JP5690695B2 - Shift control device - Google Patents

Description

  The present invention relates to a transmission control apparatus that appropriately controls a transmission ratio in a continuously variable transmission in which a characteristic of a transmission ratio with respect to an eccentric amount is geometrically nonlinear.

  A continuously variable transmission called IVT (Infinity Variable Transmission) is known which converts the rotational motion of the engine output shaft into rocking motion, and further converts the rocking motion into rotational motion and outputs it from the output shaft of the transmission. It has been. In this type of transmission, the gear ratio can be changed steplessly without using a clutch, and the maximum value of the gear ratio can be set to infinity. In the transmission, the output rotational speed is zero when the speed ratio is set to infinity.

  FIG. 6 is a side sectional view of a part of a continuously variable transmission called IVT as viewed from the axial direction. The continuously variable transmission shown in FIG. 6 includes an input shaft 101 that rotates around an input center axis O1 by receiving rotational power from a power source such as an internal combustion engine, an eccentric disk 104 that rotates integrally with the input shaft 101, A connecting member 130 connecting the input side and the output side, and a one-way clutch 120 provided on the output side are provided.

  The eccentric disk 104 is formed in a circular shape centered on the first fulcrum O3. The first fulcrum O3 is set to rotate with the input shaft 101 around the input center axis O1, while maintaining an eccentricity r1 that can be changed with respect to the input center axis O1. Accordingly, the eccentric disk 104 is provided to rotate eccentrically as the input shaft 101 rotates around the input center axis O1 while maintaining the eccentric amount r1.

  As shown in FIG. 6, the eccentric disk 104 includes an outer peripheral disk 105 and an inner peripheral disk 108 that is integrally formed with the input shaft 101. The inner circumferential disc 108 is formed as a thick disc whose center is deviated from the input center axis O1 which is the center axis of the input shaft 101 by a certain eccentric distance. The outer peripheral side disk 105 is formed as a thick disk centered on the first fulcrum O3, and has a first circular hole 106 centered at a position off the center (first fulcrum O3). Yes. And the outer periphery of the inner peripheral disk 108 is fitted to the inner periphery of the first circular hole 106 so as to be rotatable.

  Further, the inner circumferential disc 108 is provided with a second circular hole 109 centered on the input center axis O1 and having a part in the circumferential direction opened to the outer circumference of the inner circumferential disc 108. A pinion 110 is rotatably accommodated inside the two circular holes 109. The teeth of the pinion 110 are meshed with an internal gear 107 formed on the inner periphery of the first circular hole 106 of the outer peripheral disk 105 through the opening on the outer periphery of the second circular hole 109.

  The pinion 110 is provided so as to rotate coaxially with the input center axis O1, which is the center axis of the input shaft 101. That is, the rotation center of the pinion 110 and the input center axis O1 that is the center axis of the input shaft 101 coincide with each other. The pinion 110 is rotated inside the second circular hole 109 by an actuator (not shown). Normally, the pinion 110 is rotated in synchronization with the rotation of the input shaft 101, and the pinion 110 is given a rotational speed that is higher or lower than the rotational speed of the input shaft 101 with reference to the synchronous rotational speed. 110 is rotated relative to the input shaft 101. For example, when the pinion 110 and the output shaft of the actuator are arranged so as to be connected to each other, and the rotation of the actuator causes a rotation difference with respect to the rotation of the input shaft 101, the rotation difference is multiplied by the reduction ratio. This can be realized by using a speed reduction mechanism (for example, a planetary gear) in which the relative angle between the input shaft 101 and the pinion 110 changes. At this time, when there is no rotational difference between the actuator and the input shaft 101 and they are synchronized, the eccentricity r1 does not change.

  Therefore, when the pinion 110 is turned, the internal gear 107 with which the teeth of the pinion 110 are engaged, that is, the outer peripheral disk 105 rotates relative to the inner peripheral disk 108, and thereby the center ( The distance between the input center axis O1) and the center of the outer peripheral disk 105 (first fulcrum O3) (that is, the eccentric amount r1 of the eccentric disk 104) changes.

  In this case, the rotation of the pinion 110 is set so that the center of the outer peripheral disc 105 (first fulcrum O3) can be matched with the center of the pinion 110 (input center axis O1), and both the centers match. By doing so, the eccentricity r1 of the eccentric disk 104 can be set to “zero”.

  The one-way clutch 120 also swings around the output center axis O2 by receiving power in the rotational direction from the output member (clutch inner) 121 rotating around the output center axis O2 away from the input center axis O1. A ring-shaped input member (clutch outer) 122 that moves, and a plurality of rollers (between the input member 122 and the output member 121 for locking the input member 122 and the output member 121 with each other) Engaging member) 123. The one-way clutch 120 is provided with the same number of rollers 123 as the number of sides in the cross section of the output member 121.

  In the transmission of power (torque) from the input member 122 to the output member 121 of the one-way clutch 120, the rotational speed of the input member 122 in the positive direction (the direction of the arrow RD1 in FIG. 6) exceeds the rotational speed of the output member 121 in the positive direction. Only under certain conditions. In other words, in the one-way clutch 120, meshing (locking) occurs through the roller 123 only when the rotational speed of the input member 122 becomes higher than the rotational speed of the output member 121, and the swinging power of the input member 122 is output. It is converted into the rotational motion of the member 121.

  An overhang portion 124 is provided at one place in the circumferential direction of the input member 122, and the overhang portion 124 is provided with a second fulcrum O 4 that is separated from the output center axis O 2. And the pin 125 is arrange | positioned on the 2nd fulcrum O4 of the input member 122, and the front-end | tip (other end part) 132 of the connection member 130 is rotatably connected with the input member 122 by this pin 125. FIG.

  The connecting member 130 has a ring part 131 on one end side, and the inner periphery of the circular opening 133 of the ring part 131 is rotatably fitted to the outer periphery of the eccentric disk 104 via a bearing 140. Therefore, one end of the connecting member 130 is rotatably connected to the outer periphery of the eccentric disk 104 in this way, and the other end of the connecting member 130 is connected to the second fulcrum O4 provided on the input member 122 of the one-way clutch 120. By being pivotably connected, as shown in FIG. 7, a four-bar linkage mechanism having four nodes of an input center axis O1, a first fulcrum O3, an output center axis O2, and a second fulcrum O4 as pivot points. Is configured.

  FIG. 7 is an explanatory diagram of the driving force transmission principle of a continuously variable transmission configured as a four-bar linkage mechanism. In this four-bar linkage mechanism, the rotational motion given to the eccentric disk 104 from the input shaft 101 is transmitted as the swing motion of the input member 122 to the input member 122 of the one-way clutch 120 via the connecting member 130. The swinging motion of the input member 122 is converted into the rotational motion of the output member 121. When the input shaft 101 that rotates the eccentric disk 104 rotates once, the input member 122 of the one-way clutch 120 swings one reciprocating motion. As shown in FIG. 7, regardless of the value of the eccentricity r1 of the eccentric disk 104, the oscillation cycle of the input member 122 of the one-way clutch 120 is always constant. The angular velocity ω2 of the input member 122 is determined by the rotational angular velocity ω1 of the eccentric disk 104 (input shaft 101) and the eccentric amount r1.

  In that case, the outer peripheral side disk provided with the pinion 110, the inner periphery side disk 108 provided with the 2nd circular hole 109 which accommodates the pinion 110, and the 1st circular hole 106 which accommodates the inner periphery side disk 108 rotatably. 105. The eccentric amount r1 of the eccentric disk 104 can be changed by moving the pinion 110 of the speed ratio variable mechanism 112 constituted by an actuator or the like with the actuator. Then, by changing the eccentricity r1, the swing angle θ2 of the input member 122 of the one-way clutch 120 can be changed, whereby the ratio of the rotational speed of the output member 121 to the rotational speed of the input shaft 101 (speed change). The ratio: ratio i) can be varied. That is, by adjusting the eccentric amount r1 of the first fulcrum O3 with respect to the input center axis O1, the swing angle θ2 of the swing motion transmitted from the eccentric disk 104 to the input member 122 of the one-way clutch 120 is changed. It is possible to change the gear ratio when the rotational power input to the input shaft 101 is transmitted as rotational power to the output member 121 of the one-way clutch 120 via the eccentric disk 104 and the connecting member 130.

  FIGS. 8A to 8D and FIGS. 9A to 9C are explanatory diagrams of the speed change principle by the speed ratio variable mechanism 112 in the continuously variable transmission shown in FIG. As shown in FIGS. 8 and 9, the input central axis of the eccentric disk 104 is rotated by rotating the pinion 110 of the speed ratio variable mechanism 112 and rotating the outer peripheral disk 105 with respect to the inner peripheral disk 108. The amount of eccentricity r1 with respect to O1 (rotation center of the pinion 110) can be adjusted.

  For example, as shown in FIGS. 8A and 9A, when the eccentric amount r1 of the eccentric disk 104 is set to “large”, the swing angle θ2 of the input member 122 of the one-way clutch 120 is increased. Therefore, a small gear ratio i can be realized. Further, as shown in FIGS. 8B and 9B, when the eccentric amount r1 of the eccentric disk 104 is set to “medium”, the swing angle θ2 of the input member 122 of the one-way clutch 120 is set to “medium”. Therefore, a medium gear ratio i can be realized. Further, as shown in FIGS. 8C and 9C, when the eccentric amount r1 of the eccentric disk 104 is set to “small”, the swing angle θ2 of the input member 122 of the one-way clutch 120 is reduced. Therefore, a large gear ratio i can be realized. Further, as shown in FIG. 8D, when the eccentric amount r1 of the eccentric disk 104 is set to “zero”, the swing angle θ2 of the input member 122 of the one-way clutch 120 can be set to “zero”. The gear ratio i can be set to “infinity (∞)”.

  FIG. 10 is a cross-sectional view of the one-way clutch 120 and a partially enlarged view thereof. 11A to 11C are partially enlarged views of the one-way clutch 120 in each state. As shown in FIGS. 10 and 11A to 11C, the surface of the output member 121 in contact with the roller 123 is a recess in which the roller 123 can move in the swing direction according to the swing motion of the input member 122. Have However, the depth of the recess differs between the position of the input member 122 in the idling direction shown in FIG. 10 and the position in the torque transmission direction, and the depth of the position in the idling direction is deeper than the depth of the position in the torque transmission direction.

  When the input member 122 is swung in the idling direction relative to the output member 121, the roller 123 also moves in the idling direction. The space from the input member 122 to the output member 121 at the position in the idling direction is slightly larger than the size of the roller 123. For this reason, the roller 123 moved to the position rotates idly. On the other hand, when the input member 122 is relatively swung in the torque transmission direction relative to the output member 121, the roller 123 is also moved in the torque transmission direction. The space from the input member 122 to the output member 121 at the position in the torque transmission direction is slightly narrower than the size of the roller 123. For this reason, as shown in FIG. 11A, the roller 123 moved to the position is sandwiched between the input member 122 and the output member 121, and receives pressure in a direction facing each other. At this time, the input member 122 and the output member 121 are engaged (locked) via the roller 123, and the swinging power of the input member 122 is converted into the rotational motion of the output member 121. Thereafter, when the rotational speed of the input member 122 is lower than the rotational speed of the output member 121 and the input member 122 is swung in the idling direction relative to the output member 121, the lock via the roller 123 is released, As shown in FIG. 11C, the one-way clutch 120 returns to a free state (idle state).

JP-T-2005-502543 German Patent No. 102009039993 JP-A-61-105353

  As described in Patent Document 3, a transmission control device that controls the transmission ratio of a continuously variable transmission controls the transmission ratio according to the vehicle speed and the throttle opening. That is, the gear change control device calculates a gear ratio corresponding to the vehicle speed and the throttle opening or indirectly a physical quantity that represents the gear ratio, sets the calculation result to a target value, and determines whether the actual gear ratio or the physical quantity is Feedback control is performed so as to follow the target value.

  The roller 123 constituting the one-way clutch 120 of the continuously variable transmission described above is generally formed of a material such as metal having high rigidity, but has torsion (twist) characteristics. The torsional characteristics are a combination of characteristics due to slippage of the roller 123 with respect to the input member 122 and the output member 121 and characteristics due to elastic deformation due to pressure from the input member 122 and the output member 121.

  The continuously variable transmission including the roller 123 having such a torsion characteristic is a mechanism using a four-bar link, but in this mechanism, the characteristics of the speed ratio with respect to the eccentricity r1 are geometrically nonlinear. FIG. 12 is a graph showing the characteristics of the gear ratio with respect to the eccentricity r1 in the continuously variable transmission shown in FIG. 6 for each different input torque. As shown in FIG. 12, the characteristics of the gear ratio with respect to the eccentricity r1 vary depending on the input torque.

  Therefore, when the torque input from the power source to the continuously variable transmission increases, the gear ratio increases even if the eccentricity r1 is kept constant. Thus, when the gear ratio is unintentionally increased, the rotational speed of the power source is increased and the drivability is deteriorated. Further, when the rotational speed of the power source increases in this way, a difference from the target rotational speed occurs, so that even if the above-described transmission control device performs feedback control of the transmission ratio, the power source is in a state where the driving efficiency is high. Cannot be made to follow transiently. As a result, fuel consumption performance and the like are reduced.

  An object of the present invention is to provide a speed change control device capable of appropriately controlling a speed change ratio in a continuously variable transmission whose characteristic of a speed change ratio with respect to an eccentric amount is geometrically nonlinear.

In order to solve the above-described problems and achieve the object, a shift control apparatus according to a first aspect of the present invention is based on an input center by receiving rotational power from a power source (for example, the internal combustion engine in the embodiment). An input shaft (for example, the input shaft 101 in the embodiment) that rotates around an axis (for example, the input center axis O1 in the embodiment), and an inner peripheral disk (for example, eccentrically provided on the input shaft ) , An inner circumferential disk 108 in the embodiment, a circular hole that is eccentrically rotated with respect to the inner circumferential disk and has a center at a position off the center of rotation (for example, in the embodiment An outer peripheral disk having the first circular hole 106 (for example, the outer peripheral disk 105 in the embodiment), and an internal gear formed on the inner periphery of the circular hole of the outer peripheral disk (for example, Meshing with the internal gear 107) in the embodiment, the input center axis O The eccentricity modifiable pinion (e.g., a pinion 101 in the embodiment) with respect to have eccentricity (e.g., eccentricity r1 in the embodiment) first fulcrum capable of changing a for the input central axis line ( For example, an eccentric disk (for example, in the embodiment) having the first fulcrum O3 in the embodiment at each center and rotating around the input center axis along with the input shaft while maintaining the eccentric amount. An eccentric disk 104), an output member (for example, the output member 121 in the embodiment) that rotates around an output center axis (for example, the output center axis O2 in the embodiment) separated from the input center axis, and An input member (for example, the input member 122 in the embodiment) that swings around the output center axis by receiving power in the rotational direction from the outside, and the input member and the output member are connected to each other. Engagement member (for example, the roller 123 in the embodiment) to be in a closed state or a non-lock state, and the rotational speed in the positive direction of the input member exceeds the rotational speed in the positive direction of the output member A one-way clutch (for example, a one-way clutch in an embodiment) that transmits rotational power input to the input member to the output member, thereby converting a swinging motion of the input member into a rotational motion of the output member. 120), one end of which is rotatably connected to the outer periphery of the eccentric disk around the first fulcrum, and the other end is provided at a position spaced from the output center axis on the input member of the one-way clutch. By being rotatably connected to two fulcrums (for example, the second fulcrum O4 in the embodiment), the rotational movement given to the eccentric disk from the input shaft can be changed to the one-way club. Adjusting the amount of eccentricity of the first fulcrum with respect to the input center axis, and a connecting member (for example, connecting member 130 in the embodiment) that transmits the input member to the input member as a swinging motion of the input member. And an actuator (for example, an actuator in an embodiment) that changes a swing angle of a swing motion transmitted from the eccentric disk to the input member of the one-way clutch, and is thereby input to the input shaft The gear ratio is changed when the rotational power is transmitted as rotational power to the output member of the one-way clutch through the eccentric disk and the connecting member, and the eccentric amount can be set to zero, thereby changing the speed change. A variable speed ratio variable mechanism that sets the ratio to infinity (for example, the variable speed ratio variable mechanism 112 in the embodiment) and a continuously variable transmission of a four-bar link mechanism type A speed change control apparatus for controlling the speed ratio in claim 1, wherein a required output deriving unit (for example, an internal combustion engine required output deriving unit 201 in the embodiment) for deriving a required output to the power source; An output torque deriving unit (for example, an output torque calculating unit 203 in the embodiment) for deriving an output torque of the power source according to the number of rotations of the power source, and a request output to the power source, A target input rotational speed deriving unit (for example, a target BD input rotational speed deriving unit 205 in the embodiment) for deriving a target input rotational speed in the continuously variable transmission, and an actual input rotational speed in the continuously variable transmission By performing feedback control in accordance with a difference between an actual speed ratio that is a ratio of an actual output speed and a target speed ratio that is a ratio of the actual output speed to the target input speed, the eccentricity is performed. The eccentric amount control unit for deriving the eccentricity control section for controlling (e.g., the eccentricity amount control unit 207 in the embodiment), provided with a feedback gain of the feedback control, the four-bar linkage type Based on a non-linear characteristic of the gear ratio with respect to the eccentric amount in the continuously variable transmission, the stepped transmission has a substantially inversely proportional relationship with the eccentric amount.

  Furthermore, in the transmission control apparatus according to the second aspect of the present invention, the feedback gain of the feedback control increases as the output torque of the power source decreases.

According to the shift control device of the invention according to claim 1-2, characteristics of the transmission ratio to the amount of eccentricity can properly control the transmission ratio in geometrically nonlinear CVT.

The block diagram which shows the internal structure of the speed-change control apparatus of one Embodiment. Graph showing characteristics related to thermal efficiency of internal combustion engines Block diagram showing the internal configuration of the eccentricity control unit 207 A graph showing the relationship between the eccentricity r1, the output torque Tout and the feedback gain 1 is a flowchart showing the operation of the speed change control device shown in FIG. Side sectional view of a part of the continuously variable transmission called IVT as seen from the axial direction Illustration of the driving force transmission principle of a continuously variable transmission configured as a four-bar linkage mechanism (A)-(d) is explanatory drawing of the speed change principle by the gear ratio variable mechanism 112 in the continuously variable transmission shown in FIG. (A)-(c) is explanatory drawing of the speed change principle by the gear ratio variable mechanism 112 in the continuously variable transmission shown in FIG. Sectional view of the one-way clutch 120 and a partially enlarged view thereof (A)-(c) is a partially expanded view in each state of the one-way clutch 120. FIG. 6 is a graph showing the characteristics of the gear ratio with respect to the eccentricity r1 in the continuously variable transmission shown in FIG.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The transmission control device according to the present invention controls the eccentricity r1 so that the transmission ratio in the continuously variable transmission (hereinafter also referred to as “BD”) called IVT (Infinity Variable Transmission) described above becomes an appropriate value. In the following description, the power source on the input side of the IVT will be described as an internal combustion engine that is a drive source of the vehicle. In this embodiment, the crankshaft of the internal combustion engine is directly connected to the input shaft of the continuously variable transmission. Therefore, the output of the internal combustion engine is directly input to the continuously variable transmission.

  FIG. 1 is a block diagram illustrating an internal configuration of a transmission control apparatus according to an embodiment. 1 includes an internal combustion engine required output deriving unit 201, an output torque calculating unit 203, a target BD input rotation speed deriving unit 205, and an eccentricity control unit 207.

  The internal combustion engine required output deriving unit 201 derives an output (internal combustion engine required output) required for an internal combustion engine (not shown) based on the traveling speed (vehicle speed) of the vehicle and the accelerator pedal opening (AP opening).

  The output torque calculation unit 203 calculates a torque obtained by dividing the internal combustion engine required output derived by the internal combustion engine required output deriving unit 201 by the rotational speed of the internal combustion engine (internal combustion engine rotational speed) as the output torque Tout of the internal combustion engine. . As described above, in this embodiment, the output of the internal combustion engine is directly input to the continuously variable transmission. Therefore, the output torque Tout of the internal combustion engine is also the input torque (BD input torque) of the continuously variable transmission.

  The target BD input rotational speed deriving unit 205 derives a target input rotational speed (target BD input rotational speed) in the continuously variable transmission (BD) according to the internal combustion engine required output. As described above, in this embodiment, the output of the internal combustion engine is directly input to the continuously variable transmission. Therefore, the target BD input rotational speed deriving unit 205 outputs the rotational speed of the internal combustion engine corresponding to the operating point with the best fuel consumption rate of the internal combustion engine as the target BD input rotational speed when priority is given to the efficiency of the internal combustion engine. .

  FIG. 2 is a graph showing characteristics relating to thermal efficiency of the internal combustion engine. The vertical axis of the graph shows the torque of the internal combustion engine, and the horizontal axis shows the rotational speed of the internal combustion engine. The thick solid line in FIG. 2 is a line connecting the operating points of the internal combustion engine with the best fuel consumption rate (BSFC bottom line), and the alternate long and short dash line is an equal output line. The target BD input rotational speed deriving unit 205 derives, as the target BD input rotational speed, the rotational speed corresponding to the operating point at which the equal output line corresponding to the input internal combustion engine required output intersects the BSFC bottom line.

  The eccentricity control unit 207 includes (0) an actual eccentricity r1, (1) an output torque (BD input torque) Tout of the internal combustion engine, (2) a target BD input rotational speed, and (3) a continuously variable transmission ( BD) based on the actual input speed (actual BD input speed) and (4) the actual output speed (actual BD output speed) in the continuously variable transmission (BD). Then, an eccentricity amount control term for controlling the eccentricity amount r1 in the continuously variable transmission is derived. The eccentricity r1 is the distance between the first fulcrum O3 that is the center of the eccentric disk 104 shown in FIG. 6 and the input center axis O1 that is the center of the pinion 110. A signal indicating the eccentricity control term derived by the eccentricity control unit 207 is input as a drive signal to an actuator (not shown) that rotates the pinion 110 of the continuously variable transmission (BD) described above. When the pinion 110 is rotated by the actuator, the amount of eccentricity r1 changes. The actual eccentricity r1 is obtained by integrating the rotation speed of the actuator.

  The operation of the eccentricity control unit 207 and details of the internal configuration will be described below. FIG. 3 is a block diagram showing an internal configuration of the eccentricity control unit 207. As shown in FIG. 3, the eccentricity control unit 207 includes a target ratio calculation unit 211, an actual ratio calculation unit 213, a ratio difference calculation unit 215, and a feedback control unit (FB control unit) 217.

The target ratio calculation unit 211 calculates a target value (target ratio) of the gear ratio in the continuously variable transmission (BD) based on (2) the target BD input rotation speed and (4) the actual BD output rotation speed. That is, the target ratio calculation unit 211 calculates (2) a ratio of (4) actual BD output rotation speed to target BD input rotation speed (= actual BD output rotation speed / target BD input rotation speed ).

  The actual ratio calculation unit 213 calculates the actual value (actual ratio) of the speed ratio in the continuously variable transmission (BD) based on (3) the actual BD input rotation speed and (4) the actual BD output rotation speed. That is, the actual ratio calculation unit 213 calculates (3) the ratio of (4) actual BD output rotation speed to actual BD input rotation speed (= actual BD output rotation speed / actual BD input rotation speed).

  The ratio difference calculation unit 215 calculates a difference between the target ratio calculated by the target ratio calculation unit 211 and the actual ratio calculated by the actual ratio calculation unit 213 (ratio difference Δi = target ratio−actual ratio).

  The feedback control unit (FB control unit) 217 performs the PI control or the PID control according to the ratio difference Δi calculated by the ratio difference calculation unit 215, thereby providing an eccentricity amount as a feedback control term (FB control term) of the eccentricity amount r1. Deriving control terms. Note that the FB control unit 217 of the present embodiment schedules the feedback gain based on the actual eccentricity r1 and the output torque Tout when the eccentricity control term is derived.

  FIG. 4 is a graph showing the relationship between the eccentricity r1, the output torque Tout, and the feedback gain. As shown in FIG. 4, the feedback gain has a substantially inversely proportional relationship with the eccentricity r1 and the output torque Tout, and is larger as the eccentricity r1 is larger and larger as the output torque Tout is smaller. The FB control unit 217 derives a feedback gain based on the actual eccentricity r1 and the output torque Tout, and performs PI control or PID control according to the ratio difference Δi using the gain.

  FIG. 5 is a flowchart showing the operation of the shift control apparatus shown in FIG. As shown in FIG. 5, the internal combustion engine required output deriving unit 201 of the shift control device derives the internal combustion engine required output based on the vehicle speed and the AP opening (step S101). Next, the target BD input rotational speed deriving unit 205 derives a target BD input rotational speed in the continuously variable transmission (BD) corresponding to the internal combustion engine required output (step S103). Next, the output torque calculation unit 203 calculates the output torque Tout of the internal combustion engine from the internal combustion engine required output derived in step S101 and the internal combustion engine speed (step S105).

  Next, the eccentricity control unit 207 calculates the difference between the target ratio and the actual ratio (ratio difference Δi) (step S107). Next, the eccentricity control unit 207 derives an eccentricity control term by performing PI control or PID control in accordance with the ratio difference Δi calculated in step S107 (step S109). Finally, the transmission control device controls the transmission ratio of the continuously variable transmission (BD) using the eccentricity control term derived in step S109 (step S111).

  As described above, the speed change control device according to the present embodiment is based on the actual eccentricity r1 and the output torque Tout when the eccentricity control term is derived so that the transmission ratio in the continuously variable transmission (BD) becomes an appropriate value. Schedule feedback gains. By controlling the eccentricity r1 according to the eccentricity control term thus derived, the gear ratio of the continuously variable transmission is appropriately controlled.

DESCRIPTION OF SYMBOLS 101 Input shaft 104 Eccentric disk 110 Pinion 112 Transmission ratio variable mechanism 120 One-way clutch 121 Output member 122 Input member 123 Roller (engagement member)
130 Connecting member 131 One end (ring part)
132 other end 133 circular opening 140 bearing 201 internal combustion engine required output deriving unit 203 output torque calculating unit 205 target BD input rotation speed deriving unit 207 eccentricity control unit 211 target ratio calculating unit 213 actual ratio calculating unit 215 ratio difference calculating unit 217 Feedback control unit (FB control unit)

Claims (2)

An input shaft that rotates around the input center axis by receiving rotational power from a power source;
An inner circumferential disk provided eccentrically on the input shaft, an outer circumferential disk provided with a circular hole centered at a position off the center of rotation, provided eccentrically with respect to the inner circumferential disk, and rotated; And a pinion that meshes with an internal gear formed on the inner periphery of the circular hole of the outer circular disc and can change the amount of eccentricity with respect to the input center axis, and the amount of eccentricity with respect to the input center axis can be changed. An eccentric disk having a first fulcrum at each center and rotating around the input center axis with the input shaft while maintaining the amount of eccentricity;
An output member that rotates around an output center axis that is distant from the input center axis, an input member that swings around the output center axis by receiving power in the rotational direction from the outside, the input member, and the output member Engaging members that lock or unlock each other, and when the rotational speed in the positive direction of the input member exceeds the rotational speed in the positive direction of the output member, the input member is input to the input member. A one-way clutch that transmits rotational power to the output member, thereby converting a swinging motion of the input member into a rotational motion of the output member;
One end is rotatably connected to the outer periphery of the eccentric disk around the first fulcrum, and the other end is rotated to a second fulcrum provided at a position away from the output center axis on the input member of the one-way clutch. A connecting member that is movably connected to transmit a rotational motion given from the input shaft to the eccentric disk as a swinging motion of the input member to the input member of the one-way clutch;
An actuator for changing a swing angle of a swing motion transmitted from the eccentric disk to the input member of the one-way clutch by adjusting an eccentric amount of the first fulcrum with respect to the input center axis; The rotational power input to the input shaft can be changed as the rotational power to the output member of the one-way clutch via the eccentric disk and the connecting member, and the eccentricity can be set to zero. A transmission ratio variable mechanism that sets the transmission ratio to infinity,
A shift control device for controlling the gear ratio in a continuously variable transmission of a four-bar linkage mechanism comprising:
A required output deriving unit for deriving a required output to the power source;
An output torque deriving unit for deriving an output torque of the power source according to the required output and the rotational speed of the power source;
A target input rotational speed deriving unit for deriving a target input rotational speed in the continuously variable transmission according to a required output to the power source;
According to a difference between an actual transmission ratio that is a ratio of an actual output speed to an actual input speed in the continuously variable transmission and a target speed ratio that is a ratio of the actual output speed to the target input speed. An eccentricity control unit for deriving an eccentricity control term for controlling the eccentricity by performing feedback control, and
The feedback gain of the feedback control has a relationship that is substantially inversely proportional to the eccentric amount based on a non-linear characteristic of the gear ratio with respect to the eccentric amount in the continuously variable transmission of the four-bar linkage mechanism type. Control device. The shift control device according to claim 1,
The speed change control apparatus according to claim 1, wherein the feedback gain of the feedback control increases as the output torque of the power source decreases.

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