JP5514789B2 - 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 configured as a four-bar linkage mechanism.

  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. 7 is a cross-sectional view showing a specific configuration of a continuously variable transmission called IVT. FIG. 8 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 FIGS. 7 and 8 rotates around an input center axis O1 by receiving rotational power from a power source such as an internal combustion engine, and the input shaft 101 is supported by bearings 102 and 103 at both ends. And a plurality of eccentric disks 104 that rotate integrally with the input shaft 101, the same number of connecting members 130 as the eccentric disks 104 for connecting the input side and the output side, and a one-way clutch 120 provided on the output side.

  The plurality of eccentric disks 104 are each formed in a circular shape centered on the first fulcrum O3. The first fulcrum O3 is provided at equal intervals in the circumferential direction of the input shaft 101, and each of the first fulcrums O3 maintains an eccentricity r1 that can be changed with respect to the input center axis O1, and the input shaft 101 around the input center axis O1. It is set to rotate with. Therefore, the plurality of eccentric disks 104 are provided so as 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. 8, 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. As shown in FIG. 7, the pinion 110 is rotated inside the second circular hole 109 by an actuator 180 configured by a DC motor and a speed reduction mechanism. 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 180 are arranged so as to be connected to each other and the rotation of the actuator 180 causes a rotation difference with respect to the rotation of the input shaft 101, a reduction ratio is applied to the rotation difference. 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 by the amount. At this time, if there is no rotational difference between the actuator 180 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.

  As shown in FIG. 7, the output member 121 of the one-way clutch 120 is configured as a member that is integrally continuous in the axial direction. However, the input member 122 is divided into a plurality of portions in the axial direction, and the eccentric disk As many as 104 and the number of connecting members 130 are arranged so as to be able to swing independently in the axial direction. The roller 123 is inserted between the input member 122 and the output member 121 for each input member 122.

  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 arrow RD1 direction in FIG. 8) 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.

  Further, as shown in FIG. 8, a projecting portion 124 is provided at one circumferential position on each ring-shaped input member 122, and a second fulcrum spaced from the output center axis O2 is provided on the projecting portion 124. O4 is provided. And the pin 125 is arrange | positioned on the 2nd fulcrum O4 of each 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. 9, 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. The rotational motion given to the eccentric disk 104 from the input shaft 101 is transmitted to the input member 122 of the one-way clutch 120 as the swing motion of the input member 122, and the swing motion of the input member 122 Is converted into a rotational motion of the output member 121.

  FIG. 9 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. 9, the swing period of the input member 122 of the one-way clutch 120 is always constant regardless of the value of the eccentricity r1 of the eccentric disk 104. 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. The eccentric amount r1 of the eccentric disk 104 can be changed by moving the pinion 110 of the speed ratio variable mechanism 112 configured by the actuator 105 and the actuator 180 with the actuator 180. 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.

  10 (a) to 10 (d) and FIGS. 11 (a) to 11 (c) are explanatory views of the speed change principle by the speed ratio variable mechanism 112 in the continuously variable transmission shown in FIG. As shown in FIGS. 10 and 11, 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. 10A and 11A, 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. As shown in FIGS. 10B and 11B, 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. 10C and 11C, 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 decreased. Therefore, a large gear ratio i can be realized. Further, as shown in FIG. 10D, 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. 12 shows the continuously variable transmission shown in FIG. 8 in which the eccentric amount r1 (speed ratio i) of the eccentric disk 104 that rotates at the same speed as the input shaft 101 is changed to “large”, “medium”, and “small”. 6 is a diagram showing the relationship between the rotation angle (θ) of the input shaft 101 and the angular velocity ω2 of the input member 122 of the one-way clutch 120 when FIG. 13 shows the continuously variable transmission shown in FIG. 8, in which power is transmitted from the input side (the input shaft 101 and the eccentric disk 104) to the output side (the output member 121 of the one-way clutch 120) by a plurality of connecting members 130. It is a figure for demonstrating the taking-out principle of the output at the time.

  As shown in FIG. 9, the input member 122 of the one-way clutch 120 oscillates with the power applied from the eccentric disk 104 via the connecting member 130. 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. 12, the swing cycle of the input member 122 of the one-way clutch 120 is always constant regardless of the value of the eccentricity r1 of the eccentric disk 104. 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.

  As shown in FIG. 8, one end (ring part 131) of a plurality of connecting members 130 connecting the input shaft 101 and the one-way clutch 120 is rotated by an eccentric disk 104 provided at equal intervals in the circumferential direction around the input center axis O1. It is connected freely. For this reason, the swinging motion brought about by the rotational motion of each eccentric disk 104 to the input member 122 of the one-way clutch 120 sequentially occurs at a constant phase as shown in FIG.

  After the driving by one connecting member 130 is finished, the rotational speed of the input member 122 is lower than the rotating speed of the output member 121, and the lock by the roller 123 is released by the driving force of the other connecting member 130, and free Return to the normal state (idle state). This is sequentially performed by the number of the connecting members 130, whereby the swinging motion is converted into a unidirectional rotational motion. Therefore, only the power of the input member 122 at a timing exceeding the rotational speed of the output member 121 is transmitted to the output member 121 in order, and the rotational power leveled almost smoothly is applied to the output member 121.

JP-T-2005-502543

  In the continuously variable transmission described above, the torque applied to the pinion 110 (pinion torque) changes according to the state quantities such as the input rotation speed, input torque, and gear ratio i in the gear ratio variable mechanism 112. When the pinion torque changes, even if the actuator 180 changes the eccentricity r1 to the target value, the output of the continuously variable transmission becomes a value deviated from the target.

  An object of the present invention is to provide a transmission control device capable of appropriately controlling a transmission ratio in a continuously variable transmission configured as a four-bar linkage mechanism.

In order to solve the above problems and achieve the object, a shift control device according to the first aspect of the invention (for example, the shift control device 200 in the embodiment) is provided with a power source (for example, in the embodiment). An input that rotates around an input center axis (for example, the input center axis O1 in the embodiment ) that is the center of the pinion (for example, the pinion 110 in the embodiment ) by receiving rotational power from the internal combustion engine) A first fulcrum (for example, the first shaft in the embodiment) that can change the axis (for example, the input shaft 101 in the embodiment) and the amount of eccentricity (for example, the amount of eccentricity r1 in the embodiment) with respect to the input center axis. An eccentric disk (for example, the eccentric disk 104 in the embodiment) having one fulcrum O3) at each center and rotating around the input center axis while keeping the eccentric amount together with the input shaft, and the input Center axis 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) that is far away from the outside, and power in the rotational direction from the outside. An input member that swings around the output center axis (for example, the input member 122 in the embodiment) and an engaging member that locks or unlocks the input member and the output member (for example, implementation) 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 rotational power input to the input member is converted into the output member. A one-way clutch (for example, the one-way clutch 120 in the embodiment) that converts the swinging motion of the input member into the rotational motion of the output member, and one end of the eccentric A second fulcrum (for example, an embodiment) that is connected to the outer periphery of the disc so as to be rotatable about the first fulcrum, and the other end is provided at a position separated from the output center axis on the input member of the one-way clutch. The second fulcrum O4) is pivotally coupled to transmit the rotational motion applied from the input shaft to the eccentric disk to the input member of the one-way clutch as a swinging motion of the input member. connecting members (e.g., the connecting member 130 in the embodiment) and, by adjusting the eccentricity of the first pivot the pinion with respect to the input central axis by causing relative rotation with respect to the input shaft, the eccentric disc An actuator (for example, actuator 180 in the embodiment) that changes the swing angle of the swing motion transmitted to the input member of the one-way clutch from And changing the transmission gear ratio when the rotational power input to the input shaft is transmitted as rotational power to the output member of the one-way clutch via the eccentric disk and the connecting member, and the eccentricity A variable transmission ratio mechanism (for example, the transmission ratio variable mechanism 112 in the embodiment) that sets the transmission ratio to infinity by allowing the amount to be set to zero. A shift control apparatus for controlling the speed ratio in a step transmission, wherein a required output deriving unit (for example, an internal combustion engine required output deriving unit 201 in an embodiment) for deriving a required 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 according to a required output to the power source; Enter A target eccentricity deriving unit (for example, a target eccentricity deriving unit 207 in the embodiment) for deriving a target eccentricity amount corresponding to a target gear ratio that is a ratio of the actual output rotational speed of the continuously variable transmission to the rotational speed. And an eccentricity control term for controlling the eccentricity based on the difference between the target eccentricity and the actual eccentricity in the continuously variable transmission, and obtained from the state of the continuously variable transmission depending on the load characteristics according to the pinion of the gear ratio variable mechanism, the eccentric amount control unit for compensating the eccentricity control term (e.g., the eccentricity amount control unit 209 in the embodiment) and comprises, is the compensation The actuator rotates the pinion according to a control signal based on the eccentricity control term .

Furthermore, in the shift control apparatus according to the second aspect of the present invention, the load characteristic indicates that the load applied to the pinion of the speed ratio variable mechanism shows a larger characteristic as the input rotational speed in the continuously variable transmission is higher. It is a feature.

Furthermore, in the speed change control device according to claim 3, the load characteristic indicates that the load applied to the pinion of the speed ratio variable mechanism becomes larger as the input torque in the continuously variable transmission is larger. It is said.

Furthermore, in the speed change control apparatus according to the fourth aspect of the invention, the load characteristic is such that the load applied to the pinion of the speed ratio variable mechanism shows a larger characteristic as the speed ratio is smaller.

  Furthermore, the shift control apparatus according to the invention of claim 5 further includes a target value filter unit that filters the target eccentricity derived by the target eccentricity deriving unit so that the rate of change is reduced. .

According to the shift control apparatus of the first to fifth aspects of the present invention, the gear ratio is adjusted by compensating for the eccentricity based on the load characteristic applied to the pinion of the gear ratio variable mechanism of the continuously variable transmission configured as a four-bar linkage mechanism. It can be controlled properly.
According to the fifth aspect of the present invention, since the difference from the actual eccentricity can be reduced, the correction amount of the transmission ratio can be reduced.

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 The graph which showed the characteristic of the gear ratio i with respect to eccentricity r1 in the continuously variable transmission shown in FIG. 8 for every different input torque. The block diagram which shows the internal structure of the eccentricity control part 209 When the BD input rotation speed is low, medium, or high in a continuously variable transmission (BD), a graph that is a basis of a map showing the pinion torque with respect to the gear ratio i for each BD input torque 1 is a flowchart showing the operation of the speed change control device shown in FIG. Sectional drawing which shows the concrete structure of continuously variable transmission called IVT 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. In the continuously variable transmission shown in FIG. 8, the input shaft when the eccentricity r1 (speed ratio i) of the eccentric disk that rotates at the same speed as the input shaft is changed to “large”, “medium”, and “small”. It is a figure which shows the relationship between rotational angle (theta) of this, and angular velocity (omega) 2 of the input member of a one-way clutch. In the continuously variable transmission shown in FIG. 8, the principle of output extraction when power is transmitted from the input side (input shaft or eccentric disk) to the output side (output member of the one-way clutch) by a plurality of connecting members will be described. 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. The eccentricity r1 is the distance between the first fulcrum O3 that is the center of the eccentric disk 104 shown in FIG. 8 and the input center axis O1 that is the center of the pinion 110. 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. A shift control device 200 shown in FIG. 1 is a device that controls driving of an actuator 180, and is 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 a target eccentricity amount. A derivation unit 207 and an eccentricity control unit 209 are provided. The shift control device 200 includes a signal indicating the vehicle traveling speed (vehicle speed), a signal indicating the accelerator pedal opening (AP opening), a signal indicating the rotation speed of the internal combustion engine, and an encoder that detects the rotation speed of the actuator 180. A signal from 190 is input. The vehicle speed is obtained from a signal from a rotation speed sensor that detects the rotation speed of the drive shaft of the vehicle.

  The internal combustion engine required output deriving unit 201 derives an output required for the internal combustion engine (internal combustion engine required output) based on the vehicle speed and the AP opening.

  The output torque calculation unit 203 calculates the output torque of the internal combustion engine 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 described above, in this embodiment, the output of the internal combustion engine is directly input to the continuously variable transmission. Therefore, the output torque of the internal combustion engine calculated by the output torque calculation unit 203 is also the target input torque (target 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 target eccentricity deriving unit 207 calculates the target gear ratio by dividing the actual output rotational speed (actual BD output rotational speed) in the continuously variable transmission (BD) by the target BD input rotational speed. The actual BD output rotational speed corresponds to the rotational speed of the drive shaft of the vehicle. In the continuously variable transmission (BD), the characteristic of the speed ratio i with respect to the eccentricity r1 is geometrically nonlinear. FIG. 3 is a graph showing the characteristics of the speed ratio i with respect to the eccentricity r1 in the continuously variable transmission shown in FIG. 8 for each different input torque. As shown in FIG. 3, the characteristic of the eccentricity r1 with respect to the gear ratio i varies depending on the input torque. Therefore, the target eccentric amount deriving unit 207 refers to the graph shown in FIG. 3 and derives an eccentric amount corresponding to the target gear ratio based on the target BD input torque. The target eccentricity deriving unit 207 outputs the eccentricity derived in this way as the target eccentricity r1t.

  The eccentricity control unit 209 derives an eccentricity control term obtained according to the difference (Δr1) between the target eccentricity r1t and the actual eccentricity (actual eccentricity) r1r, and then continuously determines the eccentricity control term. Compensation is performed based on load characteristics applied to the pinion 110 constituting the transmission ratio variable mechanism 112 of the transmission (BD). The eccentricity control unit 209 outputs a control signal based on the compensated eccentricity control term to the actuator 180. The actuator 180 rotates and drives the pinion 110 according to the control signal output from the eccentricity control unit 209. When the pinion 110 rotates, the eccentricity r1 changes.

  FIG. 4 is a block diagram showing the internal configuration of the eccentricity control unit 209. As shown in FIG. 4, the eccentricity control unit 209 includes an actual eccentricity derivation unit 211, a map storage unit 215, an actual transmission ratio calculation unit 217, a gain calculation unit 219, a target value filter unit 221, a gain A control unit 223 and a control signal generation unit 225 are included. The gain control unit 223 includes a P gain control unit 223P, an I gain control unit 223I, and a D gain control unit 223D.

  The actual eccentricity deriving unit 211 derives the eccentricity r1 corresponding to the difference between the rotational speed of the actuator 180 indicated by the input signal from the encoder 190 and the actual BD input rotational speed as the actual eccentricity r1r.

  The map storage unit 215 stores a map indicating the pinion torque with respect to the transmission ratio i for each BD input torque in the continuously variable transmission (BD) for each different BD input rotation speed. FIG. 5 is a graph as a basis of a map showing the pinion torque with respect to the gear ratio i for each BD input torque when the BD input rotation speed is low, medium, and high in the continuously variable transmission (BD). Indicates. As shown in FIG. 5, the higher the BD input rotational speed, the greater the pinion torque. Moreover, the pinion torque increases as the BD input torque increases. Further, the smaller the gear ratio i, the larger the pinion torque.

  The actual speed ratio calculation unit 217 divides the actual output speed (actual BD output speed) in the continuously variable transmission (BD) by the actual input speed (actual BD input speed) to obtain the actual speed ratio. (Actual gear ratio) is calculated. As described above, since the crankshaft of the internal combustion engine is directly connected to the input shaft of the continuously variable transmission, the actual BD input rotational speed is equal to the rotational speed of the internal combustion engine.

  The gain calculation unit 219 includes a signal indicating the target BD input torque substituted by the output torque calculated by the output torque calculation unit 203, a signal indicating the actual BD input rotation speed, and the actual speed ratio calculation unit 217 calculated by the actual speed ratio calculation unit 217. A signal indicating the gear ratio is input. The gain calculation unit 219 uses the information indicated by the input signal and the map read from the map storage unit 215 to torque (pinion) applied to the pinion 110 constituting the transmission ratio variable mechanism 112 of the continuously variable transmission (BD). (Torque), and each gain of the eccentricity control term corresponding to the pinion torque is obtained by calculation. Note that gain scheduling is applied to each gain of the eccentricity control term corresponding to the pinion torque, and the gain at each operating point is preset by a calculation formula or the like.

  The target value filter unit 221 filters the target eccentric amount r1t according to the pinion torque derived by the gain calculation unit 219. The filtering is performed to reduce the rate of change of the target eccentricity r1t (smooth), and the degree (filter amount) increases as the pinion torque increases.

  The gain control unit 223 determines each gain (P) of the eccentricity amount control term which is a difference (Δr1 = r1t−r1r) between the actual eccentricity amount r1r and the filtered target eccentricity amount r1t according to the calculation result of the gain calculation unit 219. (Gain, I gain, D gain) are controlled. The control signal generator 225 generates a control signal corresponding to the gain eccentricity control term controlled by the gain controller 223. The control signal is input to the actuator 180.

  FIG. 6 is a flowchart showing the operation of the shift control apparatus 200 shown in FIG. As shown in FIG. 6, the internal combustion engine required output deriving unit 201 of the transmission control device 200 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 an output torque (target BD input torque) 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 target eccentricity deriving unit 207 calculates a target gear ratio, and then derives a target eccentricity r1t corresponding to the target gear ratio and the target BD input torque derived in step S105 (step S107). . Next, the eccentricity control unit 209 filters the target eccentricity r1t (step S108). Next, the eccentricity control unit 209 calculates an eccentricity control term that is a difference (Δr1) between the filtered target eccentricity r1t and the actual eccentricity r1r (step S109). Next, the eccentricity amount control unit 209 compensates the eccentricity amount control term calculated in step S109 based on the load characteristic applied to the pinion 110 constituting the transmission ratio variable mechanism 112 of the continuously variable transmission (BD) (step S109). S111). Finally, the eccentricity control unit 209 outputs a control signal based on the eccentricity control term compensated in Step S111 to the actuator 180 (Step S113).

  As described above, according to the present embodiment, the eccentricity control term is compensated based on the load characteristic applied to the pinion 110 constituting the transmission ratio variable mechanism 112 of the continuously variable transmission (BD), and the compensated eccentricity is performed. The eccentricity r1 is controlled according to the quantity control term. Therefore, even if the pinion torque changes, the eccentricity r1 can be adjusted to the target value, so that the gear ratio i of the continuously variable transmission (BD) is appropriately controlled. Further, since the target value of the eccentricity r1 is filtered, the difference (eccentricity control term) from the actual eccentricity becomes small. As a result, the correction amount of the gear ratio i can be reduced.

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 180 Actuator 190 Encoder 200 Transmission control device 201 Internal combustion engine required output deriving unit 203 Output torque calculating unit 205 Target BD input rotation speed deriving unit 207 Target eccentricity deriving unit 209 Eccentricity amount controlling unit 211 Eccentricity derivation unit 215 Map storage unit 217 Actual gear ratio calculation unit 219 Gain calculation unit 221 Target value filter unit 223 Gain control unit 225 Control signal generation unit 223P P gain control unit 223I I gain control unit 223D D gain control unit

Claims (5)

An input shaft that rotates around the input center axis that is the center of the pinion by receiving rotational power from the power source;
An eccentric disk having a first fulcrum that can change the amount of eccentricity with respect to the input center axis at each center, and rotating around the input center axis together 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;
By rotating the pinion relative to the input shaft, the eccentric amount of the first fulcrum with respect to the input center axis is adjusted, and the swinging motion transmitted from the eccentric disk to the input member of the one-way clutch is controlled. A gear ratio when the rotational power input to the input shaft is transmitted as rotational power to the output member of the one-way clutch via the eccentric disk and the connecting member. And a gear ratio variable mechanism that sets the gear ratio to infinity by allowing the eccentricity to be set to zero,
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;
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;
A target eccentricity deriving unit for deriving a target eccentricity amount corresponding to a target speed change ratio that is a ratio of an actual output speed in the continuously variable transmission to the target input speed;
Based on a difference between the actual eccentricity and the target eccentricity in the continuously variable transmission, an eccentricity control term for controlling the eccentricity is derived, and the shift obtained from the state of the continuously variable transmission is obtained. An eccentricity control unit that compensates for the eccentricity control term according to a load characteristic applied to the pinion of the ratio variable mechanism ,
The shift control device , wherein the actuator rotationally drives the pinion in response to a control signal based on the compensated eccentricity control term . The shift control device according to claim 1,
The speed change control device according to claim 1, wherein the load characteristic is such that the load applied to the pinion of the variable speed ratio variable mechanism increases as the input rotational speed of the continuously variable transmission increases. The shift control device according to claim 1,
The shift control device according to claim 1, wherein the load characteristic is such that the load applied to the pinion of the variable speed ratio variable mechanism increases as the input torque in the continuously variable transmission increases. The shift control device according to claim 1,
The load control device according to claim 1, wherein the load characteristic is such that a load applied to the pinion of the speed ratio variable mechanism is larger as the speed ratio is smaller. The shift control device according to any one of claims 1 to 4,
A speed change control device comprising a target value filter for filtering the target eccentricity derived by the target eccentricity deriving unit so as to reduce a rate of change thereof.

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