WO2015001857A1 - Dispositif de transmission de puissance - Google Patents

Dispositif de transmission de puissance Download PDF

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Publication number
WO2015001857A1
WO2015001857A1 PCT/JP2014/063213 JP2014063213W WO2015001857A1 WO 2015001857 A1 WO2015001857 A1 WO 2015001857A1 JP 2014063213 W JP2014063213 W JP 2014063213W WO 2015001857 A1 WO2015001857 A1 WO 2015001857A1
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WO
WIPO (PCT)
Prior art keywords
target
force
turning radius
output shaft
radius
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PCT/JP2014/063213
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English (en)
Japanese (ja)
Inventor
庸浩 小林
Original Assignee
本田技研工業株式会社
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 本田技研工業株式会社 filed Critical 本田技研工業株式会社
Priority to JP2015525088A priority Critical patent/JP5973075B2/ja
Priority to CN201480024109.7A priority patent/CN105247253B/zh
Publication of WO2015001857A1 publication Critical patent/WO2015001857A1/fr

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    • 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
    • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
    • F16H29/02—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts
    • F16H29/04—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts in which the transmission ratio is changed by adjustment of a crank, an eccentric, a wobble-plate, or a cam, on one of the shafts
    • 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
    • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
    • F16H29/22—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action with automatic speed change

Definitions

  • the present invention relates to a power transmission device including a continuously variable transmission of a four-bar linkage mechanism type that can be changed by adjusting a rotation radius with a rotation radius adjustment mechanism provided on a rotation center axis of an input unit.
  • an input unit to which a driving force from a main drive source such as an engine provided in a vehicle is transmitted, an output shaft arranged in parallel with the rotation center axis of the input unit, and a plurality of units provided on the rotation center axis
  • a rotating radius adjusting mechanism a plurality of swing links pivotally supported by the output shaft, an input side annular portion rotatably fitted on the rotating radius adjusting mechanism at one end, and the other end
  • a four-bar link mechanism type continuously variable transmission including a connecting rod connected to a swing end of a swing link (see, for example, Patent Document 1).
  • each rotation radius adjustment mechanism consists of the cam part eccentrically provided on the rotation center axis line, the rotation part eccentrically provided in this cam part, and the pinion shaft.
  • a one-way clutch is provided as a one-way rotation prevention mechanism between the swing link and the output shaft. The one-way clutch fixes the swing link to the output shaft when the swing link is about to rotate relative to the output shaft, and Spin the swing link idle.
  • Each cam portion is provided so as to be positioned in a direction opposite to the eccentric direction with respect to the rotation center axis line through the through hole penetrating in the axial direction of the rotation center axis line, and a notch for communicating the outer peripheral surface of the cam portion with the through hole. And a hole. Further, the cam portion is provided with a pair of expansion portions so as to sandwich the notch hole in the axial direction. Adjacent cam portions are fixed with bolts, thereby forming a cam portion coupling body. One end in the axial direction of the cam portion connecting body is connected to the input portion, and the cam portion connecting body and the input portion constitute a camshaft.
  • the cam part connecting body is hollow by connecting through holes of each cam part, and a pinion shaft is inserted into the inside.
  • the inserted pinion shaft is exposed from the notch hole of each cam portion.
  • the rotating part is provided with a receiving hole for receiving the camshaft. Internal teeth are formed on the inner peripheral surface of the rotating part that forms the receiving hole.
  • the inner teeth mesh with the pinion shaft exposed from the notch hole in the camshaft.
  • the camshaft and the pinion shaft are rotated at the same speed, the turning radius of the turning radius adjusting mechanism is maintained.
  • the rotational speeds of the camshaft and the pinion shaft are made different, the rotational radius of the rotational radius adjusting mechanism is changed, and the transmission ratio of the continuously variable transmission is changed.
  • a lever crank mechanism is configured by the turning radius adjusting mechanism, the connecting rod, and the swing link. Since the swing link is provided on the output shaft via the one-way clutch, the rotational drive force (torque) is transmitted to the output shaft only when rotating to one side.
  • the eccentric direction of the cam disk of each turning radius adjusting mechanism is set so as to make a round around the input shaft with different phases. Therefore, the connecting rod that is externally fitted to each turning radius adjusting mechanism causes the swing link to transmit torque to the output shaft in order, so that the output shaft can be smoothly rotated.
  • Patent Document 1 when a high vehicle speed and a high driving force are required, the rotation radius of the turning radius adjusting mechanism and the driving force of the main drive source are driven to the output shaft so as to complete the speed change quickly.
  • the target is set based on the target vehicle speed and the target output driving force in the idling region in which the swing link is idled with respect to the output shaft without transmitting force (hereinafter referred to as idling region). It is controlled to approach the point.
  • An object of the present invention is to provide a power transmission device including a continuously variable transmission of a four-bar linkage mechanism type that can reach a target point more quickly than before when shifting.
  • the present invention provides an input unit that is rotated by transmission of a rotational driving force of a main drive source, an output shaft that is disposed in parallel to the rotation center axis of the input unit, and a shaft support that is supported by the output shaft.
  • a lever crank mechanism for converting the rotational movement of the input portion into the rocking movement of the rocking link, and the rocking link to rotate relative to the output shaft.
  • a one-way rotation prevention mechanism that can be switched to any one of an idling state in which the link is idling, and the lever crank mechanism is a power transmission device that includes a turning radius adjusting mechanism capable of adjusting a turning radius.
  • a turning radius adjusting mechanism and the main drive source A control unit for controlling, and the control unit determines a fixed region in which the one-way rotation prevention mechanism is in a fixed state and an idle region in which the one-way rotation prevention mechanism is in an idle state from a rotation radius and a driving force;
  • a target radius setting unit that sets a target turning radius based on vehicle information, a target driving force setting unit that sets a target driving force based on predetermined vehicle information, and a diameter reduction that a force applied to the turning radius adjustment mechanism reduces the turning radius.
  • a diameter reducing force determining unit that determines whether or not the force is a direction force, a point set based on the current turning radius and driving force is defined as a current point, and the target turning radius and the target driving force are A point set based on the target rotation point is defined as a target point, and when the target rotation radius is smaller than the current rotation radius and when shifting from the current point to the target point, Idling to shift near the target point with A shift method determining unit that executes an internal shift, and when the control unit determines that a force in the diameter reduction direction that reduces the rotation radius is applied to the rotation radius adjustment mechanism by the diameter reduction force determination unit. The driving force of the main driving source is increased.
  • the control unit increases the driving force of the main drive source when it is determined by the diameter reducing force determining unit that the force in the diameter reducing direction for reducing the turning radius is applied to the rotating radius adjusting mechanism. .
  • the force in the reduced diameter direction can be effectively utilized as the force required for the shift, and the shift can be completed more rapidly than in the past.
  • Explanatory drawing which shows embodiment of the power transmission device of this invention in a partial cross section.
  • Explanatory drawing which shows the lever crank mechanism of this embodiment.
  • Explanatory drawing which shows the change of the rotation radius of this embodiment.
  • A shows the state where the turning radius is the maximum
  • B shows the inside of the turning radius
  • C shows the turning radius is small
  • D shows the state where the turning radius is 0.
  • Explanatory drawing which shows the change of the rocking
  • A shows the swing range where the turning radius is maximum, B is the turning radius is medium, and C is the turning radius is small.
  • the block diagram which showed typically the power transmission device of this embodiment.
  • region shifting of this embodiment The graph which shows the transition of the boundary line of the fixed area
  • a continuously variable transmission 1 of a four-bar linkage mechanism type receives a rotational drive force from a main drive source 50 (see FIG. 5) such as an engine or an electric motor that is an internal combustion engine, thereby rotating the rotation center axis.
  • a main drive source 50 such as an engine or an electric motor that is an internal combustion engine
  • An input unit 2 that rotates about P1; an output shaft 3 that is arranged in parallel to the rotation center axis P1 and that transmits rotational power to drive wheels 65 (see FIG. 5) of the vehicle via a differential gear (not shown);
  • Six turning radius adjusting mechanisms 4 provided on the rotation center axis P1.
  • a propeller shaft may be provided instead of the differential gear.
  • each turning radius adjusting mechanism 4 includes a cam disk 5 as a cam part and a rotating disk 6 as a rotating part.
  • the cam disks 5 have a disk shape, are eccentric from the rotation center axis P ⁇ b> 1, and are provided in each rotation radius adjustment mechanism 4 so as to form one set with respect to one rotation radius adjustment mechanism 4.
  • the cam disk 5 is provided with a through hole 5a penetrating in the direction of the rotation center axis P1. Further, the cam disk 5 is opened in a direction opposite to the direction decentered with respect to the rotation center axis P1, and a notch hole 5b for communicating the outer peripheral surface of the cam disk 5 with the inner peripheral surface constituting the through hole 5a. Is provided.
  • Each set of cam disks 5 is arranged so as to make a round in the circumferential direction of the rotation center axis P1 with six sets of cam disks 5 with a phase difference of 60 degrees.
  • the cam disk 5 is formed integrally with the cam disk 5 of the adjacent turning radius adjusting mechanism 4 to constitute an integrated cam portion 5c.
  • the integrated cam portion 5c may be formed by integral molding, or may be integrated by welding two cam portions.
  • a pair of cam disks 5 of each turning radius adjusting mechanism 4 are fixed by bolts (not shown).
  • the cam disk 5 located closest to the main drive source 50 on the rotation center axis P ⁇ b> 1 is formed integrally with the input unit 2. In this way, the camshaft 51 is configured by the input unit 2 and the cam disk 5.
  • the camshaft 51 includes an insertion hole 60 formed by connecting the through holes 5 a of the cam disk 5.
  • the camshaft 51 is configured in a hollow shaft shape in which one end opposite to the main drive source 50 is opened and the other end is closed.
  • the cam disk 5 located at the other end on the main drive source 50 side is formed integrally with the input unit 2.
  • integral molding may be used, or the cam disk 5 and the input part 2 may be integrated by welding.
  • each set of cam disks 5 has a disc-shaped rotating disk 6 provided with a receiving hole 6a for receiving the cam disk 5, and is rotatably fitted in an eccentric state.
  • the rotating disk 6 has a cam disk 5 center point P2 and a rotating disk 6 center point P3, a distance Ra between the rotation center axis P1 and the center point P2, and the center point P2 and the center point. It is eccentric with respect to the cam disk 5 so that the distance Rb of P3 is the same.
  • an internal tooth 6 b is provided between the pair of cam disks 5.
  • the pinion 70 is positioned concentrically with the rotation center axis P ⁇ b> 1 and corresponding to the inner teeth 6 b of the rotary disk 6 so that the pinion 70 can rotate relative to the camshaft 51.
  • the pinion 70 is formed integrally with the pinion shaft 72.
  • the pinion 70 may be configured separately from the pinion shaft 72, and the pinion 70 may be connected to the pinion shaft 72 by spline coupling.
  • the term “pinion 70” is defined as including the pinion shaft 72.
  • the pinion 70 meshes with the internal teeth 6b of the rotating disk 6 through the notch hole 5b of the cam disk 5.
  • the pinion shaft 72 is provided with a bearing 74 positioned between the adjacent pinions 70.
  • the pinion shaft 72 supports the camshaft 51 via the bearing 74.
  • the differential mechanism 8 is connected to the pinion shaft 72.
  • the driving force of the adjusting drive source 14 is transmitted to the pinion 70 via the differential mechanism 8.
  • the center point P3 of the rotating disk 6 is positioned on the same axis as the rotation center axis P1.
  • the distance between the rotation center axis P1 and the center point P3, that is, the eccentricity R1 can be set to “0”.
  • a connecting rod 15 having a large-diameter large-diameter annular portion 15a at one end and a small-diameter annular portion 15b having a smaller diameter than the large-diameter annular portion 15a at the other end is provided at the periphery of the rotating disk 6.
  • a large-diameter annular portion 15a is rotatably fitted via a connecting rod bearing 16 made of a roller bearing.
  • the connecting rod bearing 16 may comprise two ball bearings arranged in the axial direction as a set.
  • Six swing links 18 corresponding to the connecting rod 15 are provided on the output shaft 3 via a one-way clutch 17.
  • the one-way clutch 17 is provided between the swing link 18 and the output shaft 3.
  • the swing link 18 When the swing link 18 is about to rotate relative to the output shaft 3 on one side, the swing link 18 is connected to the output shaft. 3 (fixed state), and the rocking link 18 is idled with respect to the output shaft 3 (idle state) when trying to rotate relatively to the other side.
  • the swing link 18 is formed in an annular shape, and a swing end portion 18a connected to the small-diameter annular portion 15b of the connecting rod 15 is provided above the swing link 18.
  • the swing end portion 18a is provided with a pair of projecting pieces 18b projecting so as to sandwich the small-diameter annular portion 15b in the axial direction.
  • the pair of projecting pieces 18b are provided with insertion holes 18c corresponding to the inner diameter of the small-diameter annular portion 15b.
  • a connecting pin 19 as a swing shaft is inserted into the insertion hole 18c and the small-diameter annular portion 15b. Thereby, the connecting rod 15 and the swing link 18 are connected.
  • the hole defined by the inner peripheral surface of the small diameter annular portion 15b corresponds to the insertion hole of the present invention.
  • the oscillating end 18a is disposed below the output shaft 3 so that the oscillating end 18a of the oscillating link 18 is immersed in the oil reservoir of lubricating oil collected below the case 80.
  • the oscillating end 18a can be lubricated with the oil reservoir, and the lubricating oil in the oil reservoir can be lifted by the oscillating motion of the oscillating link 18 to lubricate other components of the continuously variable transmission 1. it can.
  • the gear ratio is defined as the rotational speed of the input unit / the rotational speed of the output shaft.
  • FIG. 3 shows the positional relationship between the pinion shaft 72 and the rotating disk 6 in a state where the eccentricity R1 of the turning radius adjusting mechanism 4 is changed.
  • FIG. 3A shows a state where the eccentric amount R1 is “maximum”, and the pinion shaft is such that the rotation center axis P1, the center point P2 of the cam disk 5, and the center point P3 of the rotation disk 6 are aligned. 72 and the rotary disk 6 are located. At this time, the gear ratio h is minimized.
  • FIG. 3B shows a state where the eccentric amount R1 is “medium” smaller than FIG. 3A
  • FIG. 3C shows a state where the eccentric amount R1 is “small” smaller than FIG. 3B
  • the gear ratio h is “medium” which is larger than the gear ratio h in FIG. 3A in FIG. 3B and “large” which is larger than the gear ratio h in FIG. 3B in FIG.
  • FIG. 3D shows a state where the amount of eccentricity R1 is “0”, and the rotation center axis P1 and the center point P3 of the rotating disk 6 are located concentrically.
  • the gear ratio h at this time is infinite ( ⁇ ).
  • the rotational radius of the rotational radius adjusting mechanism 4 is adjustable by changing the eccentric amount R1 by the rotational radius adjusting mechanism 4.
  • FIG. 4 shows a change in the swing range of the swing link 18 when the eccentric amount R1 of the turning radius adjusting mechanism 4 is changed.
  • 4A shows the swing range of the swing link 18 when the eccentric amount R1 is the maximum
  • FIG. 4B shows the swing range of the swing link 18 when the eccentric amount R1 is medium
  • FIG. The swing range of the swing link 18 when the eccentric amount R1 is small is shown. It can be seen from FIG. 4 that the swing range becomes narrower as the eccentric amount R1 becomes smaller. When the eccentric amount R1 becomes “0”, the swing link 18 does not swing.
  • the turning radius adjusting mechanism 4, the connecting rod 15, and the swing link 18 constitute a lever crank mechanism 20 (four-bar linkage mechanism). Then, the lever crank mechanism 20 converts the rotational motion of the input unit 2 into the swing motion of the swing link 18.
  • the continuously variable transmission 1 of this embodiment includes a total of six lever crank mechanisms 20.
  • the swing link 18 Since the small-diameter annular portion 15b of the connecting rod 15 is connected to the swing link 18 provided on the output shaft 3 via the one-way clutch 17, the swing link 18 is pushed and pulled by the connecting rod 15 to swing.
  • the output shaft 3 rotates only when the swing link 18 rotates in either the pushing direction side or the pulling direction side, and the output shaft 3 rotates when the swing link 18 rotates in the other direction.
  • the force of the swinging motion of the swing link 18 is not transmitted, and the swing link 18 rotates idle. Since each turning radius adjusting mechanism 4 is arranged with a phase changed every 60 degrees, the output shaft 3 is rotated in turn by each turning radius adjusting mechanism 4.
  • the power transmission device of the present embodiment includes a control unit 40 that controls the adjustment drive source 14.
  • the control unit 40 is an electronic unit composed of a CPU, a memory, and the like, and controls the adjustment drive source 14 by executing a control program held in the memory by the CPU, thereby eccentricity of the turning radius adjustment mechanism 4. Serves to regulate the amount R1.
  • control unit 40 of the present embodiment includes an area determination unit 100, a target radius setting unit 110, a target driving force setting unit 120, a reduced diameter force determination unit 130, a speed change method determination unit 140, and a rotation radius difference.
  • a determination unit 150 and a current driving force determination unit 160 are provided.
  • the target radius setting unit 110 sets a target turning radius based on predetermined vehicle information received by the control unit 40.
  • the target driving force setting unit 120 sets the target driving force based on predetermined vehicle information such as the accelerator pedal depression amount.
  • control unit 40 receives information on the rotational speed of the main drive source 50 from the input side rotational speed detection unit 41. Further, the control unit 40 receives information on the rotation speed of the output shaft 3 or the drive wheel 65 from the output side rotation speed detection unit 42. Further, the control unit 40 receives the opening degree information from the throttle valve opening degree detecting unit 43 that detects the opening degree of the throttle valve that opens and closes depending on the depression amount of the accelerator pedal. The control unit 40 also receives vehicle speed information from a vehicle speed detection unit (not shown) that detects the traveling speed of the vehicle. Further, the control unit 40 receives information on the rotation radius (the amount of eccentricity) from the rotation radius detection unit (not shown).
  • the control unit 40 executes the process shown in the flowchart of FIG. 8 when the accelerator pedal is depressed to increase the gear ratio and increase the driving force (so-called kick down).
  • points set based on the current rotational radius and the driving force are defined as current points Ps1, Ps2, and the target A point set based on the amount of eccentricity (target rotation radius) and the target driving force is defined as a target point Pt.
  • control unit 40 first receives accelerator pedal opening information, vehicle speed information, and rotation radius information (eccentric amount information) in STEP 1 and determines a target eccentric amount (target rotational radius).
  • the control unit 40 includes a fixed region where the one-way clutch 17 is fixed, and an idle region where the one-way clutch 17 is idle. And the boundary line L between the fixed region and the idle region is determined.
  • FIG. 7 is a graph showing a boundary line between the fixed region and the idling region, where the horizontal axis represents the amount of eccentricity and the vertical axis represents the rotational speed of the main drive source 50. It can be seen that as the traveling speed of the vehicle increases, the boundary line moves in the upper right direction in FIG.
  • the control unit 40 includes a storage unit (not shown) in which a fixed region and an idling region are stored in advance in association with the vehicle speed, the amount of eccentricity, and the rotational speed through experiments, simulations, and the like. And the control part 40 determines a fixed area
  • the process proceeds to STEP 5 and it is determined whether or not the difference between the current eccentric amount and the target eccentric amount is a predetermined value or more. To do. If it is equal to or greater than the predetermined value, the process proceeds to STEP 6 to determine whether or not the current driving force is equal to or smaller than the predetermined value.
  • the process proceeds to STEP7, the eccentric amount is lowered from the current point Ps1 to the predetermined eccentric amount and shifted to the idling region, and then the rotational speed is increased to the target point Pt.
  • the process of shifting in the idling region to be reached is executed. As a result, the amount of eccentricity can be reduced smoothly to the vicinity of the target point Pt within the idling region that is not affected by the inertial force or running resistance of the drive wheels or vehicle.
  • the process branches to STEP 8, and the target point Pt is set within the fixed region while increasing the rotational speed while decreasing the eccentric amount from the current point Ps1.
  • the process of shifting within the fixed area is performed to perform shifting up to.
  • the predetermined value of STEP5 is a value that is assumed to be faster when shifting in the fixed region as it is than in the idling region, and is a value that is obtained in advance through experiments or the like.
  • the process branches to STEP 8 to execute the fixed region shift process.
  • the predetermined value of STEP 6 is set to a value that may cause the driver to feel uncomfortable due to the loss of driving force caused by shifting to the idling region, and this predetermined value is also obtained in advance by experiments or the like.
  • the process branches to STEP 9 and the control unit 40 determines whether or not a force in a direction to reduce the eccentricity is applied to the turning radius adjusting mechanism 4. If a force in the direction of decreasing the amount of eccentricity is applied to the turning radius adjusting mechanism 4, the process proceeds to STEP 10 where the rotational speed of the main drive source 50 is increased and moved from the current point Ps2 in the idling region to the fixed region. .
  • the process proceeds to STEP8, in which the gear shift to the target point Pt is performed in the fixed region while increasing the rotational speed of the main drive source 50 while decreasing the eccentricity R1.
  • the shift process is executed.
  • the process branches to STEP 7, and the eccentric amount R1 is equal to or equal to the target eccentric amount from the current point Ps2.
  • the idling region shifting process for increasing the rotational speed to reach the target point Pt is executed.
  • FIG. 8 in FIG. 8 of the present embodiment is the processing of the region determination unit 100
  • STEP1 is the processing of the target radius setting unit 110 and the target driving force setting unit 120
  • STEP4 and STEP9 are the diameter reduction force determination unit 130. Further, the flow chart of FIG.
  • FIG. 6 shows the rotational speed (the number of revolutions, the unit is, for example, [rpm]) of the main drive source 50 and the eccentric amount R1 of the rotational radius adjusting mechanism 4 (the rotational radius is, for example, [mm]) in the power transmission device of the present embodiment.
  • An orthogonal coordinate system with and as coordinate axes is shown.
  • the solid curve indicates the boundary line L between the idle region and the fixed region.
  • the lower left direction is the idling region with the boundary line L as the boundary
  • the upper right direction of the drawing is the fixed region.
  • the boundary line L transitions to La, Lb, and Lc so that the idling region expands as the traveling speed of the vehicle increases.
  • a point obtained from the current rotational speed of the main drive source 50 and the current eccentric amount R1 is defined as the current point, and a point obtained from the target rotational speed and the target eccentric amount R1 is defined.
  • Ps1 indicates a point when the current point is within the fixed region, and this point of Ps1 is defined for the sake of explanation as the current point within fixed.
  • Ps2 indicates a point when the current point is in the idling region, and this point of Ps2 is defined as the current point in idling for explanation.
  • Pt is a target point.
  • C1 is a control path for shifting from the current point Ps1 within the fixed range to the target point Pt within the fixed region without passing through the idle region. Further, C1 ′ passes through the idle region from the fixed current point Ps1, controls the eccentric amount R1 to near the target eccentric amount, and the eccentric amount R1 and the main drive source 50 so as to reach the target point therefrom. It is a control path in the case of controlling the rotation speed.
  • C2 increases the rotational speed of the main drive source 50 while shifting the rotation speed from the current point Ps2 in the idling state to the fixed region, and then reaches the target point in the fixed region.
  • This is a control path when the eccentric amount R1 and the rotation speed of the main drive source 50 are controlled so as to reach each other.
  • C2 ′ controls the eccentric amount R1 from the current idling point Ps2 to near the target eccentricity within the idling region, and the eccentric amount R1 and the rotational speed of the main drive source 50 are adjusted so as to reach the target point from there. This is a control path for control.
  • Step 21 the current eccentric amount R1 is detected. Then, the process proceeds to STEP 22, where it is determined whether or not the force applied to the turning radius adjusting mechanism 4 is a force in the direction of decreasing the eccentricity based on the information stored in the storage unit and the received information.
  • the process proceeds to STEP 23, in which it is determined whether or not the force applied to the turning radius adjusting mechanism 4 is a force in a direction that reduces the amount of eccentricity.
  • the process proceeds to STEP 24 and processing for decreasing the eccentric amount R1 is executed.
  • the process proceeds to STEP 25, where a process for increasing the driving force (torque) of the main drive source 50 is executed.
  • STEP 27 if the current point is not the idling region, the process branches to STEP 28, and a process of reducing the driving force (torque) of the main drive source 50 is executed so as to shift to the idling region. Then, returning to STEP 23, it is determined whether or not the force applied to the turning radius adjusting mechanism 4 is a force in a direction that reduces the eccentricity.
  • the controller 40 determines that the force in the diameter reducing direction that reduces the rotation radius is applied to the rotation radius adjusting mechanism 4 by the diameter reducing force determination unit 130 (The driving force of the main drive source 50 is increased (STEP 25). For this reason, the force in the reduced diameter direction can be effectively utilized as the force required for the shift, and the shift can be completed more rapidly than in the past.
  • the input portion 2 and the cam disk 5 constitute a camshaft 51, and the camshaft 51 includes an insertion hole 60 formed by connecting the through holes 5a of the cam disk 5.
  • the camshaft of the present invention is not limited to this.
  • the input portion is configured as a hollow shaft having an insertion hole whose one end is open and the other end is closed, and the input portion is inserted into a disc-shaped cam disk.
  • the through hole may be formed to be larger than that of the first embodiment so that the cam disk can be splined to the outer peripheral surface of the input portion configured in a hollow shaft shape.
  • a notch hole corresponding to the notch hole of the cam disk is provided in the input portion composed of the hollow shaft. Then, the pinion inserted into the input part meshes with the internal teeth of the rotating disk through the notch hole of the input part and the notch hole of the cam disk.
  • the one-way clutch 17 is used as the one-way rotation prevention mechanism.
  • the one-way rotation prevention mechanism of the present invention is not limited to this, and torque is applied from the swing link 18 to the output shaft 3. You may comprise with the two-way clutch comprised so that the rotation direction with respect to the output shaft 3 of the rocking

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Abstract

Le problème décrit par la présente invention est de produire un dispositif de transmission de puissance pouvant, lors d'un changement de vitesse, atteindre un point cible plus rapidement que cela n'est habituellement possible. La solution selon l'invention porte sur un dispositif de transmission de puissance comprenant une source d'entraînement principale, une transmission à variation continue et une unité de commande. La transmission à variation continue comprend : un mécanisme levier-bielle qui convertit un mouvement rotatif d'une unité d'entrée en un mouvement pivotant d'une liaison pivotante ; et un arbre de sortie. Un embrayage unidirectionnel se situe sur l'arbre de sortie. L'arbre de sortie tourne dans une seule direction, à la suite du mouvement pivotant de la liaison pivotante. L'unité de commande augmente (ETAPE 25) la force d'entraînement de la source d'entraînement principale si on a déterminé (OUI à l'ETAPE 23) qu'une force a été appliquée à un mécanisme d'ajustement de rayon de rotation, ladite force se faisant dans la direction de rayon réduit dans laquelle le rayon de rotation est réduit par l'unité de détermination de force de rayon réduit.
PCT/JP2014/063213 2013-07-01 2014-05-19 Dispositif de transmission de puissance WO2015001857A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2015525088A JP5973075B2 (ja) 2013-07-01 2014-05-19 動力伝達装置
CN201480024109.7A CN105247253B (zh) 2013-07-01 2014-05-19 动力传递装置

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Application Number Priority Date Filing Date Title
JP2013138469 2013-07-01
JP2013-138469 2013-07-01

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WO2015001857A1 true WO2015001857A1 (fr) 2015-01-08

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PCT/JP2014/063213 WO2015001857A1 (fr) 2013-07-01 2014-05-19 Dispositif de transmission de puissance

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JP (1) JP5973075B2 (fr)
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Citations (3)

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Publication number Priority date Publication date Assignee Title
JPS5287887U (fr) * 1975-12-25 1977-06-30
WO2003067126A1 (fr) * 2002-02-07 2003-08-14 Katsuya Kawakita Transmission continue et equipement dote d'une transmission continue
JP2013024382A (ja) * 2011-07-25 2013-02-04 Honda Motor Co Ltd 無段変速機構及び自動車用駆動システム

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Publication number Priority date Publication date Assignee Title
JP4414972B2 (ja) * 2006-02-08 2010-02-17 ジヤトコ株式会社 車両の制御装置
JP2007292245A (ja) * 2006-04-26 2007-11-08 Mazda Motor Corp ベルト式ｃｖｔの挟圧力制御装置
JP2007315520A (ja) * 2006-05-26 2007-12-06 Toyota Motor Corp 無段変速機の変速制御装置
JP4747059B2 (ja) * 2006-09-20 2011-08-10 ジヤトコ株式会社 車両の制御装置
JP5638075B2 (ja) * 2010-07-09 2014-12-10 本田技研工業株式会社 自動車用駆動システム及びその制御方法
JP5234443B2 (ja) * 2011-08-29 2013-07-10 本田技研工業株式会社 駆動制御装置及び駆動制御方法

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5287887U (fr) * 1975-12-25 1977-06-30
WO2003067126A1 (fr) * 2002-02-07 2003-08-14 Katsuya Kawakita Transmission continue et equipement dote d'une transmission continue
JP2013024382A (ja) * 2011-07-25 2013-02-04 Honda Motor Co Ltd 無段変速機構及び自動車用駆動システム

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CN105247253A (zh) 2016-01-13
JP5973075B2 (ja) 2016-08-23
JPWO2015001857A1 (ja) 2017-02-23

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