear trains are formed by the low speed gear train and the high speed gear train.
- the high-speed driven gear 211 is rotatably fitted and arranged on the output shaft 3205.
- the high speed driven gear 211 has a third boss 3216.
- the third boss 3216 is rotatably supported by a bearing 225 on the case 02f and is positioned and fixed in the axial direction.
- torque is transmitted by the second meshing clutch mechanism 2002 of the second embodiment for the low-speed stage and the third friction clutch mechanism 3004 for the high-speed stage, as in the other embodiments.
- the shift is performed in collaboration with both parties.
- the second meshing clutch mechanism 2002 has a configuration in which the low-speed driven gear 3201 and the output shaft 3205 are coupled and released.
- the third friction clutch mechanism 3004 has a configuration in which the high-speed driven gear 211 and the output shaft 3205 are coupled and released.
- the first and second friction clutch mechanisms 1004 and 2004 can be used instead of the third friction clutch mechanism 3004.
- the third friction clutch mechanism 3004 includes a third clutch housing 237, a third clutch hub 233, first and second friction members 153, 154, and the push pressure adjusting means. ..
- the third clutch housing 237 is integrally coupled to the third boss 3216 of the high-speed driven gear 211.
- the third clutch housing 237 is rotatably supported by the third boss 3216 with the bearing 225 interposed therebetween and is positioned in the axial direction.
- the third clutch housing 237 has means for receiving the pressing force of the first and second friction members 153 and 154.
- the third clutch hub 233 is provided with a shaft portion that penetrates the inner diameter portion of the third boss 3216 on the inner peripheral portion, and this shaft portion is rotatably supported by the third boss 3216 by a bearing 217.
- the shaft portion of the third clutch hub 233 is integrally coupled to the output shaft 3205.
- the first friction member 153 is engaged with the outer peripheral portion of the third clutch hub 233 in the rotational direction.
- the second friction member 154 is rotationally engaged with the inner peripheral portion of the third clutch housing 237.
- the second friction member 154 is configured to be in contact with the first friction member 153 on one side or both sides.
- the second pressing force adjusting member 231 is in contact with the first or second friction member 153, 154 and is configured to adjust the pressing force applied to the first and second friction members 153, 154.
- the elastic body 227 is configured to urge the second pressing pressure adjusting member 231 and apply an axial force to press the first and second friction members 153 and 154.
- the reaction force of the elastic body 227 is received by the fastening member 229 fixed to the third clutch housing 237.
- the inner diameter portion of the second push pressure adjusting member 231 is rotatably supported by the bearing 223.
- the bearing 223 is coupled to the piston rod of the clutch actuator 2159 via the decompression member 235.
- the pressure reducing member 235 is integrally configured with the inner race of the bearing 223.
- the clutch actuator 2159 drives the inner diameter portion of the second push pressure adjusting member 231 axially via the decompression member 235 and the bearing 223. By this drive, the axial force in the direction of reducing the pressing force of the elastic body 227 is reversibly applied. The pressing force of the elastic body 227 is adjusted by such application.
- the two-speed transmission of the seventh embodiment has a low-speed speed by coupling the low-speed driven gear 3201 and the output shaft 3205 by the two-way clutch function of the second meshing clutch mechanism 2002.
- the rotation phase of the second cam ring 2148 of the second meshing clutch mechanism 2002 is shifted, the second meshing clutch mechanism 2002 has a one-way clutch function, and the third friction clutch mechanism 3004 is coupled to shift to a high speed stage.
- the downshift is performed as described in the other examples described above. That is, the fastening of the third friction clutch mechanism 3004 is released.
- the rotation of the motor 005 is rapidly increased until the first meshing clutch 117 synchronizes with or slightly overtakes the rotation of the second meshing clutch 119.
- the cam actuator 2148 is driven by the cam actuator 147 to engage the first and second meshing clutches 117 and 119.
- Seamless downshifting is performed as described above. That is, the friction torque of the third friction clutch mechanism 3004 is reduced. Due to this decrease, a minute slip between the first and second friction members 153 and 154 is detected. This minute slip is detected, for example, by detecting the rotation speed of the second drive pinion 221 by the rotation detection means 2302 as a sensor and comparing it with the rotation speed of the motor 005. At the moment when the minute slip occurs, the fastening force of the third friction clutch mechanism 3004 is fixed. Specifically, the clutch actuator 2159 is stopped, and the rotation speed of the motor 005 is rapidly increased to the rotation speed at which the first meshing clutch 117 synchronizes with the second meshing clutch 119 or the rotation speed slightly overtakes. At this point, the first and second meshing clutches 117 and 119 are engaged, and at the same time, the third friction clutch mechanism 3004 is released.
- the second meshing clutch mechanism 2002 and the third friction clutch mechanism 3004 are arranged on the output shaft 3205, but the second meshing clutch mechanism 2002 and the third friction clutch mechanism 3004 are arranged in the following (1).
- a second meshing clutch mechanism 2002 and a third friction clutch mechanism 3004 are provided on the input shaft 3203. The above four combinations are possible.
- the third friction clutch mechanism 3004 can be configured by other clutches such as hydraulic pressure, pneumatic pressure and electromagnetic.
- the gear ratio can be freely selected for both the high-speed stage and the low-speed stage.
- the basic structure is simply to add one gear train to the single gear train of a normal two-axis electric self-propelled vehicle reducer and change it to two gear trains. Therefore, the basic structure and the external shape of the speed reducer for the two-axis electric self-propelled vehicle are less likely to be changed, the structure is simple, the weight is light, and the vehicle is convenient for in-vehicle use.
- FIG. 14 is a schematic cross-sectional view of the skeleton according to the eighth embodiment, in which a part of the two-speed transmission is omitted.
- the two-speed transmission of the eighth embodiment is basically configured in the same manner as the third embodiment. Therefore, the same or corresponding components as those in the third embodiment will be described with the same reference numerals, and duplicated description will be omitted.
- the second output shaft 3112 is provided as an output shaft coupled to the first planet carrier 113 and projecting to the outside.
- a second output shaft 3112 is provided on one side of the first planet carrier 113.
- the second output shaft 3112 penetrates the inner diameter portion of the first clutch hub 133 of the first meshing clutch mechanism 1002 and the case 02g, and is arranged so as to project to the outside.
- the configuration is such that an external member can be coupled to the second output shaft 3112.
- the other side portion of the first planet carrier 113 is separated from the portion that was the hollow output shaft 1112 in the third embodiment, and the output shaft 1112 is configured as a hollow shaft that does not directly output.
- the first sun gear 107 is coupled to the hollow shaft 1112, and the hollow shaft 1112 is coupled and fixed to the motor shaft 007.
- Example 3 when the two-speed transmission of Example 8 is used for an electric vehicle are as follows. That is, the two-speed transmission of the third embodiment is suitable for the layout in which the motor 005 is arranged horizontally with respect to the vehicle, whereas the layout of the eighth embodiment is suitable for the layout in which the motor 005 is arranged vertically.
- FIG. 15 is a schematic cross-sectional view of the skeleton according to the ninth embodiment, in which a part of the two-speed transmission is omitted.
- the two-speed transmission of the ninth embodiment is basically configured in the same manner as the fourth embodiment. Therefore, the same or corresponding components as those in the fourth embodiment will be described with the same reference numerals, and duplicated description will be omitted.
- the third sun gear output shaft 4205 and the extended output shaft 4114 are provided as output shafts coupled to the third sun gear 4110 and projected to the outside.
- the positions of the first gear 2114 and the second sun gear 4108 and the second gear 2116 and the third sun gear 4110 are opposite to each other in the axial direction with respect to the two-speed transmission according to the fourth embodiment. Have been placed.
- the second sun gear 4108 is fastened to the motor shaft 007 or integrally processed.
- the third sun gear 4110 is provided with a third sun gear output shaft 4205 and an extension output shaft 4114 as output shafts.
- the extension output shaft 4114 has a configuration in which the third sun gear output shaft 4205 is extended and formed.
- the third sun gear output shaft 4205 corresponds to the third sun gear shaft 3105 of the fourth embodiment.
- the third sun gear output shaft 4205 is rotatably supported by a bearing 115 on the second boss 2214 of the second planet carrier 4113.
- the extension output shaft 4114 penetrates the case 02h and is arranged so as to project to the outside.
- the configuration is such that an external member can be coupled to the extended output shaft 4114.
- the second sun gear 4108 is coupled to the hollow shaft 2105, and the hollow shaft 2105 is fixed to the motor shaft 007.
- the hollow shaft 2105 corresponds to the second sun gear shaft 2105 of the fourth embodiment.
- the second sun gear shaft 2105 of the fourth embodiment was used as a hollow shaft 2105 and was directly coupled to the motor shaft 007.
- the second friction clutch hub 140b in the fourth embodiment is integrally provided with the second sun gear 4108 in the ninth embodiment.
- the second friction clutch mechanism 2004 of the ninth embodiment is configured to fasten and adjust between the second planet pinion 2201 and the second sun gear 4108.
- the second friction clutch mechanism 2004 can be replaced with the first friction clutch mechanism 1004.
- the present embodiment 9 is effective for an electric vehicle having a vertical motor as in the eighth embodiment.
- the torque transmission of the high-speed stage in the two-stage transmissions of Examples 3 to 9 is carried out by the first, second, and third friction clutch mechanisms 1004, 2004, and 3004, but the following modifications are also possible. .. (1) Instead of the first and second differential gear sets 0171 and 0271, thrust is generated by the worm wheel and the torque cam to press the first and second friction members 153 and 154. (2) Use a hydraulic clutch or an electromagnetic clutch.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
(1)アウトプットシャフト3205上に第二噛み合いクラッチ機構2002と第三摩擦クラッチ機構3004を設ける本実施例7で説明した前記のレイアウト。
(2)アウトプットシャフト3205上に第二噛み合いクラッチ2002を設けインプットシャフト3203上に第三摩擦クラッチ機構3004を設けるレイアウト。
(3)アウトプットシャフト3205上に第三摩擦クラッチ機構3004、インプットシャフト3203上に第二噛み合いクラッチ機構2002を設けるレイアウト。
(4)インプットシャフト上3203上に第二噛み合いクラッチ機構2002と第三摩擦クラッチ機構3004を設ける。以上の4つの組み合わせが可能である。
(1)第一、第二差動ギヤーセット0171、0271に代え、ウオームホイールとトルクカムとで推力を発生させて第一、第二摩擦部材153、154を押圧する。
(2)油圧クラッチや電磁クラッチを用いる。
101 第一回転体、インターナルギヤー(回転体)
102、221 出力用のドライブピニオン
107 第一サンギヤー(サンギヤ―)
111 第一プラネットピニオン(プラネットピニオン)
113 第一プラネットキャリア(プラネットキャリア)
117 第一噛み合いクラッチ
119 第二噛み合いクラッチ
120、122 負トルクを伝達する歯面
123、125 正トルクを伝達する歯面
121 第一スリーブ(スリーブ)
124 第二カム
133 第一クラッチハブ(クラッチハブ)
139、2155 保持部材
143 第一カム
145 第二カム
147 カムアクチュエーター
148 カムリング
153 第一摩擦部材
154 第二摩擦部材
157 クラッチピニオン
159 クラッチアクチュエーター
162 トルクカム
169 第二差動ギヤ―
171 第一差動ギヤ―
175 押圧部材
177 弾性体
197 高速ドライブギヤ―
199 低速ドライブギヤ―
211 高速ドリブンギヤ―
227 弾性体
231 第二押圧力調整部材(押圧力調整部材)
301 コントローラー
302、303 センサー
1002 第一噛み合いクラッチ機構
1004 第一摩擦クラッチ機構(摩擦クラッチ機構)
2002 第二噛み合いクラッチ機構
2004 第二摩擦クラッチ機構(摩擦クラッチ機構)
2101 第二回転体(回転体)
2102 トルク伝達軸
2103 ドライブギヤ―
2104 ドリブンギヤ―
2105 第二サンギヤ―シャフト(サンギヤ―シャフト)
2113 第二プラネットキャリア(プラネットキャリア)
2114 第一歯車
2116 第二歯車
2121 第二スリーブ(スリーブ)
2126 カム部材
2133 第二クラッチハブ(クラッチハブ)
2123 第一カム
2126 カム部材
2133 第二クラッチハブ(クラッチハブ)
2148 第二カムリング(カムリング)
2159 クラッチアクチェーター
2171 第一差動ギヤ―
2172 第二差動ギヤ―
2189 第一押圧力調整部材(押圧力調整部材)
2201 第二プラネットピニオン(プラネットピニオン)
2302 回転検出手段(センサー)
3004 第三摩擦クラッチ機構(摩擦クラッチ機構)
3105 第三サンギヤ―シャフト
3112 第二出力軸(出力軸)
3201 低速ドリブンギヤ―
3203 インプットシャフト
3205 アウトプットシャフト
4108 第二サンギヤ―(サンギヤ―)
4110 第三サンギヤ―
4113 第二プラネットキャリア(プラネットキャリア)
4114 延長出力軸(出力軸)
4205 第三サンギヤー出力軸(出力軸)
Claims (12)
- 正トルクを伝達する歯面及び負トルクを伝達する歯面を有し前記負トルクを伝達する歯面は前記負トルクにより噛合を外すための傾斜を有する第一噛合いクラッチを備え回転自在に支持された回転体と、
前記第一噛み合いクラッチに噛合する第二噛み合いクラッチ及び前記噛合のための第一カムを備え前記噛合を解放するように付勢されケース側に固定されたクラッチハブに回転方向に係合し軸方向に移動可能に支持されたスリーブと、
前記スリーブを付勢し前記第一、第二噛み合いクラッチの解放位置を保持する保持部材と、
前記第一カムに係合する第二カムを備え前記第一、第二カムの協働により回転方向の動きを軸方向の動きに変換して前記スリーブに伝達し前記噛合を回転駆動で解除可能にロックするカムリングと、
前記カムリングを回転駆動するカムアクチュエーターと、
を備えた噛み合いクラッチ機構。 - 正トルクを伝達する歯面及び負トルクを伝達する歯面を有し前記負トルクを伝達する歯面は前記負トルクにより噛合いを外す傾斜を有する第一噛合いクラッチを備えてクラッチハブを備えたトルク伝達軸に回転自在に嵌合支持された回転体と、
前記第一噛み合いクラッチに噛合する第二噛み合いクラッチを備え前記噛合いを解放するように付勢され前記クラッチハブに回転方向に係合し軸方向に移動可能に支持されたスリーブと、
前記スリーブを付勢し前記第一、第二噛み合いクラッチを噛合の解放位置を保持する保持部材と、
前記クラッチハブに回転自在に嵌合し軸方向に移動可能に支持され前記噛合のための第一カムを備え前記スリーブに対して相対回転可能且つ軸力伝達可能に隣接配置されケース側に回転不能に係合するカム部材と、
前記第一カムに係合する第二カムを備えて前記カム部材に対向配置され前記クラッチハブに相対回転可能に支持され且つ前記カム部材に対し軸方向離反移動が阻止され前記第一、第二カムの協働により回転方向の動きを軸方向の動きに変換して前記カム部材に伝達し前記噛合を回転駆動で解除可能にロックするカムリングと、
前記カムリングを回転駆動するカムアクチュエーターと、
を備えた噛み合いクラッチ機構。 - 請求項1記載の噛合いクラッチ機構を用いた2段変速装置であって、
回転入力を受けるサンギヤーと、
前記サンギヤーにプラネットピニオンを介して噛合い前記回転体を構成するインターナルギヤーと、
前記インターナルギヤーに相対回転自在に支持され前記プラネットピニオンを回転自在に支持すると共に出力用のドライブピニオンを備えたプラネットキャリアと、
前記インターナルギヤーとプラネットキャリアとの間に介設され締結により前記インターナルギヤーと前記プラネットキャリアとの間の結合を調節する摩擦クラッチ機構と、
前記摩擦クラッチ機構の締結調節により前記結合の摩擦トルクを調節するクラッチアクチュエーターと、
を備えた2段変速装置。 - 請求項1記載の噛合いクラッチ機構を用いた2段変速装置であって、
サンギヤーシャフトにより回転入力を受けるサンギヤーと、
前記サンギヤーシャフトに回転自在に支持され第三サンギヤーと出力用のドライブピニオンとを備えた第三サンギヤーシャフトと、
前記サンギヤーに噛合う第一歯車及び前記第三サンギヤーに噛合う第二歯車を一体的に備えたプラネットピニオンと、
前記プラネットピニオンを回転自在に支持して前記回転体を構成するプラネットキャリアと、
前記プラネットキャリアと前記第三サンギヤーシャフトとの間に介設され締結により前記プラネットキャリアと前記第三サンギヤーシャフトとの間の結合を調節する摩擦クラッチ機構と、
前記摩擦クラッチ機構の締結により前記結合の摩擦トルクを調節するクラッチアクチュエーターと、
を備えた2段変速装置。 - 請求項3又は4記載の2段変速装置であって、
前記サンギヤーへの回転入力は、モーターからドライブギヤー及びドリブンギヤーを介して行う、
2段変速装置。 - 請求項3~5の何れか1項に記載の2段変速装置であって、
前記クラッチアクチュエーターと前記摩擦クラッチ機構との間に前記締結を行わせるための押圧力調整手段を備え、
前記押圧力調整手段は、相対回転自在に支持され歯数が異なる第一差動ギヤー及び第二差動ギヤーと、前記第一差動ギヤー及び第二差動ギヤー間の相対回転を軸推力に変換するトルクカムと、前記第一差動ギヤー及び第二差動ギヤーに噛合い前記クラッチアクチュエーターから回転入力を受けるクラッチピニオンと、前記トルクカムが変換した軸推力を受けて前記締結を行わせる押圧部材とを備えた、
2段変速装置。 - 請求項3~5の何れか1項に記載の2段変速装置であって、
前記クラッチアクチュエーターと前記摩擦クラッチ機構との間に前記締結を行わせるための押圧力調整手段を備え、
前記押圧力調整手段は、相対回転自在に支持され歯数が異なる第一差動ギヤー及び第二差動ギヤーと、前記第一差動ギヤー及び第二差動ギヤー間の相対回転を軸推力に変換するトルクカムと、前記第一差動ギヤー及び第二差動ギヤーに噛合い前記クラッチアクチュエーターから回転入力を受けるクラッチピニオンと、前記締結のための押圧力を発生する弾性体と、前記弾性体の押圧力を受けて前記締結を行わせ前記トルクカムが変換した軸推力を受けて前記弾性体の押圧力を減ずる押圧力調整部材とを備えた、
2段変速装置。 - 請求項2記載の噛合いクラッチ機構を用いた2段変速装置であって、
低速ドライブギヤー及び高速ドライブギヤーを備えて回転入力受けるインプットシャフトと、
前記低速ドライブギヤーに噛合する低速ドリブンギヤー及び前記高速ドライブギヤーに噛合する高速ドリブンギヤーと出力用のドライブピニオンとを備えたアウトプットシャフトと、
前記インプットシャフト又は前記アウトプットシャフトは、前記トルク伝達軸を構成し、
前記インプットシャフトが前記トルク伝達軸を構成する場合は、前記低速ドライブギヤーが前記回転体を構成すると共に前記低速ドリブンギヤーが前記アウトプットシャフトに固定され、
前記アウトプットシャフトが前記トルク伝達軸を構成する場合は、前記低速ドリブンギヤーが前記回転体を構成すると共に前記低速ドライブギヤーが前記インプットシャフトに固定され、
前記インプットシャフト及び前記インプットシャフトに回転自在に備える前記高速ドライブギヤー間の結合を調節する摩擦クラッチ機構を備え又は前記アウトプットシャフト及び前記アウトプットシャフトに回転自在に備える前記高速ドリブンギヤー間の結合を調節する摩擦クラッチ機構を備え、
前記摩擦クラッチ機構の締結調節により前記結合の摩擦トルクを調節するクラッチアクチュエーターと、
を備えた2段変速装置。 - 請求項8記載の2段変速装置であって、
前記クラッチアクチュエーターと前記摩擦クラッチ機構との間に前記締結を行わせるための押圧力調整手段を備え、
前記押圧力調整手段は、前記締結のための押圧力を発生する弾性体と、前記弾性体の押圧力を受けて前記締結を行わせ前記クラッチアクチュエーターに結合された押圧力調整部材とを備え、
前記クラッチアクチュエーターは、前記押圧力調整部材を駆動して前記弾性体の押圧力を調整する、
2段変速装置。 - 請求項1記載の噛合いクラッチ機構を用いた2段変速装置であって、
回転入力を受けるサンギヤーと、
前記サンギヤーにプラネットピニオンを介して噛合い前記回転体を構成するインターナルギヤーと、
前記インターナルギヤーに相対回転自在に支持され前記プラネットピニオンを回転自在に支持するプラネットキャリアと、
前記インターナルギヤーとプラネットキャリアとの間に介設され締結により前記インターナルギヤーと前記プラネットキャリアとの間の結合を調節する摩擦クラッチ機構と、
前記摩擦クラッチ機構の締結調節により前記結合の摩擦トルクを調節するクラッチアクチュエーターと、
前記プラネットキャリアに結合され外部に突出配置された出力軸と、
を備えた2段変速装置。 - 請求項1記載の噛合いクラッチ機構を用いた2段変速装置であって、
回転入力を受けるサンギヤーと、
外部に突出配置された出力軸を有する第三サンギヤーと、
前記サンギヤーに噛合う第一歯車及び前記第三サンギヤーに噛合う第二歯車を一体的に備えたプラネットピニオンと、
前記プラネットピニオンを回転自在に支持して前記回転体を構成するプラネットキャリアと、
前記プラネットキャリアと前記サンギヤーとの間に介設され締結により前記プラネットキャリアと前記サンギヤーとの間の結合を調節する摩擦クラッチ機構と、
前記摩擦クラッチ機構の締結により前記結合の摩擦トルクを調節するクラッチアクチュエーターと、
を備えた2段変速装置。 - 請求項3~11の何れか1項に記載の2段変速装置であって、
前記摩擦クラッチ機構のスリップを検出するセンサーと、
前記検出したスリップに応じて前記クラッチアクチュエーターを制御するコントローラーと、
を備えた2段変速装置。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2022565192A JPWO2022113709A1 (ja) | 2020-11-26 | 2021-11-08 | |
EP21897684.3A EP4253783A1 (en) | 2020-11-26 | 2021-11-08 | Meshing clutch mechanism and two-speed transmission |
CN202180079326.6A CN116583682A (zh) | 2020-11-26 | 2021-11-08 | 啮合离合器机构以及两级变速装置 |
US18/039,119 US20240003390A1 (en) | 2020-11-26 | 2021-11-08 | Meshing clutch mechanism and two-speed transmission |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2020206327 | 2020-11-26 | ||
JP2020-206327 | 2020-11-26 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2022113709A1 true WO2022113709A1 (ja) | 2022-06-02 |
Family
ID=81755802
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2021/040922 WO2022113709A1 (ja) | 2020-11-26 | 2021-11-08 | 噛み合いクラッチ機構及び2段変速装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US20240003390A1 (ja) |
EP (1) | EP4253783A1 (ja) |
JP (1) | JPWO2022113709A1 (ja) |
CN (1) | CN116583682A (ja) |
WO (1) | WO2022113709A1 (ja) |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS52145655A (en) * | 1976-05-28 | 1977-12-03 | Borg Warner | Selffalignment bearing assembly for clutch release |
JP2016187981A (ja) * | 2015-03-30 | 2016-11-04 | Ntn株式会社 | 四輪駆動車の差動制限装置 |
US20160369873A1 (en) * | 2015-06-19 | 2016-12-22 | Hyundai Motor Company | Transmission apparatus of hybrid vehicle |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6290044B1 (en) * | 2000-04-03 | 2001-09-18 | General Motors Corporation | Selectable one-way clutch assembly |
US6505721B1 (en) * | 2000-05-25 | 2003-01-14 | Means Industries, Inc. | Planar one-way clutch |
US6615965B2 (en) * | 2001-05-18 | 2003-09-09 | Epx, L.P. | Planar over-running clutch and method |
DE10196484B4 (de) * | 2001-06-05 | 2014-03-06 | Valeo | Vorrichtung zum Sperren der Zahnräder einer Kraftübertragung |
FR2952677B1 (fr) * | 2009-11-18 | 2011-12-09 | Snecma | Dispositif de changement du rapport de transmission entre un arbre de turbine et un arbre d'un demarreur-generateur d'un moteur d'aeronef |
-
2021
- 2021-11-08 JP JP2022565192A patent/JPWO2022113709A1/ja active Pending
- 2021-11-08 US US18/039,119 patent/US20240003390A1/en active Pending
- 2021-11-08 WO PCT/JP2021/040922 patent/WO2022113709A1/ja active Application Filing
- 2021-11-08 EP EP21897684.3A patent/EP4253783A1/en active Pending
- 2021-11-08 CN CN202180079326.6A patent/CN116583682A/zh active Pending
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS52145655A (en) * | 1976-05-28 | 1977-12-03 | Borg Warner | Selffalignment bearing assembly for clutch release |
JP2016187981A (ja) * | 2015-03-30 | 2016-11-04 | Ntn株式会社 | 四輪駆動車の差動制限装置 |
US20160369873A1 (en) * | 2015-06-19 | 2016-12-22 | Hyundai Motor Company | Transmission apparatus of hybrid vehicle |
Also Published As
Publication number | Publication date |
---|---|
EP4253783A1 (en) | 2023-10-04 |
CN116583682A (zh) | 2023-08-11 |
JPWO2022113709A1 (ja) | 2022-06-02 |
US20240003390A1 (en) | 2024-01-04 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US7097584B2 (en) | Synchronization device for a dual clutch gearbox based on at least one planetary gear set, and corresponding dual clutch gearbox | |
EP2662256B1 (en) | Vehicle motor drive device and automobile | |
JP5876410B2 (ja) | 動力伝達装置 | |
US20060025278A1 (en) | Transmission devices, for ground vehicles and more particularly for motors-cars | |
CN103813922A (zh) | 带电动机的驱动单元 | |
KR20120098812A (ko) | 전기식 동력전달장치 | |
KR20020070482A (ko) | 육상 차량, 특히 자동차용 변속 장치 | |
JP2004138131A (ja) | 自動車のパワートレーンにおけるシンクロ機構の操作装置 | |
JPS6112139B2 (ja) | ||
WO2021110154A1 (zh) | 智能化自适应自动变速器 | |
JP6996667B2 (ja) | 動力伝達経路切換装置および2段変速機 | |
US20090273156A1 (en) | Planetary gear transmission and vehicle using same | |
US8469855B2 (en) | Two-speed transmission module with passive automatic shifting | |
JP2001517762A (ja) | 変速機 | |
JP2023041927A (ja) | 動力伝達経路切換装置 | |
CN110296194B (zh) | 一种行星式三挡换挡装置 | |
KR102356303B1 (ko) | 이륜 차량용 2단 변속장치 | |
WO2022113709A1 (ja) | 噛み合いクラッチ機構及び2段変速装置 | |
CN100394070C (zh) | 用于机动车例如轻型机动车的传动装置 | |
RU2300032C1 (ru) | Бесступенчатая трансмиссия, механизм реверсирования, модуль варьирования и управляемый ограничитель диапазона передаточных чисел | |
KR101467058B1 (ko) | 변속 시 토크 드롭이 방지된 변속장치 | |
JP2003004065A (ja) | 摩擦係合装置 | |
JP2006097886A (ja) | トルク伝達装置 | |
KR20220097163A (ko) | 감속기 | |
WO2022019063A1 (ja) | 動力伝達経路切換装置および2段変速機 |
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: 21897684 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2022565192 Country of ref document: JP Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 202180079326.6 Country of ref document: CN |
|
WWE | Wipo information: entry into national phase |
Ref document number: 18039119 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
ENP | Entry into the national phase |
Ref document number: 2021897684 Country of ref document: EP Effective date: 20230626 |