WO2004010028A1 - Dispositif de changement de vitesse progressif - Google Patents

Dispositif de changement de vitesse progressif Download PDF

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Publication number
WO2004010028A1
WO2004010028A1 PCT/JP2003/009265 JP0309265W WO2004010028A1 WO 2004010028 A1 WO2004010028 A1 WO 2004010028A1 JP 0309265 W JP0309265 W JP 0309265W WO 2004010028 A1 WO2004010028 A1 WO 2004010028A1
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WO
WIPO (PCT)
Prior art keywords
power
wheel
rolling elements
shaft
transmission
Prior art date
Application number
PCT/JP2003/009265
Other languages
English (en)
Japanese (ja)
Inventor
Suenori Tsujimoto
Original Assignee
Suenori Tsujimoto
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Suenori Tsujimoto filed Critical Suenori Tsujimoto
Priority to AU2003281545A priority Critical patent/AU2003281545A1/en
Publication of WO2004010028A1 publication Critical patent/WO2004010028A1/fr

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Classifications

    • 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
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/26—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the motors or the generators
    • 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
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
    • 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
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/40—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the assembly or relative disposition of components
    • B60K6/405—Housings
    • 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
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • 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
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
    • B60K6/54—Transmission for changing ratio
    • B60K6/543—Transmission for changing ratio the transmission being a continuously variable transmission
    • 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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/40—Gearings providing a continuous range of gear ratios in which two members co-operative by means of balls, or rollers of uniform effective diameter, not mounted on shafts
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

Definitions

  • the present invention relates to a transmission, and more particularly, to a friction type transmission capable of changing a gear ratio steplessly.
  • a forward / reverse continuously variable transmission in which a large number of small-diameter spheres are arranged is described.
  • a large number of spheres of the continuously variable transmission extend in the radial direction of the rotating plate, and are supported by a fixed plate disposed between the pair of rotating plates so as to be tiltable with respect to the input shaft and the output shaft. It is rotatably held on a shaft.
  • the continuously variable transmission rotates a small-diameter sphere at the periphery of the large-diameter rotary plate where the peripheral speed is highest, the rotation speed of the sphere becomes extremely high.
  • an automobile engine rotates at about 100 to 800 revolutions per minute
  • an aircraft or marine turbine engine rotates at about several thousand to tens of thousands of revolutions per minute.
  • the motor rotates at about 100 to 300 rotations per minute Is done. For this reason, even if forced lubrication is applied to the bearing portion of the rotating shaft that supports the sphere, a large power loss occurs in the bearing portion.
  • the present invention has been made in view of such circumstances, and has a simple structure, high transmission efficiency, low weight, and low cost that can transmit large power. It is intended to provide a step transmission.
  • a transmission according to the present invention comprises: a first and a second power wheels having circular engagement portions provided at a distal end thereof arranged to face each other; and a first power wheel formed at a tapered end portion. , Frictionally engage with the engaging portions of these power wheels via the second inclined surface, and rotate while rotating along these engaging portions.
  • a plurality of first rolling elements that revolve around the center axis of the wheel and frictionally engage with the peripheral surfaces of two adjacent first rolling elements, and the power wheel while rotating together with the first rolling elements;
  • a plurality of second rolling elements orbiting about the central axis of the second rolling element, and frictionally engaging with the peripheral surface of the second rolling element, the center of the power wheel being pressed by the first and second power wheels.
  • the first rolling element biased in the direction of the axis is supported via these second rolling elements, and the first rolling element and the second rolling element are separated from each other. And a support wheel for holding each at equal intervals in the circumferential direction.
  • the first rolling element has a tilt with respect to the center axis and a tilt corresponding to the tilt in accordance with at least one axial position of the first and second power wheels and the support wheel.
  • the distance between the engaging position of the engaging portion on the inclined surface of the and the rotating shaft is set.
  • the rotation of the input shaft is transmitted to the first rolling element by one of the first and second power wheels and the supporting wheel via the second rolling element, and the rotation of the input shaft is performed by the first rolling element.
  • the rotation output can be output to the output shaft via the other of the first and second power wheels.
  • the first rolling elements are pressed against the first and second inclined surfaces disposed on both sides by the engaging portions of the first and second power wheels, respectively. Therefore, the power wheel is urged in the direction of the central axis.
  • the peripheral surface of each of the first rolling elements is frictionally engaged with the peripheral surface of each of the two second rolling elements supported by the support wheel, so that the forces along the circumferential direction of the engaging portions are balanced.
  • each of the second rolling elements frictionally engages with two adjacent first rolling elements, so that a force along a circumferential direction of the engaging portion is balanced, and these first rolling elements are balanced.
  • the rolling elements and the second rolling elements are respectively held at equal intervals in the circumferential direction along the engaging portion of the power wheel. And the first, second, and so on.
  • the support wheel is formed of a central wheel provided on an input shaft concentric with the central axis, and the central wheel has a circumferential groove on the outer peripheral portion where the second rolling element rolls. Is preferred.
  • the driving force branched from the input shaft via the driving force branching mechanism is transmitted to one of the first and second power wheels.
  • the first and second power wheels are preferably used. It is also possible to fix either one of them and the support wheel so that they do not rotate.
  • the rotation direction of one of the first and second wheels and the center wheel is in the opposite direction, the revolving speed of the first and second rolling elements is reduced, and the input shaft and, therefore, the start-up of the motor, that is, the start-up In this case, the load of potential energy at the time of rotation is reduced, thereby increasing the responsiveness to fluctuations in the rotation speed of the prime mover.
  • the rotation direction of one of the first and second power wheels and the center wheel is in the same direction, the rotation speed of the first and second rolling elements is reduced, and each of these rolling elements is reduced. The number of rolling stakes decreases, which increases transmission efficiency.
  • an on-way clutch interposed between the driving force source and a center wheel, and a rotor connected to the center wheel
  • a first motor generator ; a second motor generator having a rotor connected to one of the first and second power wheels; an output shaft driven by the other of the first and second power wheels; And a clutch interposed between the shaft and a driven device operated by the shaft.
  • the support wheel is formed by a center wheel provided on a hollow shaft which is concentric with the center shaft and cannot rotate, and further comprises a motor having a rotor connected to one of the first and second power wheels.
  • a generator may be provided, and an operating gear unit connected to the other of the first and second power wheels and the left and right drive shafts. In this case, the internal space of the motor generator can be used efficiently.
  • the center wheel is mounted on the input shaft so as to be immovable in the circumferential direction and slidable in the axial direction, and can control the inclination of the first rolling element with respect to the center axis.
  • the first and second power wheels can be connected to each other via a transmission having a constant speed ratio.
  • the support wheel is formed of a guide that surrounds the first and second rolling elements and frictionally engages with a peripheral surface of the second rolling element, and is provided between the other of the first and second power wheels and an output shaft. It may be through a clutch. In this case, the alignment between the first rolling element and the second rolling element can be further ensured.
  • the rotation of the input shaft is transmitted to the first rolling element by one of the first and second power wheels and the supporting wheel via the second rolling element, and the first rolling element rotates.
  • the first and second power wheels are connected to each other via a speed change mechanism having a constant speed ratio.
  • the rotation of the input shaft is transmitted to the first rolling element, and the rotation output from the center wheel rotated through the second rolling element can be taken out to the output shaft.
  • the rotation output from the center wheel rotated through the second rolling element can be taken out to the output shaft.
  • FIG. 1 is a longitudinal section of a transmission according to a first embodiment of the present invention.
  • FIG. 2 is a sectional view of the transmission of FIG. 1 taken along line ⁇ _ ⁇ .
  • FIG. 3 is a sectional view similar to FIG. 1 of a transmission according to a second embodiment.
  • FIG. 4 is an explanatory view of a state in which the transmission according to the third embodiment shown in FIG. 3 is formed for an automobile.
  • FIG. 5 is a longitudinal sectional view of a transmission according to a fourth embodiment formed for a hybrid vehicle.
  • FIG. 6 is a longitudinal sectional view of a transmission according to a fifth embodiment formed for an electric vehicle.
  • FIG. 7 is a cross-sectional view of the transmission of FIG. 6 taken along line W.
  • FIG. 8 is a longitudinal sectional view of a transmission according to a sixth embodiment.
  • FIG. 9 is a cross-sectional view of the transmission of FIG. 8 taken along line X-IX.
  • FIG. 10 is a longitudinal sectional view of a transmission according to a seventh embodiment.
  • FIG. 11 is a longitudinal sectional view of a transmission according to an eighth embodiment formed for a wind turbine generator.
  • FIG. 12 is a longitudinal sectional view of a transmission according to a ninth embodiment.
  • FIG. 13 is a cross-sectional view of the transmission of FIG. 12 taken along the line ⁇ - ⁇ .
  • 1 and 2 show a transmission according to a first embodiment of the present invention.
  • This transmission is formed as a wide range of industrial continuously variable transmissions including, for example, automobiles, and is formed in a compact structure in which the entirety is housed in a housing 10.
  • the housing 10 includes a cylindrical body 10a having both ends opened, and a lid 10b that closes both ends. 2 and the output shaft 14 penetrate these lids 10b along the central axis C common to both shafts, and are rotatably supported via appropriate bearings such as ball bearings.
  • a suitable seal member is disposed at a portion where the input shaft 12 and the output shaft 14 penetrate to prevent leakage of lubricant and the like and prevent foreign substances from entering the housing 10.
  • the lid 10b through which the input shaft 12 penetrates is recessed inward, so that the entire axial length of the power transmission system can be shortened.
  • the first drum 16 rotatably supported on the input shaft 12 and the second drum 18 coupled to the output shaft 14 are arranged inside the nozzle 10. .
  • the first drum 16 has a disk-shaped portion 16a rotatably supported on the input shaft 12 via, for example, a ball bearing, and the second drum 18 has a hollow disk-shaped portion 18a. It is integrally connected to the output shaft 14 via the boss 14a.
  • the distal end portion 12a of the input shaft 12 is inserted into the boss portion 14a, and is rotatably supported via bearings at two positions separated in the axial direction. I have.
  • the nozzle 10 extends beyond the outer peripheral portion of the second drum 18 toward the first drum 16, and the tip thereof extends to the first drum 16.
  • a connecting member 20 fixed to the outer peripheral portion of the drum 16 is rotatably supported by a boss portion 14a of the output shaft via an axial bearing 22.
  • the axial bearing 22 acts as a force in the opposite direction via the second drum 18 and the second drum 18 to cancel each other.
  • the housing 10 can be formed in a lightweight structure.
  • the boss portion 14a of the output shaft 14 is fixed to the disc-shaped portion 18a instead of being formed integrally with the disc-shaped portion 18a of the second drum 18. It can be formed as a separate member.
  • the first and second drums 16 and 18 have annular inner holes 26 and 28 opposed to each other at positions close to the outer peripheral portions thereof.
  • the first, second, and third wheels 30 and 32 can be moved only in the axial direction along the central axis C by, for example, a spline (not shown). Will be accommodated.
  • the front ends of these power wheels 30 and 32 are formed with first and second engaging portions 30a and 32a, which are frictionally engaged with a power roller described later.
  • the seven first rolling elements that is, the power rollers 40, are located between the power wheels 40 and 32 at positions separated from the center axis C with respect to the rotation axis r. Is pressed from both sides.
  • 3 2 engagement portion 3 that presses frictionally engage these power rollers 4 0 0 a, 3 2 a is Bruno, 0 Wah Russia over La 4 0 rotation axis r and between the center axis C of the It has a circular shape with a radius larger than the distance.
  • Each of the power rollers 40 sandwiched between the power wheels 30 and 32 has a hollow structure in which both ends are formed in a tapered or hemispherical shape. 1, 2nd inclined surface 40a, 40b Force S no. ⁇ Frictionally engages with the engaging portions 30a and 32a of the wheels 30 and 32.
  • each of the seven second rolling elements that is, the spherical planetary rollers 44
  • each of the planetary rollers 44 is arranged in the circumferential direction of two power rollers adjacent to each other. Fit into groove 42.
  • Each of the planetary rollers 44 rolls along the circumferential groove 42 and frictionally engages with a circumferential surface formed on the bottom surface of the circumferential groove 42 at a contact point s (see FIG. 2).
  • the rotation axis p passing through the center point of these planetary rollers 44 is closer to the center axis C, that is, radially inward than the straight line connecting the rotation axes r of the two adjacent power rollers 40. To position.
  • each power roller 40 is located radially outward from the center axis C with respect to a straight line connecting the rotation axes ⁇ of the two planetary rollers 44 adjacent to each other.
  • the planetary rollers 44 are not limited to the spherical structure as shown, but may be formed in a plate-like or cylindrical structure.
  • the respective first rollers 40 become the first and second inclined surfaces 4.
  • a support wheel 46 which is a central wheel formed integrally with the input shaft 12 in this embodiment.
  • a circumferential groove formed on the outer peripheral surface of the support wheel 46 is provided with a guide groove 46 a that frictionally engages with the planetary roller 44 to prevent axial movement and guides in the circumferential direction. It works. With this, no ,. Circumferential forces acting on the word rollers 40 and the planetary rollers 44 cancel each other out and are held at equal intervals in the circumferential direction about the center axis C.
  • the circumferential groove 42 formed on the power roller 40 and the guide groove 46 a of the support wheel 46 are formed by a smooth annular curved surface. The axial movement of the power roller 4 ⁇ and the support wheel 46 is prevented. Due to this, no. When the wheels 30 and 32 move in the same direction along the central axis C while pressing the power rollers 40 sandwiched therebetween from both sides, the power rollers 40 move more than the rotation axis r. Engagement parts 30a, 3
  • the distance between the engagement position of the engagement portions 30a, 30b on the inclined surfaces 40a, 40b and the rotation axis r is: It is set at an angle of inclination centered on the contact s of the warlor 40.
  • the power wheels 30 and 32 have pressure chambers 26 a and 28 a partitioned into annular bores 26 and 28, respectively, and the pipelines 36 and 28.
  • a speed ratio changing means is formed by the pressure fluid control device supplied through the pressure fluid control device 38 and the pressure chambers 26 a and 28 a from a pressure fluid source (not shown) through the pressure fluid control device.
  • the driving force splitting mechanism 50 of the present embodiment includes an external gear 52 provided on the outer periphery of the input shaft 12 and a support shaft 54 projecting from the inner surface of the lid 10b on the input shaft 12 side.
  • An intermediate gear 56 that is rotatably mounted and mates with the external gear 52, and an internal gear that is provided on the disk-shaped portion 16a of the first drum 16 and mates with the intermediate gear 56. 5 8 and. Since the intermediate gear 5 6 is interposed between the external gear 52 and the internal gear 58, the speed of the external gear 52 and the internal gear 58 is inversely proportional to the number of teeth. Rotate in opposite directions by the ratio.
  • the first power wheel 30 and the support wheel 46 rotate the input shaft 12 in rotation.
  • the speed-changed rotation output transmitted to the power roller 40 and output from the second power wheel 32 can be output to the output shaft 14.
  • the driving force extracted from the output shaft 14 can be transmitted to a driven device such as a propeller shaft of an automobile, for example.
  • the center wheel 46 is driven by a power roller via a planetary roller 44. Rotate 40 in the same direction as this center wheel 46.
  • the internal gear 58 through the external gear 52 of the input shaft 12 and the intermediate gear 10 causes the first drum 16 to rotate in the opposite direction to the input shaft 12 at a predetermined speed ratio. Rotate.
  • Each power roller 40 has a first and a second power wheel from both sides.
  • the first drum 16 and the center wheel 46 cause the input shaft 12 to be pressed by the center wheels 46 through the planetary rollers 44 and pressed by the rollers 30 and 32.
  • the rotation is transmitted to the power roller 40.
  • each power roller 40 rotates while revolving around the center wheel 46.
  • the second power wheel 32 becomes the first power wheel. It rotates in the same direction as the wheel 30, and the driving force is transmitted to the output shaft 14 through the second drum 18.
  • the trajectory radii drawn by 30a and 3Ob around the rotation axis r are represented by rl and r2.
  • each power roller is moved.
  • the second nozzle wheel 32 rotates at an increased speed, and the reduced rotational driving force is transmitted to the output shaft 14 through the second drum 18.
  • the first, second When the wheels 30 and 32 are moved to the input shaft 12 side, the respective power rollers 40 are inclined to the input shaft 12 side so that r 2 ⁇ r 1, and the engagement portion 32 a Peripheral speed is lower than engagement part 30a And Thus, the second wheel, the second power wheel 32, is rotated at a reduced speed, and the reduced driving force is transmitted to the output shaft 14 through the second drum 18.
  • the input of the driving force is performed through both the first drum 16 and the center wheel 46 via the planetary rollers 44, and the input is lower than the conventional one-way input.
  • the speed ratio can be reduced with respect to rotation.
  • the pair of power wheels 30 and 32 that press the roller 40 rotate with each of the drums 16 and 18. Driving force can be efficiently transmitted without hindering rotation and revolution of the word rollers 40, and transmission loss can be significantly reduced.
  • the engaging portion 30a of the first power wheel 30 that transmits the driving force by changing the speed is frictionally engaged with the power roller 40 near the maximum radial position of the transmission, It is possible to simultaneously reduce the size and weight while increasing the workload.
  • the central wheel 46 is arranged along the central axis C, the speed change device can be made robust and the durability can be improved.
  • the power roller 40 and the planetary roller 44 can be used. Are maintained at equal intervals around the center wheel 46 without requiring a special support mechanism, thereby reducing the loss of driving force due to rotation and further improving transmission efficiency. Can be done.
  • FIG. 3 shows a transmission according to a second embodiment. Since various embodiments described below are basically the same as the above-described embodiments, similar parts are denoted by the same reference numerals, and detailed description thereof will be omitted.
  • the driving force branching mechanism 50 is formed by a planetary gear set, and the first drum 16 and the first drum 16.
  • the present embodiment differs from the above-described embodiment only in that the wheel 30 is rotated in the same direction as the input shaft 12.
  • a support shaft 54 for supporting the intermediate gear 56 is provided on the disk-shaped portion 16a of the first drum 16 and the internal gear 58 is connected to the input shaft 12 side.
  • the lid 10b of the camera Provided on the lid 10b of the camera.
  • each of the power rollers 40 is rotationally driven in the same direction by both the center wheel 46 and the first power wheel 30 with the rotary shaft interposed therebetween, so that the rotation speed thereof is reduced. Be confused Thereby, the rolling resistance of each power roller 40 is reduced, and the transmission efficiency is improved.
  • the speed ratio of the rotation speed of the output shaft 14 to the rotation speed of the input shaft 12 is the first and second nose.
  • Various settings can be made according to the effective diameter of each of the wheel 30, 32, the center wheel 46, and the power roller 40, that is, the diameter actually formed by the engaging portion of each member.
  • a forward rotation region that rotates in the same direction as the input shaft 12 and a reverse rotation region that rotates in the opposite direction to the input shaft 12 can be provided.
  • the forward rotation region and the reverse rotation region be in a one-to-one relationship, and that the intermediate point be a neutral position. Further, when used for construction equipment such as bulldozers, it is preferable to set the ratio of the forward or forward rotation region to the reverse or reverse rotation region to be 2 to 3. When it is used as a vehicle tractor, it is preferable that the ratio of the forward area to the reverse area is about 5 to 2. Thus, it is easy to change the speed ratio of the speed change device according to the application, and the efficiency and convenience of the speed change device are improved.
  • FIG. 4 shows a transmission according to a third embodiment.
  • the transmission shown in FIG. 3 is optimized for an automobile, so that the forward rotation region for forward movement is expanded, and the output shaft 14 and the propeller shaft 60 as a driven device are enlarged. Between them, an intervening clutch mechanism 62 is interposed.
  • Such a combined clutch mechanism 62 for connecting or separating the output shaft 14 and the propeller shaft 58 can be formed in an appropriate structure.
  • the combined clutch mechanism 62 of the present embodiment includes a cam block 64 non-rotatably connected to the output shaft 14 by a suitable means such as a screw, for example, and a propeller shaft 60.
  • a shifter 68 that is non-rotatably mounted on the top and is movable in the axial direction by a shift lever 66. Both ends of the shifter 68 are formed with teeth or ridges extending in the radial direction, and are combined with the teeth or ridges formed on the cam block 64 and the control housing 10c. I can.
  • the shifter 168 engages with the cam block 64, thereby connecting the input shaft 14 and the propeller shaft 60. Is done.
  • the shift lever 68 is engaged with the control housing 10 c, whereby the propeller shaft 60 is separated from the input shaft 14. This propeller shaft 60 is It is fixed to the housing 10 c to prevent rotation of the propeller shaft.
  • the opening shaft 60 is separated from both the input shaft 14 and the control housing 10c.
  • the shift lever 66 can be arranged at the P position or the N position. Only then can a mechanical or electrical interlocking mechanism be provided to allow the engine to start. As a result, when the crankshaft of the engine is connected to the propeller shaft 60 via the transmission, the engine cannot be started, and an excessive load on the engine is prevented. At the same time, runaway of the vehicle when the engine is started can be reliably prevented.
  • the shift lever 66 is located at the position P, the propeller shaft 60 is made unrotatable, so that braking during parking can be secured and the movement of the vehicle can be prevented.
  • the propeller shaft 60 can freely rotate to secure the rotation of the engine trouble and the like. It is possible to secure the movement of the vehicle, for example, by towing when the vehicle is unable to run.
  • FIG. 5 shows a transmission according to a fourth embodiment.
  • This embodiment is formed for a hybrid vehicle, and the first drum 16 is driven to rotate by a motor generator instead of the driving force branching mechanism 50 in the above-described embodiment. can do.
  • the coupling 72 is attached to the end of the input shaft 12 via a one-way clutch 70, and the rotor 76 of the first motor generator 74 is connected to the nut 78. It is fixed with.
  • This one-way clutch 70 is preferably formed by a coupling with a damper for damping the rotational vibration of an engine connected via a spline joint, for example. When the number of revolutions is equal to or less than the number of revolutions of the drive shaft of the engine connected via the power ring 72, these input shafts 12 and the drive shaft are connected.
  • the rotor 82 of the second motor generator 80 is fixed to the connecting member 20.
  • the stators 75, 81 of these first and second motor generators 74, 80 are fixed inside the body 10a of the housing, respectively, and the rotors 76, 82 are Opposite to the stator, permanent magnets 76a and 82a, for example, neodymium magnets, are arranged at equal intervals along the periphery thereof, and are formed as a so-called PM motor.
  • the housing 10 housing such motor generators 74 and 80 preferably has a liquid-tight interior.
  • first and second motor generators 74 and 80 act as drive motors which are rotated by electric power from a battery as necessary by a motor generator controller (not shown). Or act as a generator to power the battery, so that kinetic and electrical energy can be maintained even when the weight of the vehicle fluctuates significantly due to the load or the number of passengers. Can be converted efficiently. For example, it increases the acceleration force when starting a car and increases the energy efficiency when decelerating. By recovering at a low rate, fuel efficiency can be reduced.
  • the transmission equipped with the two motor generators 74 and 80 can be operated in various modes according to the situation of the vehicle. Will be described. If the remaining amount of the battery is insufficient, the vehicle is brought into a braking state in advance, and the shift lever 66 is arranged at the position D. In addition, the first and second motor generators 74 and 80 are brought into a power generation state via the motor generator control device. In this state, when the input shaft 12 is rotated by an engine (not shown), the rotor 76 of the first motor generator 74 is rotated at the same speed in the same direction as the drive shaft, and charges the battery.
  • the second drum 18 and the second power wheel 32 remain stationary, and the lower roller 40 has its second inclined surface 40 b Is frictionally engaged with the engagement portion 32 a, and revolves while rotating along the second wheel 32. This causes the first power wheel 30 and the first drum 16 to rotate the rotor 82 of the second motor generator 80 on the first inclined surface 40a, thereby removing the battery. Charge.
  • the input shaft 12 is fixed to the housing 10 and does not rotate.
  • the second motor generator 80 is driven, the power roller 40 rolls along the engaging portion 30a of the first power wheel 3 ⁇ , thereby Then, the second No. 3 wheel 32 is rotated at a speed relative to the first power wheel, and 2 Drum 18, output shaft 14 and propeller shaft 60 rotate.
  • the driving by the second motor generator 80 is controlled by controlling the rotation of the second motor generator 80 when the running resistance of the vehicle is the smallest.
  • the speed can be changed from a state in which the vehicle is started forward or backward to the cruising speed, and therefore, it is possible to travel with the minimum power by the second motor generator 80 having a small output. Obviously, it is also possible to move the first and second power wheels 30, 32 in the axial direction if necessary.
  • the output shaft 14 rotates. Furthermore, the first, is rotated synchronously with the second Motor generators 7 4, 8 0, Nono 0 Waro over La 4 0 does not rotate, therefore, the output shaft 1 4 same as the input shaft 1 2 speed And the speed ratio becomes 1: 1. Since the movable member of the continuously variable transmission transmits the rotation of the input shaft 12 to the output shaft 14 and the propeller shaft 60 without rotating relatively, the transmission efficiency is highest. In addition, the first and second power wheels 30 and 32 are moved through the speed ratio changing means, and are notched. As in the above-described embodiment, the speed ratio between the input shaft 12 and the output shaft 14 can be changed over a wide range by setting the tilt position of the word roller 40.
  • a hybrid drive suitable for an automobile is formed. If integrated into a car, through a suitable motor generator control It can be operated as follows.
  • the input shaft 12 is driven by the first motor generator 74.
  • the one-way clutch 70 separates the drive shaft of the engine from the input shaft 12. Then, the rotation of the first drum 16 is stopped, the electric power is supplied to the first motor generator 74, and the input shaft 12 is driven to rotate.
  • the motor generator control device rotationally drives the first motor generator 74 with an output corresponding to a signal requested by the driver, which is sent based on, for example, an accelerator pedal (not shown). If the output of the first motor generator 74 is insufficient, the second motor generator 80 is further driven to rotate, and the output shaft 14 is rotated by the driving force required by the driver.
  • the motor generator controller When the vehicle travels at a speed that is efficient for driving by the engine, the motor generator controller reduces the power supplied to the first and second motor generators 74, 80, and the engine, which is the main driving force source, To rotate the output shaft 1 2. Also, when the driver decelerates the accelerator pedal when decelerating the car, the rotation speed of the engine decreases, and the on-way clutch 70 separates the input shaft 12 from the engine. Then, the first motor generator 74 is operated as a generator, recovers kinetic energy associated with the deceleration of the vehicle as electric energy, and stores it in the knotter.
  • the second motor generator 80 is also operated as a generator, and the first and second motor generators are also operated.
  • the speed ratio of this transmission can be increased.
  • the braking force is increased, thereby increasing the amount of power generated by the first and second motor generators 74, 80 and hence the braking force.
  • the transmission according to the fourth embodiment like the transmissions according to the above-described embodiments, not only exhibits quick response and high transmission efficiency, but also has a large acceleration force when starting and accelerating. Thus, energy can be recovered with high efficiency at the time of deceleration, thereby making it possible to reduce the fuel consumption of the vehicle.
  • the number of motor generators is not limited to two, but may be one or three or more.
  • FIG. 6 shows a transmission according to a fifth embodiment formed for an electric vehicle.
  • a non-rotatable hollow shaft 13 having one end fixed to the housing 10 extends coaxially with the center axis C in place of the input shaft 12 in the above-described embodiment, and the other end is a boss. 14 a and a hollow output shaft 14.
  • the first and second drums 16 and 18, the boss 14 a and the output shaft 14 are rotatably supported on the hollow shaft 13.
  • the connecting member 20 extends over substantially the entire length of the body 10a of the housing 10 and is supported by the second drum 18 via an axial bearing 22 instead of the boss 14a.
  • a large number of permanent magnets 84 are fixed to the outer periphery of the connecting member 20, and a stator coil 86 is fixed to the inner peripheral surface of the body 10 a opposed thereto.
  • the connecting member 20 functions as a rotor of the motor generator 88, and drives the first drum 16 and thus the first power wheel 30 to rotate.
  • This motor energy In order to make the radiator 88 have a liquid-tight structure, it is necessary to place the first drum 16 between the fixed shaft 13 and the connecting member 20 and the partition plate 11 in the housing 10 respectively A seal member is provided.
  • a planetary gear set 90 functioning as a final reduction mechanism is arranged in the housing 10 around the output shaft 14 and the rotational output of the output shaft 14 is transmitted to the left and right drive shafts.
  • a differential gear device 92 for transmitting to 94 and 96 is arranged.
  • the left and right drive shafts 94, 96 are rotatably supported in the hollow shaft 13.
  • the planetary gear set 90 and the differential gear set 92 are interlocked with each other via a carrier 91 of the planetary gear set 90 and laid out.
  • the trajectory radii drawn at the center are denoted by r 1 and r 2.
  • r 2 r 1
  • the power wheel 30 rotates the second power wheel 32 at a constant speed.
  • the respective power rollers 40 are inclined rightward so that r 2> r 1.
  • the peripheral speed of the engaging part 3 2a is The speed becomes larger than 30a, and the second No. 3 wheel 32 is accelerated.
  • first and second When the wheels 30 and 32 are moved to the left, the respective power rollers 40 are inclined to the left, so that r 2 ⁇ r 1, and the peripheral speed of the engaging portion 32 a becomes the engaging portion 30 a As it becomes smaller, the second power wheel 32 is decelerated and rotates.
  • the output shaft 14 rotates, and the planetary gear unit 90 reduces the speed to a predetermined reduction ratio to support a plurality of planetary gears.
  • the differential gear device 9 2 is driven via the carrier 91.
  • a planetary gear 93 rotatably supported by a carrier 91 revolves around a center axis C, and a sun gear 95 connected to a left drive shaft 94.
  • the internal gears 9 7 and 9 7 fixed to the right drive shaft 9 6 are rotationally driven.
  • the axial ball bearing 22 of the present embodiment cancels the reaction force of each of the power wheels 30 and 32 pressing the power roller 40 and also reduces the thrust load acting on the housing 10. .
  • the first and second power wheels 30 and 32 rotate at a constant speed, only the thrust load acts on the axial ball bearing 22.
  • the first and second no-wheels 30 and 32 rotate in synchronism with the rotational speed difference generated according to the tilt angle, and large-capacity bearings are mounted on the left and right sides of the housing as in the conventional case.
  • the transmission efficiency is improved by greatly reducing the loss as compared with the case of mounting.
  • the latest PM motors for electric vehicles that use permanent magnets are more efficient in the low-speed rotation range than conventional electric vehicle motors. Is excellent, but the starting torque is small, and there is a problem that the efficiency is extremely reduced in the field of weakening in the constant output region and in the high-speed rotation region.
  • the transmission according to the fifth embodiment overcomes the problems of the motor for PM electric vehicles, and satisfies the demands for a highly efficient continuously variable transmission for electric vehicles.
  • a space is formed in the rotor of a conventional PM motor for electric vehicles using permanent magnets.
  • the transmission of the present embodiment utilizes the internal space effectively by being housed in this internal space together with the final reduction gear 90 and the differential gear 92.
  • it is suitable as a drive device for an electric vehicle of an FF (front engine drive / front wheel drive) vehicle which is limited by space.
  • FF front engine drive / front wheel drive
  • the first and second power wheels 30 and 32 are formed integrally with the first and second drums, respectively, and the first and second power wheels 30 and 3 are formed integrally with the first and second drums.
  • the tilting of Nono 0 word b over La 4 0 that supported by two rows cormorants also Ru Nodea axial movement of the central wheel Lumpur 4 6.
  • a slide-shaped slider 98 that is slidable in the axial direction and relatively non-rotatable is mounted on the input shaft 12 by, for example, a spline. , Through the planetary rollers 4 4.
  • the center wheel 46 supporting the roller 40 is formed integrally with the slider 98.
  • the slider 98 has a flange portion 98a formed at the end of the input shaft 12 side, and the outer periphery of the input shaft 12 has the flange portion 98a.
  • a cylindrical box portion 100 for receiving 98a is provided.
  • the flange 98a is accommodated in the annular space of the box 100, and the open end of the box 100 is closed with the cover 102. Accordingly, the annular space in the box portion 100 is divided into two pressure chambers 104a and 104b, each of which is formed in a liquid-tight manner.
  • the first and second inclined surfaces 40a and 40b of the word roll 40 form a part of a circle having the swing center q as a base point.
  • the box portion 100 is disposed in a concave portion 16b formed in the disk-shaped portion 16b of the first drum 16, and a roller bearing is provided.
  • the first disk 16 is rotatably supported.
  • the thrust load acting on the first disk 16 is applied to the housing via the support cylindrical portion 106 and the axial bearing 108 connected to the disk-shaped portion 16a.
  • the thrust load acting on the second disk 18 on the opposite side is transmitted from the disk-shaped portion 18a to the boss portion 14 via the ball cam 110 and axially It is transmitted to the housing 10 via the bearing 1 1 2.
  • the pole cam 110 is formed of a normal pressure cam, and generates an axial thrust load according to the size of the tonnolek, and the second disk 18 and therefore the second disk. Automatically adjusts the pressing force of power wheel 40 against power wheel 40. This acts on the first and second disks 16 and 18. These thrust loads cancel each other out in the housing 10 to form a compact and lightweight transmission.
  • a shaft portion 19a extends from the disk-shaped portion 18a of the second disk 18 in the direction of the input shaft 12 and is inserted into the recess of the input shaft 12 to be rotatable. It is supported by.
  • the shaft 18b extending toward the output shaft 14 is inserted into the boss 14a and the output shaft 14 1.
  • the second disk 18 is supported by the rotation axis on the center axis C together with the input shaft 12 and the output shaft 14.
  • the coil spring 114 accommodated in the boss portion 14 does not act on the second disk when the pressing force of the cam 110 is not acting, that is, when the output shaft 14 is stopped. 1 8 and the second power wheel 3 2 are pressed, whereby all of the nozzles are pressed. Maintain the alignment of the warr rollers 40 and the planetary rollers 44 and secure the torque at the beginning of driving.
  • This transmission operates in the same manner as the second embodiment shown in FIG. 3, except that the tilting of the power roller 40 is performed through the axial movement of the central wheel 46.
  • FIG. 10 shows a transmission according to a seventh embodiment.
  • the first and second power wheels 30 and 32 and thus the first and second drums 16 and 18 are connected to each other via a transmission mechanism 120 having a constant gear ratio.
  • the boss portion 14a is formed in a solid structure, and the shaft portion 14b is inserted into the concave portions of the center wheel 46 and the input shaft 12, and is rotatably supported. You.
  • the transmission mechanism 120 in this embodiment is provided outside the output shaft 14.
  • An intermediate gear 1 2 which is rotatably mounted on an external gear 1 2 2 provided on the periphery and a support shaft 1 2 4 protruding from the wall of the connecting member 20, and which is combined with the external gear 1 2 2. 6 and an internal gear 1 28 provided on the output shaft 14 b of the nosing 10 on the side of the output shaft 10 b and corresponding to the intermediate gear 12 6.
  • the first power wheel 30 functions as a driving force combining mechanism that combines the torque of the first drum 16 and the torque of the output shaft 14.
  • the transmission of the present embodiment is different from the transmission of the second embodiment shown in FIG. 3 in that the driving force splitting mechanism 50 is replaced by a driving force combining mechanism 120 and a first drum 16 and an output shaft 14.
  • the input shaft 12 and the output shaft 14 of the transmission shown in FIG. 3 are reversed.
  • the speed ratio of the transmission mechanism that is, the driving force synthesizing mechanism 120, it can be used for various applications.
  • FIG. 11 shows a transmission according to an eighth embodiment.
  • the transmission according to this embodiment is formed for a wind power generator, and a plate 13 2 of a wind turbine 130 is fixed to an input shaft 12 by, for example, a nut 13 4. .
  • the input shaft 12 is formed integrally with the first drum 16, and the tip 12 a is inserted into the boss 14 a forming the center wheel 46, and is rotatably supported and supported. .
  • the second wheel 18 is rotatably mounted on the boss 14a via a ball bearing, and projects inward from the lid 10b on the output shaft 14 side of the housing 10. It is rotatably supported on an annular tubular portion 10 c via an axial bearing 22.
  • This The axial bearing 22 supports not only the thrust load of the second drum 18 but also the thrust load of the plate 13 2 acting via the input shaft 12.
  • the thrust load and the radial load acting on the input shaft 12 in the opposite direction are supported by the axial bearing 23 interposed between the input shaft 12 and the lid 10b on the input shaft side. .
  • the second drum 18 and the input shaft 12 are connected by a driving force branching mechanism 50 which is a speed changing mechanism having a constant speed ratio.
  • a rotatable support shaft 54 is provided on the connecting member 20 fixed integrally with the second drum 18. Therefore, when the input shaft 12 rotates, the intermediate gear 56 is combined with the external gear 56 provided on the input shaft 12 and the internal gear 58 provided on the cover member 10b. Then, it revolves around the central axis C while revolving, and rotates the second drum 18. As a result, the power roller 40 is the first and second nodes.
  • the rotation of the input shaft 12 is transmitted via the wheel 3G, 32, and revolves along the circumferential groove 46a of the central wheel 46 while revolving, via the planetary rollers 44. Rotating the center wheel 4 6, and thus the output shaft 14.
  • the second drum 18 that transmits the rotation of the input shaft 12 to the power roller 40 together with the first drum 16 has a coil spring 29 disposed in its annular inner hole 28.
  • the coil spring 29 keeps the second power wheel 32 pressed against the power roller 40 with a constant pressing force at all times, and maintains a state in which the power roller 40 and the planetary roller 44 are arranged at equal intervals. As a result, the torque at the initial Can be secured.
  • a rotor 13 formed by winding a coil 13 around a core 13 is fastened and fixed with a nut 15.
  • the circumference of the rotor 13 is A compact power generator is formed together with a stator 1339 fixed to the inner surface of the body 10a of the housing 10 with a predetermined gap disposed in the housing.
  • This transmission is rotatably mounted on the top of the table T via a turntable 140 so that the blade 132 can always be arranged in the direction of the wind.
  • the output shaft 14 also functions as a rotating shaft of the generator, thereby reducing the number of parts of the power generation device and reducing the cost. The whole can be reduced in size.
  • by moving the first and second power rollers 30 and 32 in the axial direction to control the inclination angle of the power roller 40 with respect to the center axis C it is possible to respond to the constantly changing wind force. By rotating the rotor 1338 at the optimum gear ratio, the power generation efficiency of the power generator can be improved.
  • FIGS. 12 and 13 show a transmission according to a ninth embodiment.
  • the input shaft 12 is formed into a relatively short hollow structure, and the end wall 14 2 provided at the end on the output shaft 14 side is formed.
  • the dry ling 144 extends from the outer edge to form a gap between the outer periphery of the first drum 16.
  • a guide 144 that covers the gap between the first and second power wheels 30 and 32 is formed at the tip of the driving ring 144.
  • the guide 1 46 supports a planetary roller 44 formed in an annular plate-like structure in the present embodiment through a guide groove 1 46 a having an arcuate cross section formed on the inner surface thereof. Further, the planetary roller 44 is supported by a circumferential groove 42 of the power roller 40 and a ridge 42a projecting from a side wall thereof. Therefore, the guide 146 acts as a support wheel that holds the power roller 40 and the planetary roller 44 at equal intervals in the circumferential direction.
  • this guide 1 46 is the planetary roller 4 4 and the nozzle. ⁇ ⁇
  • each planetary roller 44 frictionally engages with the peripheral surface formed by the bottom surface of the circumferential groove 42 at the contact point s.
  • the rotation axis p of these planetary rollers 44 is more radially away from the center axis C than the straight line connecting the rotation axes r of the two adjacent power rollers 40.
  • the rotation axis r of each power roller 40 is located further radially outward from the center axis C than the straight line connecting the rotation axes p of the two planetary rollers 44 adjacent to each other.
  • each power roller 40 engages a portion separated from the central axis C with respect to the rotation axis r. It is pressed by 30a and 32a, and rotates about the contact point s with the adjacent planetary roller 44. As a result, the engagement portions on the inclined surfaces 40a and 40b
  • the engagement position of 30a and 32a moves, and the distance from the rotation axis r changes.
  • the inclination angle of the rotation axis r of each power roller 40 with respect to the center axis C is simultaneously changed to the same angle, and at the same time, the circumferential groove is formed.
  • Each planetary roller 44 fitted to 42 is also urged by the power roller 40 via the ridge 42a, and the adjacent power roller while maintaining frictional engagement with the guide groove 144a. Rotate all around the same angle around the contact s with 40. As a result, the rotation axis r of the power roller 40 and the rotation axis p of the planetary roller 44 are disposed at substantially the same angle with respect to the center axis C.
  • the connecting member 20 extends from the center of the first drum 16 along the center axis C, is connected to the boss 14a, and the nut 17 is placed on the boss 14a. It is connected to the second drum 18 via an axial bearing 22 fixed at the position.
  • a transmission mechanism 120 acting as a driving force synthesizing mechanism for the first and second drums 16 and 18 is disposed in the concave portion of the second drum 18 so that the intermediate gear 12 26 can rotate freely.
  • a supporting shaft 124 supports the second drum 18 and the axial bearing 22 mechanically.
  • the speed change mechanism 120 has an intermediate gear 122 mounted rotatably on a support shaft 124, an external gear 122 provided on a pos part 14a, and a housing 10 provided on a housing 110. And the first and second drums 16 and 18 at a constant speed ratio as a planetary gear device that revolves around the center axis C while rotating. Rotate.
  • a vane clutch 70 is disposed between the inner peripheral side of the input shaft 12 and the spline shaft 148 connecting the drive shaft of the engine.
  • a motor generator 150 for driving the above-mentioned guide 144 is provided on the outer peripheral side of the input shaft 12.
  • This motor generator 150 is preferably formed by a PM motor, and a number of permanent magnets 152 are fixed to the inner peripheral side of the extension portion 148 of the driving ring 144, and this is combined with the motor generator 150.
  • the stator coils 154 facing each other with a predetermined gap are attached to a cylindrical support portion 156 projecting inward from the housing lid 1 Ob.
  • the transmission according to this embodiment shifts in substantially the same manner as the transmission shown in FIG. However, the transmission shown in FIG. While the roller 44 rotates in the opposite direction to the input shaft 12, the transmission of the present embodiment has the idler roller 44 inscribed in the guide groove 144 a of the guide 146. The idler roller 4 rotates in the same direction as the input shaft 12.
  • the first and second nose urge the power roller 40 from both sides. ⁇ ⁇ ⁇ ⁇ Wheels 30 and 32 for power output.
  • the forces are balanced on both sides of the word roller 40 and the planetary rollers 44, so that the alignment of the near roller 40 and the planetary rollers 44 can be ensured.
  • the one-way clutch 70 integrally with the input shaft 12, the connection of the drive shaft such as an engine to the input shaft 12 can be made compact. ⁇
  • the permanent magnets 152 of the motor generator 150 are arranged on the inner peripheral side of the extension portion 148 of the dry ring 144, the permanent magnets are prevented from being separated and scattered by centrifugal force. It can be prevented reliably. As a result, the motor generator 150 can be rotated at a high speed, the operating radius of the magnetic force can be increased, and the output of the motor generator 150 can be increased, which is suitable for automobiles. It is possible to form a hybrid drive device.
  • motor generator 150 When such a motor generator 150 is incorporated in an automobile, it can be operated as follows through a suitable motor generator control device.
  • the motor generator 150 which exhibits high efficiency at low speeds, is supplied from the battery. It is driven by the supplied power.
  • the motor generator 150 When the engine speed rises above the speed of the input shaft 12 and the drive shaft and the input shaft 12 are connected via the one-way clutch 70, the motor generator The power supply to 70 can be stopped, and the input shaft 12 can be rotationally driven by the engine.
  • the input shaft 12 is mainly driven by the engine.
  • the power supplied to the motor generator 70 is suppressed, and the battery is charged by operating the motor generator 70 as a generator to charge the battery.
  • the motor generator 70 is operated as a motor, and the driving force of the motor generator 70 is added to the driving force of the engine. Can also respond to the acceleration required by the driver.
  • the motor generator 70 When the vehicle is decelerated, the motor generator 70 operates as a generator, and the power generated at this time is stored in a battery. That is, when the vehicle is decelerated, the accelerator pedal is loosened, and when the rotation speed of the engine is reduced, the one-way clutch 70 separates the drive shaft 60 from the input shaft 12, which causes Then, all the rotating forces acting on the input shafts 12 act on the motor generator 70 as generated energy, and are converted into electric power. The braking energy converted to this electric power is stored in the notifier.
  • the transmission according to the present embodiment not only exhibits quick responsiveness and high transmission efficiency, but also has a great performance when starting and accelerating. It forms an accelerating force and recovers energy with high efficiency during deceleration, which makes it possible to reduce the fuel consumption of automobiles.
  • the pressure difference in the housing 10 to circulate the lubricating oil to the lubricant cooling device 86, there is no need to provide a circulating pump for cooling.
  • the overall structure of the device can be simplified and the weight can be reduced.
  • a continuously variable transmission that has a simple structure, high transmission efficiency, and is capable of transmitting large power while being lightweight is manufactured at low cost. can do. This makes it possible to support an extremely wide range of industrial uses such as automobiles, ships, construction machinery, agriculture, and power generation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Friction Gearing (AREA)

Abstract

La présente invention concerne un dispositif de changement de vitesse progressif qui comprend des cylindres moteurs (40) couplés par frottements entre une paire de roues motrices (30, 32) par des surfaces inclinées (40a, 40b) au niveau d'extrémités opposées et effectuant un mouvement orbital autour d'un axe central (C) de la roue motrice tout en tournant autour de leur propre axe, et des cylindres planétaires (44) couplés par frottements aux surfaces périphériques de ces cylindres moteurs et effectuant un mouvement orbital autour de l'axe central (C) de la roue motrice tout en tournant autour de leur propre axe. Une surface de guidage (46) couplée par frottements aux surfaces périphériques des cylindres planétaires sert de support aux cylindres moteurs (40) contraints dans la direction de l'axe central (C) de la roue motrice par application d'une force de compression produite par la paire de roues motrices, par l'intermédiaire des cylindres planétaires (44), et maintient les cylindres moteurs (40) et les cylindres planétaires (44) à des espaces équidistants du point de vue périphérique.
PCT/JP2003/009265 2002-07-22 2003-07-22 Dispositif de changement de vitesse progressif WO2004010028A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2003281545A AU2003281545A1 (en) 2002-07-22 2003-07-22 Stepless speed change device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2002-212576 2002-07-22
JP2002212576A JP2006052739A (ja) 2002-07-22 2002-07-22 無段変速装置

Publications (1)

Publication Number Publication Date
WO2004010028A1 true WO2004010028A1 (fr) 2004-01-29

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ID=30767812

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2003/009265 WO2004010028A1 (fr) 2002-07-22 2003-07-22 Dispositif de changement de vitesse progressif

Country Status (3)

Country Link
JP (1) JP2006052739A (fr)
AU (1) AU2003281545A1 (fr)
WO (1) WO2004010028A1 (fr)

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2860530A (en) * 1954-10-29 1958-11-18 Curtiss Wright Corp Ball speed changers
US2974547A (en) * 1960-03-03 1961-03-14 Egan Joseph Thomas Speed change mechanism
JPS55100743U (fr) * 1979-01-09 1980-07-14
US4667525A (en) * 1984-12-19 1987-05-26 Henry Schottler Variable speed frictional drive transmissions
JPH04272553A (ja) * 1991-02-26 1992-09-29 Suzuki Motor Corp 摩擦無段変速機
JPH06294462A (ja) * 1993-04-02 1994-10-21 Mazda Motor Corp トロイダル型無段変速機
JPH0783300A (ja) * 1993-09-14 1995-03-28 Mitsubishi Heavy Ind Ltd 遊星式摩擦伝動装置
US5433282A (en) * 1992-05-19 1995-07-18 Kabushikikaisha Equos Research Hybrid vehicle powered by an internal combustion engine and an electric motor
US20010016532A1 (en) * 1999-12-28 2001-08-23 Hu-Yong Jung Transmission for hybrid electric vehicle
JP2002181153A (ja) * 2000-12-15 2002-06-26 Nsk Ltd トロイダル型無段変速機
WO2003019044A1 (fr) * 2001-08-23 2003-03-06 Suenori Tsujimoto Transmission a changement de vitesses continu

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2860530A (en) * 1954-10-29 1958-11-18 Curtiss Wright Corp Ball speed changers
US2974547A (en) * 1960-03-03 1961-03-14 Egan Joseph Thomas Speed change mechanism
JPS55100743U (fr) * 1979-01-09 1980-07-14
US4667525A (en) * 1984-12-19 1987-05-26 Henry Schottler Variable speed frictional drive transmissions
JPH04272553A (ja) * 1991-02-26 1992-09-29 Suzuki Motor Corp 摩擦無段変速機
US5433282A (en) * 1992-05-19 1995-07-18 Kabushikikaisha Equos Research Hybrid vehicle powered by an internal combustion engine and an electric motor
JPH06294462A (ja) * 1993-04-02 1994-10-21 Mazda Motor Corp トロイダル型無段変速機
JPH0783300A (ja) * 1993-09-14 1995-03-28 Mitsubishi Heavy Ind Ltd 遊星式摩擦伝動装置
US20010016532A1 (en) * 1999-12-28 2001-08-23 Hu-Yong Jung Transmission for hybrid electric vehicle
JP2002181153A (ja) * 2000-12-15 2002-06-26 Nsk Ltd トロイダル型無段変速機
WO2003019044A1 (fr) * 2001-08-23 2003-03-06 Suenori Tsujimoto Transmission a changement de vitesses continu

Also Published As

Publication number Publication date
JP2006052739A (ja) 2006-02-23
AU2003281545A1 (en) 2004-02-09

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