JP2011153649A - Drive control device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a drive control device capable of suppressing an increase in a drive loss. <P>SOLUTION: In the drive control device 1 of a continuously variable transmission 100, a continuously variable transmission mechanism 10 for continuously changing the gear ratio, and a differential mechanism 30 having a plurality of rotation elements (a ring gear 31, a sun gear 32, a planetary gear 33, a planetary gear carrier 34) are disposed between an input shaft 101 and an output shaft 102. A first output disk 13 and a second output disk 14 of the continuously variable transmission mechanism 10 can be controlled to be the same rotational number. In the continuously variable transmission 10, the ratio of the rotational number is continuously changed between the first output disk 13 and the second output disk 14. In the differential mechanism 30, the sun gear 32 and the ring gear 31 are engaged relative to the first output disk 13 and the second output disk 14 with one-to-one relationship. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a drive control device that controls a continuously variable transmission that continuously changes a gear ratio.

  2. Description of the Related Art Conventionally, a continuously variable transmission configured by a so-called traction planetary gear mechanism including a plurality of rotating elements is known. For example, in Patent Document 1 below, a continuously variable transmission mechanism having a plurality of balls (rolling members) sandwiched between an input disk and an output disk, and changing the gear ratio by adjusting the tilt angle of the balls. And a planetary gear mechanism in which one of the rotating elements engages with the output shaft of the continuously variable transmission mechanism. Further, in Patent Document 2 below, in a continuously variable transmission having a belt-type continuously variable transmission mechanism and a planetary gear mechanism, the output of the continuously variable transmission mechanism is transmitted to the sun gear of the planetary gear mechanism and the ring gear is also transmitted. A technique is disclosed in which the output of the prime mover is transmitted and the ring gear and the sun gear are rotated in the same direction, thereby avoiding the circulation of power input to the planetary gear mechanism (that is, the planetary gear mechanism is not operated differentially). Yes. Further, in Patent Document 3 below, in a continuously variable transmission having a toroidal-type continuously variable transmission mechanism and a planetary gear mechanism, the output of the continuously variable transmission mechanism is transmitted to the sun gear or ring gear of the planetary gear mechanism, A technique is disclosed in which the output of the engine can be transmitted to the carrier of the pinion gear and the speed ratio can be widened. In Patent Document 4 below, in a continuously variable transmission having a toroidal-type continuously variable transmission mechanism and a differential unit, the input side disk of the continuously variable transmission mechanism rotates together with the first input portion of the differential unit. This is possible, and the output side disk of the continuously variable transmission mechanism is connected to the second input portion of the differential unit. In the continuously variable transmission of Patent Document 4, the rotational speed of the output shaft is obtained based on the rotational speeds of the input side disk and the output side disk detected by the sensor and the speed ratio of the differential unit, and the output shaft The gear ratio of the continuously variable transmission mechanism is adjusted so that the rotation speed of the motor is zero. Further, in Patent Document 5 below, in a continuously variable transmission having a toroidal continuously variable transmission mechanism and a planetary gear mechanism, state quantities (input torque from the engine, vehicle speed, A technique for correcting a deviation amount from a target gear ratio according to an oil temperature or the like is disclosed. In the continuously variable transmission of Patent Document 5, the relationship between the change amount of the gear ratio and the state quantity is experimentally obtained at the time of control, and a map prepared in advance (correcting the designed gear ratio is corrected based on this). Map).

JP-T-2006-519349 JP 2001-050368 A Japanese Patent Laid-Open No. 11-303969 JP 2005-133777 A JP 2006-348888 A

  By the way, in the continuously variable transmission mechanism, so-called traction fluid having a traction coefficient higher than that of normal ATF (Automatic Transmission Fluid) is used to enable torque transmission on the rolling surface. However, when the traction fluid is used as a lubricating oil for a planetary gear mechanism (differential mechanism), the driving loss increases between the tooth surfaces.

  Therefore, the present invention improves the disadvantages of the conventional example, and can suppress an increase in driving loss of the differential mechanism in the continuously variable transmission drive control apparatus having the continuously variable transmission mechanism and the differential mechanism. The purpose is to provide something.

  In order to achieve the above object, the present invention provides a continuously variable transmission mechanism that continuously changes a transmission gear ratio and a differential mechanism having a plurality of rotating elements disposed between an input unit and an output unit. In the transmission drive control device, each output member of the continuously variable transmission mechanism can be controlled to the same rotational speed. Here, the continuously variable transmission mechanism continuously changes the ratio of the rotational speeds between the plurality of output members, and the differential mechanism applies the rotational element to the output member. Each output member is engaged in a one-to-one relationship.

  Here, it is desirable to control the rotation speed ratio between the output members so that the rotation difference between the rotating elements in the differential mechanism falls within a predetermined range.

  Further, it is desirable to control the rotation speed ratio between the output members so that the rotation difference of the differential mechanism is within a predetermined range including zero.

  The continuously variable transmission mechanism includes an input member connected to the input unit, a rolling member that rolls as the input member rotates, and the two output members that sandwich the rolling member. The torque of the input member is transmitted to the respective output members by the friction force generated between the input member, the rolling member, and the output members, and between the output members. It is desirable to change the ratio of the number of rotations steplessly according to the tilt angle of the rolling member.

  Further, the rotation ratio between the output members can be controlled by inclining the rolling members that are arranged between the creep amounts of the output members and the output members and change the rotation ratio therebetween in a stepless manner. It is desirable to use a map describing the relationship with the turning angle.

  Further, it is desirable that the control of the rotation speed ratio between the output members is performed by detecting the rotation speed of each output member.

  When the continuously variable transmission mechanism includes the two output members, the ratio of the rotation speed between the output members is controlled by any one of the output members, the output members, It is desirable to detect the rotational speed of the rotating element in the differential mechanism that is not engaged.

  Since the drive control device according to the present invention can control each output member of the continuously variable transmission mechanism to the same rotational speed, the rotational elements of the differential mechanism engaged with them are also rotated at the same rotational speed. Is possible. When the rotation speed is controlled to be the same, the differential mechanism suppresses the differential operation between the rotating elements, so that an increase in driving loss can be suppressed. Therefore, in the continuously variable transmission, a reduction in torque transmission efficiency between the input and output is suppressed.

FIG. 1 is a conceptual diagram illustrating an example of a configuration of a continuously variable transmission according to a first embodiment that is a control target. FIG. 2 is a collinear diagram of the continuously variable transmission of FIG. FIG. 3 is a conceptual diagram showing another configuration example of the continuously variable transmission of the first embodiment to be controlled. FIG. 4 is a collinear diagram of the continuously variable transmission of FIG. FIG. 5 is a conceptual diagram illustrating another configuration example of the continuously variable transmission according to the first embodiment to be controlled. FIG. 6 is a collinear diagram of the continuously variable transmission of FIG. FIG. 7 is a collinear diagram of the continuously variable transmission according to the second embodiment. FIG. 8 is a conceptual diagram illustrating an example of a configuration of a continuously variable transmission according to a second embodiment that is a control target. FIG. 9 is a flowchart showing a control operation of the continuously variable transmission of FIG. FIG. 10 is a conceptual diagram illustrating another configuration example of the continuously variable transmission according to the second embodiment to be controlled. FIG. 11 is a flowchart illustrating a modification of the control operation of the continuously variable transmission according to the second embodiment.

  A drive control device according to the present invention has an input member as a rotating element and a plurality of output members, and a continuously variable transmission mechanism that continuously changes a rotation speed ratio between the output members, and an output thereof A continuously variable transmission including a differential mechanism having a rotating element engaged with a member for each output member is a control target. Here, the continuously variable transmission mechanism is configured as, for example, a so-called traction planetary gear mechanism including a plurality of rotating elements, and includes an input member, a rolling member that rolls as the input member rotates, Two output members that sandwich the rolling member, and the torque of the input member is transmitted to the respective output members by the frictional force generated between the input member, the rolling member, and each output member. And the ratio of the rotation speed between the respective output members is changed steplessly according to the tilt angle of the rolling member. On the other hand, the differential mechanism is configured as a so-called planetary gear mechanism, for example, and includes a plurality of rotating elements. The drive control device controls each output member of the continuously variable transmission mechanism to the same rotational speed, thereby stopping the differential operation of the differential mechanism (differential rotation between the rotating elements in the engaged state), The rotational difference of each rotating element of the differential mechanism is set to zero. At that time, each rotating element of the differential mechanism rotates together with each output member of the continuously variable transmission mechanism. Therefore, this drive control apparatus can suppress the drive loss accompanying the differential operation of the differential mechanism. Embodiments of a drive control apparatus according to the present invention will be described below in detail with reference to the drawings. The present invention is not limited to the embodiments.

[Example 1]
A drive control apparatus according to a first embodiment of the present invention will be described with reference to FIGS.

  First, an example of a continuously variable transmission to be controlled by the drive control apparatus according to the first embodiment will be described with reference to FIG. Reference numeral 100 in FIG. 1 indicates a continuously variable transmission according to the first embodiment. In the continuously variable transmission 100, an input shaft 101 that forms a torque input portion and an output shaft 102 that forms an output portion are arranged coaxially. The input shaft 101 is connected to the output side of the driving force source of the vehicle. The input shaft 101 and the output shaft 102 have a common rotation axis X as shown in FIG. In the following, unless otherwise specified, the direction along the rotation axis X is referred to as the axial direction, and the direction around the rotation axis X is referred to as the circumferential direction. Further, the direction perpendicular to the rotation axis X is referred to as a radial direction, and among these, the inward side is referred to as a radial inner side, and the outward side is referred to as a radial outer side.

  The continuously variable transmission 100 includes a continuously variable transmission mechanism 10 that forms a transmission unit, a shift mechanism 20 that shifts the continuously variable transmission mechanism 10, and a differential mechanism 30 that forms an output unit together with an output shaft 102. .

  First, the continuously variable transmission mechanism 10 according to the first embodiment will be described in detail.

  The continuously variable transmission mechanism 10 includes a sun roller 11 as an input member, a plurality of planetary balls 12 as rolling members, and first and second output disks 13 and 14 as output members. To form a traction planetary gear mechanism.

  The sun roller 11 is, for example, a cylindrical rotating body that can rotate around the rotation axis X, and rotates in conjunction with the rotation of the input shaft 101. The sun roller 11 may be configured to rotate integrally with the input shaft 101 at the same rotational speed, and may be configured to rotate at different rotational speeds with other components interposed between the input shaft 101 and the sun roller 11. May be good. In the sun roller 11, an outer peripheral surface thereof serves as a torque transmission surface to the planetary ball 12. The sun roller 11 transmits torque to each planetary ball 12 by a frictional force generated between the outer peripheral surface of the sun roller 11 and the outer peripheral curved surface of the planetary ball 12.

  The respective planetary balls 12 are arranged on the outer circumferential surface of the sun roller 11 radially at substantially equal intervals around the rotation axis X. The planetary ball 12 is a rolling element and corresponds to a ball-type pinion in the traction planetary gear mechanism. The planetary ball 12 is preferably a perfect spherical body, but may have an elliptical cross section such as a rugby ball.

  The planetary ball 12 is rotatably supported by a support shaft 12a that passes through the center thereof. For example, the planetary ball 12 can be rotated relative to the support shaft 12a (that is, rotated) by a bearing (not shown) disposed between the outer periphery of the support shaft 12a. Therefore, the planetary ball 12 can roll on the outer peripheral surface of the sun roller 11 around the support shaft 12a.

  The support shaft 12a is disposed such that its central axis is on a plane including the rotation axis X. The reference position of the support shaft 12a is a position where the central axis is parallel to the rotation axis X, as shown by a solid line in FIG. The support shaft 12a can swing (tilt) between the reference position and a position inclined from the reference position. The tilting is performed in a plane including the central axis of the support shaft 12a and the rotation axis X. This tilting operation is performed by a shift mechanism 20 attached to both ends of the support shaft 12a protruding from the outer peripheral curved surface of the planetary ball 12.

  The shift mechanism 20 includes a tilting arm 21 attached to both ends of the support shaft 12a, and a pushing member 22 that moves the tilting arm 21.

  The tilting arm 21 is a member for causing a tilting force to act on the support shaft 12a and the planetary ball 12 and tilting the rotation center axis of the planetary ball 12, that is, the center axis of the support shaft 12a. A pair of tilting arms 21 is prepared for one support shaft 12 a and one planetary ball 12. For example, the tilting arm 21 is formed and arranged in a shape extending in a direction perpendicular to the rotation axis X. The tilting arm 21 is attached at its radially outer end to the end of the support shaft 12a. One of the pair of tilting arms 21 moves radially outward and the other moves radially inward, so that a tilting force is applied to the support shaft 12 a and the planetary ball 12. The tilting arm 21 is housed and held in an operable state in a groove formed in the disc portion of the carrier 15. The grooves are formed radially about the rotation axis X in accordance with the number and position of the tilting arms 21. The tilting arm 21 is disposed so as not to move relative to the input shaft 101 in the axial direction and to rotate in the circumferential direction.

  The tilting force is generated by moving the pushing member 22 in the axial direction and applying the pushing force of the pushing member 22 to the radially inner portion of the tilting arm 21. For example, the distal end portions on the radially inner side of the pair of tilting arms 21 that support the support shaft 12a have wall surfaces that are opposed to each other in the axial direction tapering toward the radially inner side. Further, in the pushing member 22, the respective wall surfaces at both ends in the axial direction serve as contact surfaces with the tapered surfaces of the respective tilting arms 21, and the contact surfaces are tapered toward the radially outer side. . As a result, the tilting arm 21 is pushed up radially outward when the pushing force of the pushing member 22 is applied, so that the support shaft 12a is tilted, and the planetary ball 12 is tilted in conjunction therewith. The tilt angle φ of the planetary ball 12 is 0 degree at the reference position in FIG.

  The shift mechanism 20 is provided with a movable part and an engaging part (not shown) for operating the pushing member 22. The movable part can reciprocate in the axial direction. On the other hand, the engaging portion is engaged with the pushing member 22 and reciprocates integrally with the movable portion. In this shift mechanism 20, by operating the movable part, the engaging part is also moved in the axial direction, thereby pushing the pushing member 22 in the axial direction. Here, the shift mechanism 20 includes an electric actuator such as an electric motor, a hydraulic actuator, or the like as a drive source (not shown) of the movable part. The operation of the drive source is controlled by the drive control device 1.

  The continuously variable transmission mechanism 10 is provided with a carrier 15 that holds the planetary ball 12, the support shaft 12a, and the tilting arm 21 so as not to move relative to the sun roller 11 input shaft 101 in the axial direction. The carrier 15 has a pair of disc parts having the rotation axis X as a central axis. Each disk part is disposed at a position where the planetary ball 12, the support shaft 12a, the tilting arm 21 and the like are sandwiched in the axial direction, and these are moved relative to the sun roller 11 and the input shaft 101 in the axial direction. Hold it without letting it go. In addition, the respective disk portions are arranged so as not to rotate relative to the input shaft 101 in the circumferential direction.

  The first and second output disks 13 and 14 can transmit mechanical power, in other words, torque, to and from each planetary ball 12. The first and second output disks 13 and 14 are formed in an annular shape having the rotation axis X as a central axis, and are arranged so as to sandwich each planetary ball 12 while facing each other in the axial direction. The first and second output disks 13 and 14 rotate relative to the input shaft 101.

  The first and second output disks 13 and 14 have contact surfaces that come into contact with the outer peripheral curved surface on the radially outer side of each planetary ball 12. Each contact surface forms a concave arc surface having a curvature equivalent to the curvature of the outer peripheral curved surface of the planetary ball 12, and the distance Rd from the rotation axis X to the contact portion with each planetary ball 12 has the same length. It is formed to become. For this reason, here, the contact angles θ of the first and second output disks 13 and 14 with respect to the planetary balls 12 are the same. The contact angle θ is an angle from the reference to the contact portion with each planetary ball 12. Here, the radial direction is used as a reference. The respective contact surfaces are in point contact or line contact with the outer peripheral curved surface of the planetary ball 12. In addition, the direction of the contact line in the line contact is an orthogonal direction to the plane when the planetary ball 12 is tilted. Each contact surface is radially inward of the planetary ball 12 when a force in the axial direction toward the planetary ball 12 is applied to the first and second output disks 13 and 14. And it is formed so that the force of the diagonal direction may be added.

  In this continuously variable transmission mechanism 10, when the tilt angle φ of each planetary ball 12 is 0 degree, the first output disk 13 and the second output disk 14 have the same rotational speed (same rotational angular velocity). Rotate. On the other hand, when each planetary ball 12 is tilted from the reference position, the respective distances from the central axis of the support shaft 12a to the contact portions with the first and second output disks 13, 14 change. Therefore, one of the first or second output disks 13 and 14 rotates at a higher speed than when it is at the reference position, and the other rotates at a lower speed. For example, the first output disk 13 rotates at a lower speed than the second output disk 14 when the planetary ball 12 is tilted to one side. Here, the upper planetary ball 12 in FIG. 1 is tilted in the clockwise direction on the paper, and the lower planetary ball 12 is tilted in the counterclockwise direction on the paper. Further, when the planetary ball 12 is tilted to the other side, the first output disk 13 rotates at a higher speed than the second output disk 14. Here, the upper planetary ball 12 in FIG. 1 is tilted counterclockwise on the page, and the lower planetary ball 12 is tilted clockwise on the page. Therefore, in this continuously variable transmission mechanism 10, the ratio of the rotation speed (rotational angular velocity) between the first output disk 13 and the second output disk 14 is made stepless by changing the tilt angle φ. Can be changed.

  In this continuously variable transmission mechanism 10, at least one of the first or second output disks 13, 14 is pressed against each planetary ball 12, and the first and second output disks 13, 14; A pressing portion (not shown) that generates a pinching force between each planetary ball 12 is provided. For example, the pressing portion may be a drive source such as an electric actuator or a hydraulic actuator, and a torque cam that generates an axial force with the rotation of the first or second output disk 13 or 14 to be disposed. Such a mechanism may be used. In this continuously variable transmission mechanism 10, by operating the pressing portion, a clamping pressure is generated between the first and second output disks 13, 14 and each planetary ball 12, and a frictional force is generated therebetween. To do. For this reason, in the continuously variable transmission mechanism 10, the rotational torque due to the rotation of the respective planetary balls 12 is transmitted to the first and second output disks 13, 14, and the first and second output disks 13, 14 can be rotated. At that time, the pinching force by the pressing portion also generates a pressing force for pressing each planetary ball 12 against the sun roller 11. Accordingly, in this continuously variable transmission mechanism 10, a frictional force is also generated between each planetary ball 12 and the sun roller 11. Therefore, the rotational torque (input) of the sun roller 11 is transmitted to each planetary ball 12, and the respective planetary planets 12. The ball 12 can be rotated.

  The differential mechanism 30 includes a plurality of rotating elements capable of differential operation (differential rotation) between the engaged states. For example, the differential mechanism 30 is configured as a planetary gear mechanism in which a third rotation element having a different rotation axis is engaged between a first rotation element having a common rotation axis X and a second rotation element. To do. The first and second output disks 13 and 14 described above are engaged with any one of the rotating elements in the differential mechanism 30. The rotation elements to be connected are selected to be different between the first output disk 13 and the second output disk 14.

  Specifically, the differential mechanism 30 includes, as rotating elements, a ring gear 31 in which a tooth surface is formed on the inner peripheral surface of a cylindrical portion having the rotational axis X as a central axis, and a cylindrical portion having the rotational axis X as a central axis. And a plurality of planetary gears 33 that are disposed between the tooth surfaces of the ring gear 31 and the sun gear 32 and mesh with each other. Each planetary gear 33 is connected by a planetary gear carrier 34. The planetary gear carrier 34 is coupled to the output shaft 102 so as to rotate together.

  In the first embodiment, the ring gear 31 and the second output disk 14 are coupled so as to rotate together, and the sun gear 32 and the first output disk 13 rotate together. Link.

  In this continuously variable transmission 100, when each planetary ball 12 is at the reference position (tilt angle φ is 0 degree), the first output disk 13 (Dout1) and the second output disk 14 (Dout2) Rotate at the same rotation speed, the planetary gears 33 do not rotate, and the respective rotating elements of the differential mechanism 30 rotate as a unit. The state at the constant speed is shown in the alignment chart of FIG.

  On the other hand, when each planetary ball 12 tilts with respect to the reference position, each planetary gear 33 rotates due to the rotational difference between the first output disk 13 and the second output disk 14, and the output shaft 102 Increase or decrease the rotation speed. The state at the time of acceleration or deceleration is also shown in the alignment chart of FIG. For example, when the planetary ball 12 is tilted in the clockwise direction in FIG. 1, the ring gear 31 has a higher rotation than the sun gear 32, and the rotation of the output shaft 102 is increased more than at the reference position. Can do. On the other hand, when the planetary ball 12 is tilted counterclockwise in FIG. 1, the ring gear 31 rotates less than the sun gear 32, and the rotation of the output shaft 102 is decelerated compared to the reference position. Can do.

  In the continuously variable transmission 100, as shown in the collinear diagram of FIG. 2, the speed ratio γf in the continuously variable transmission 100 is narrower than the speed ratio γcvp in the continuously variable transmission mechanism 10. The speed ratio γcvp in the continuously variable transmission mechanism 10 is the speed ratio of the continuously variable transmission mechanism 10 between the sun roller 11 (input shaft 101) and the first and second output disks 13 and 14. . On the other hand, the gear ratio γf in the continuously variable transmission 100 is the final gear ratio between the sun roller 11 (input shaft 101) and the output shaft 102.

  The final gear ratio γf of the continuously variable transmission 100 is derived from Equation 1 below. In Equation 1, “ρ” is a ratio of the number of teeth Zr of the ring gear 31 and the number of teeth Zs of the sun gear 32 (ρ = Zs / Zr). “Rs” is a radius of the sun roller 11 around the rotation axis X.

  By the way, the continuously variable transmission 100 is provided with the continuously variable transmission mechanism 10 and the differential mechanism 30 as described above. In this type of continuously variable transmission mechanism 10, it is more than hydraulic oil such as ATF normally used in a transmission so that torque can be transmitted on the rolling surface by frictional force while suppressing slippage between the respective rotating elements. A thing with a high traction coefficient (so-called traction fluid etc.) is used. On the other hand, the differential mechanism 30 uses hydraulic oil such as ATF for lubrication. This is because when the hydraulic fluid such as traction fluid is used for the differential mechanism 30, the driving loss increases between the tooth surfaces as compared with the case where hydraulic fluid such as ATF is used. Therefore, in order to use two types of hydraulic oil in this continuously variable transmission 100, the continuously variable transmission mechanism 10 and the differential mechanism 30 are stored in separate rooms, and liquid tightness between the respective rooms is ensured. There must be. For this reason, when two types of hydraulic fluid are used, the number of parts increases and the physique increases.

  Therefore, in the first embodiment, such a separate chamber structure is not used, and hydraulic oil such as traction fluid is also used for lubrication of the differential mechanism 30, thereby increasing the number of parts and the size of the body. While suppressing enlargement, the increase in the drive loss in the differential mechanism 30 is also suppressed.

  On the other hand, this causes a drive loss in the differential mechanism 30 as described above, and reduces the transmission efficiency of torque between the input and output in the continuously variable transmission 100. Here, the drive loss is caused when the differential mechanism 30 performs a differential operation and there is a rotational difference between the respective rotating elements, that is, the planetary gear 33 rotates between the ring gear 31 and the sun gear 32. Sometimes occurs. For this reason, the continuously variable transmission 100 according to the first embodiment is configured so as to shift gears only under a necessary minimum condition, and to prevent the differential mechanism 30 from being differentially operated in normal times. Specifically, the planetary ball 12 is controlled to the reference position (that is, the tilt angle φ is 0 degree), and the first output disk 13 and the second output disk 14 are rotated at the same rotational speed (same rotational angular velocity). The drive control device 1 is configured to perform the above.

  As a useful application example of this configuration, the following can be considered. For example, in a vehicle using an electric motor (not shown) as a drive source, a configuration in which the motor torque of the electric motor is input to the input shaft 101 and the torque is transmitted to the drive wheels via the continuously variable transmission 100 can be considered. In this case, the drive control device 1 normally controls the tilt angle φ of the planetary ball 12 to 0 degree, and causes the drive control device 1 to execute a thing corresponding to a shift by adjusting the motor torque of the electric motor. Thereby, in the continuously variable transmission 100, since the differential mechanism 30 does not perform a differential operation, it is possible to suppress the drive loss between the tooth surfaces of each rotating element, and to reduce the torque transmission efficiency between the input and output. Can be suppressed. In this case, the continuously variable transmission 100 does not perform the speed change function because the gear ratio γf = 1, but the motor torque of the electric motor itself is adjusted, so that a desired required driving force can be generated in the vehicle. it can.

  The drive control device 1 tilts the planetary ball 12 when a large output torque or high rotation is required in the output shaft 102, for example, when a large required driving force or maximum speed is required. The continuously variable transmission 100 is shifted by controlling the angle φ to the required speed increasing side. Thereby, in this case, since the differential mechanism 30 performs a differential operation, the transmission efficiency of torque between the input and output of the continuously variable transmission 100 is lower than normal, but the required driving force and the like are realized. be able to. Here, in other words, the time means that the required driving force or the like cannot be realized only by adjusting the motor torque. Therefore, the normal time mentioned above refers to a time when the required driving force can be realized only by adjusting the motor torque. Further, the drive control device 1 shifts the continuously variable transmission 100 by controlling the tilt angle φ of the planetary ball 12 to a necessary deceleration side angle, for example, when a large required deceleration is required. Let In other words, the time is the time when the required deceleration cannot be realized only by adjusting the motor torque. Thereby, in this case, since the differential mechanism 30 performs a differential operation, the torque transmission efficiency between the input and output of the continuously variable transmission 100 is lower than normal, but the required deceleration is realized. Can do.

  As described above, the drive control device 1 according to the first embodiment has the structure of the continuously variable transmission 100 that suppresses the increase in the number of parts and the enlargement of the physique by controlling the shift timing of the continuously variable transmission 100. The cost can be reduced. Furthermore, the drive control device 1 can improve the torque transmission efficiency between the input and output of the continuously variable transmission 100, and can suppress the decrease in the transmission efficiency to the minimum necessary. Therefore, in the vehicle exemplified above, the motor torque can be efficiently transmitted to the drive wheels, and wasteful energy consumption in the drive source can be suppressed. Further, in a vehicle having an engine such as an internal combustion engine as a drive source, the fuel consumption of the engine can be improved.

  The shift timing control by the drive control device 1 can be applied to the continuously variable transmission 100 described above as well as the following configuration, and the same effect as that of the continuously variable transmission 100 can be applied. Can be obtained.

  For example, a continuously variable transmission 110 shown in FIG. 3 can be considered as an example. The continuously variable transmission 110 is obtained by changing the connection form between the continuously variable transmission mechanism 10 and the differential mechanism 30 and the connection form between the differential mechanism 30 and the output shaft 102 with respect to the continuously variable transmission 100. In the continuously variable transmission 110, the second output disk 14 and the planetary gear carrier 34 are connected to rotate together, and the ring gear 31 and the output shaft 102 are connected to rotate together. is doing. According to this continuously variable transmission 110, the final speed ratio γf can be made wider than the continuously variable transmission 100. The final width of the gear ratio γf is wider than the width of the gear ratio γcvp in the continuously variable transmission mechanism 10, as shown in the collinear diagram of FIG. Here, the final gear ratio γf of the continuously variable transmission 110 can be derived from the following equation 2.

  Moreover, the continuously variable transmission 120 shown in FIG. 5 may be used. In this continuously variable transmission 120, the first output disk 13 and the planetary gear carrier 34 are connected so as to rotate together, and the second output disk 14 and the ring gear 31 rotate together. Further, the sun gear 32 and the output shaft 102 are connected so as to rotate together. According to this continuously variable transmission 120, the final speed ratio γf can be made wider than the continuously variable transmission 110. The width of the final gear ratio γf is significantly wider than the width of the gear ratio γcvp in the continuously variable transmission mechanism 10 as shown in the alignment chart of FIG. Here, the final gear ratio γf of the continuously variable transmission 120 can be derived from the following equation (3).

[Example 2]
Next, a second embodiment of the drive control apparatus according to the present invention will be described with reference to FIGS.

  In the above-described drive control device 1 of the first embodiment, the tilt angle φ of the planetary ball 12 is normally set in order to improve the torque transmission efficiency between the input and output of the continuously variable transmissions 100, 110, 120. Is controlled to 0 degrees, and the first output disk 13 and the second output disk 14 are rotated at the same rotational speed, thereby prohibiting the differential operation of the differential mechanism 30. However, under actual usage conditions, even if a load is applied to the continuously variable transmission 100 (110, 120) (when loaded) and the tilt angle φ of the planetary ball 12 is controlled to 0 degree, the first output It may be difficult to rotate the disc 13 and the second output disc 14 at the same rotational speed. This is because a minute slip (so-called creep) occurs between the first and second output disks 13 and 14 and the respective planetary balls 12 when there is a load, and the slip amount (creep amount). This is because the first output disk 13 and the second output disk 14 may be different. The reason for the difference in the amount of slip is that the ratio of torque sharing between the first output disk 13 and the second output disk 14 is not uniform. The ratio varies depending on what is the rotational element of the differential mechanism 30 to be engaged with the first and second output disks 13 and 14, and what is the gear ratio of the differential mechanism 30. . Therefore, depending on the structure of the continuously variable transmission 100 (110, 120), each of the first output disk 13 and the second output disk 14 can be controlled only by controlling the tilt angle φ of the planetary ball 12 to 0 degrees. There is a possibility that the rotation speed cannot be made uniform.

  The actual use situation is shown in the alignment chart of FIG. When there is no load, which is an ideal state, almost no creep occurs in the first output disk 13 (Dout1) and the second output disk 14 (Dout2), so that the respective rotation speeds become the same, and the difference There is no rotational difference between the respective rotating elements such as the ring gear 31 and the sun gear 32 in the moving mechanism 30, and these rotate together (one-dot chain line). Alternatively, since the rotational difference between the first output disk 13 and the second output disk 14 is very small, the differential operation in the differential mechanism 30 is suppressed, and even if a differential operation occurs, it is insignificant. The drive loss is negligible.

  However, the rotation speed of the first output disk 13 and the second output disk 14 at the time of loading may decrease at different reduction rates depending on each creep, and may rotate at different rotation speeds. For this reason, the differential mechanism 30 starts a differential operation (broken line).

  Here, in the differential mechanism 30 of the continuously variable transmission 100 under load, if the output torque of the planetary gear carrier 34 (output shaft 102) is “1 + ρ”, the torque of the ring gear 31 is “1”, and the sun gear 32 Torque becomes “ρ”. Note that “ρ” is the ratio of the number of teeth Zr of the ring gear 31 and the number of teeth Zs of the sun gear 32 described above. Generally, since the value of ρ used for a transmission of an automobile is about 0.3 to 0.6, the ring gear 31 and the sun gear 32 each have a different magnitude of torque. Therefore, in the continuously variable transmission 100, the first and second output disks 13 and 14 and the planetary balls 12 are controlled in order to suppress a large slip (so-called gross slip) with respect to the contact member of each rotating element. Is set in accordance with the higher torque sharing ratio. In the case of the continuously variable transmission 100, the clamping pressure of the first output disk 13 that is engaged with the sun gear 32 becomes excessive, so that the creep amount of the first output disk 13 is engaged with the ring gear 31. Less than the related second output disk 14. As a result, as shown by a broken line in the collinear diagram of FIG. 7, in the differential mechanism 30, a rotational difference is generated between the ring gear 31 and the sun gear 32, and a drive loss occurs between the planetary gear 33. .

  Therefore, in the second embodiment, control is performed so that the difference in rotation speed (rotational angular velocity) between the first output disk 13 and the second output disk 14 falls within an allowable range. The rotational difference of each rotating element is also set within an allowable range. Specifically, by adjusting the tilt angle φ of the planetary ball 12, the ratio of the rotational speed (rotational angular velocity) of the first output disk 13 and the second output disk 14 can be suppressed from lowering the torque transmission efficiency. Control to size. For this purpose, the drive control device 1 of the second embodiment detects or estimates the respective rotation speeds (rotational angular velocities) of the first output disk 13 and the second output disk 14.

  For example, in the continuously variable transmission 130 according to the second embodiment, as shown in FIG. 8, the first rotation information detector 41 capable of detecting the rotation information of the first output disk 13 and the second output disk 14 are detected. And a second rotation information detector 42 capable of detecting the rotation information. The continuously variable transmission 130 is provided with first and second rotation information detection units 41 and 42 for the continuously variable transmission 100 of FIG. The rotation information detected by the first and second rotation information detectors 41 and 42 is information for obtaining the rotation speed (rotational angular velocity) of the first and second output disks 13 and 14. For example, the rotational angle or rotational speed of the first and second output discs 13 and 14, the rotational angle of the sun gear 32 and the ring gear 31 that are engaged with the first and second output discs 13 and 14, or It refers to the rotational angular velocity.

  In the drive control device 1 according to the second embodiment, if the difference in rotational speed (rotational angular velocity) between the first output disk 13 and the second output disk 14 is not more than a predetermined value, the tilt angle φ of the planetary ball 12 is Is maintained as it is, and if the difference is larger than a predetermined value, the tilt angle φ of the planetary ball 12 is adjusted so that the difference is not more than the predetermined value. The difference being equal to or less than a predetermined value means that the difference is within an allowable range in terms of torque transmission efficiency. Accordingly, the predetermined value includes, for example, the difference in the rotational speed (rotational angular velocity) when the torque transmission efficiency of the continuously variable transmission 130 does not need to be reduced, and when the reduction is within an allowable range. What is necessary is just to set the largest difference in the difference of rotation speed (rotation angular velocity). The control operation will be described below with reference to the flowchart of FIG.

  The drive control device 1 acquires gear ratio control information of the continuously variable transmission 130 (step ST1). The gear ratio control information is information for controlling the gear ratio of the continuously variable transmission 130, and corresponds to, for example, the vehicle speed, the required driving force, the hydraulic oil temperature, and the like. The drive control device 1 sets a required value of the gear ratio of the continuously variable transmission 130 based on the gear ratio control information, and controls the continuously variable transmission 130 so that the required gear ratio is obtained.

  The drive control device 1 uses the speed ratio control information to determine whether the speed ratio of the continuously variable transmission 130 is fixed at the current speed ratio or is changed (step ST2). Here, when it is determined that the gear ratio is changed, the drive control device 1 ends the control operation.

  If it is determined in step ST2 that the gear ratio is fixed, the drive control device 1 determines the first and second output discs based on the detection signals of the first and second rotation information detectors 41 and 42. Information on the respective rotational speeds (or rotational angular velocities) 13 and 14 is acquired (step ST3). Then, the drive control apparatus 1 determines whether or not the difference ΔN in the rotation speed (rotational angular velocity) between the first output disk 13 and the second output disk 14 is within the predetermined value N0 (step). ST4).

  If the difference ΔN is within the predetermined value N0, the drive control device 1 returns to step ST1 and repeats this control operation. The reason why this control operation is repeated at this time is that the reason for the difference in the rotation speed (rotational angular velocity) between the first output disk 13 and the second output disk 14 is mainly due to the structure of the continuously variable transmission 130. This is because the difference ΔN is not always the same. For example, the difference ΔN depends on the amount of creep of each of the first and second output disks 13 and 14, and depends on the magnitude of the load on the input shaft 101 or the output shaft 102 and the fluctuation of the load. It may change. Therefore, the accuracy of this control can be increased by performing such repeated operations.

  When it is determined in step ST4 that the difference ΔN is greater than the predetermined value N0, the drive control device 1 controls the tilt angle φ of each planetary ball 12 according to the magnitude of the difference ΔN (step ST5). The adjustment amount (target tilt angle) of the tilt angle φ of the planetary ball 12 may be set to a size that can keep the difference ΔN within at least a predetermined value, and the difference ΔN becomes 0 as much as possible. It is desirable to set such a value. The relationship between the difference ΔN and the adjustment amount of the tilt angle φ may be prepared in advance as a map.

  Thereby, in the continuously variable transmission 130, the difference ΔN between the rotation speeds (rotational angular velocities) of the first output disk 13 and the second output disk 14 is reduced, and the differential operation of the differential mechanism 30 is suppressed. Thus, the rotational difference between the rotating elements of the differential mechanism 30 falls within an allowable range including zero. For example, with this tilt angle change control, the rotational speed of each of the first output disk 13 and the second output disk 14 must take into account the reduction in rotation due to creep, as shown in the collinear diagram of FIG. In this case, the number of revolutions is different, but the same number of revolutions is obtained by taking into account the reduction in rotation. For this reason, the differential mechanism 30 does not perform the differential operation after the respective rotation speeds are corrected. Therefore, the continuously variable transmission 130 can appropriately suppress a decrease in torque transmission efficiency between its input and output regardless of various conditions such as structure. It should be noted that the rotation reduction allowance due to the creep in the first and second output disks 13 and 14 is almost the same whether or not the tilt angle φ of the planetary ball 12 is changed.

  After performing this tilt angle change control, the drive control device 1 returns to step ST1 and repeats this control operation for the same reason as when an affirmative determination is made in step ST4.

  As described above, the drive control device 1 according to the second embodiment can obtain not only the same effects as the first embodiment but also a good torque transmission efficiency according to the actual use situation. Accordingly, the effect of suppressing energy and the effect of improving fuel consumption can be enhanced.

  Here, the continuously variable transmission 110 of FIG. 3 and the continuously variable transmission 120 of FIG. 5 may also employ the same configuration using the detection signals of the two rotation information detection units. Also by this, the same effect as the previous illustration can be obtained.

  By the way, in this example, the rotation information detection unit (the first output disk 13 and the second output disk 14 or both of the rotation information detection units (first output disks 14) are provided on the two rotation elements of the differential mechanism 30 that are engaged with each other. 1 rotation information detection part 41 and 2nd rotation information detection part 42) are provided. Here, in a general vehicle, in order to detect the vehicle speed, a rotation information detection unit is provided on the output shaft of the transmission (in this example, the output shaft 102) or the torque transmission member on the drive wheel downstream of the transmission shaft. It has been. Further, in order to perform ABS control of the braking device, a rotation information detection unit capable of detecting the rotation information is provided on the axle or the like. From the rotation information of the rotation information detector used for detecting the vehicle speed, the detection target and the first output disk 13 or the rotating element (sun gear 32) of the differential mechanism 30 in engagement with the first output disk 13 are detected. By using this gear ratio, it is possible to obtain rotation information on the first output disk 13 or the rotation element of the differential mechanism 30 that is engaged with the first output disk 13. Similarly, rotation information on the second output disk 14 or the rotation element (ring gear 31) of the differential mechanism 30 engaged therewith can also be obtained.

  Therefore, the drive control device 1 uses one rotation information of the first or second output disks 13 and 14 as a target rotation information detection unit (the first rotation information detection unit 41 or the second rotation information detection unit). 42) and the other rotation information may be obtained based on a rotation information detection unit for vehicle speed detection or the like. In other words, the rotation information detection unit is not engaged with any one of the first rotation information detection unit 41 or the second rotation information detection unit 42 and the first and second output disks 13 and 14. And a rotation information detection unit of a rotation element of the differential mechanism 30.

  For example, an example of the configuration is shown in FIG. The continuously variable transmission 140 of FIG. 10 is provided with the second rotation information detection unit 42 with respect to the continuously variable transmission 100 of FIG. 1 described above. In other words, the continuously variable transmission of FIG. The first rotation information detection unit 41 is removed from 130. Here, the existing rotation information detection unit 103 capable of detecting the rotation information of the output shaft 102 is used. The drive control device 1 obtains the rotation information of the second output disk 14 from the second rotation information detection unit 42. Further, the drive control device 1 obtains the rotation information of the first output disk 13 based on the rotation information of the rotation information detection unit 103 and the gear ratio of the differential mechanism 30. In this way, the drive control device 1 executes the process of acquiring the rotational speed (rotational angular velocity) of each of the first and second output disks 13 and 14 in step ST3.

  Here, since the rotation information detection unit (the first rotation information detection unit 41 or the second rotation information detection unit 42) can be reduced by one by adopting such a configuration, the drive control device 1 reduces the cost. It is possible to obtain the above-described effects while suppressing them. A configuration similar to this may be employed in the continuously variable transmission 110 of FIG. 3 or the continuously variable transmission 120 of FIG. 5, and the same effect can be obtained.

  In these examples, a rotation information detection unit (the first rotation information detection unit 41 or the second rotation information detection) for obtaining rotation information of at least one of the first or second output disks 13 and 14. Part 42) must be prepared. Therefore, a map for deriving the adjustment amount (target tilt angle) of the tilt angle φ of the planetary ball 12 is prepared in advance, and the drive control device 1 tilts without using the new rotation information detection unit. You may comprise so that angle change control can be performed.

  Here, the adjustment amount (target tilt angle) of the tilt angle φ is based on the difference ΔN between the rotation speeds (rotational angular velocities) of the first output disk 13 and the second output disk 14, and the differential mechanism 30. There is a correlation between the differential states (the rotational difference between the ring gear 31 and the sun gear 32 in the case of the continuously variable transmission 100 of FIG. 1). The difference ΔN and the differential state of the differential mechanism 30 depend on the respective creep amounts of the first and second output disks 13 and 14. For this reason, the tilt angle φ has a correlation with the respective creep amounts. Therefore, the map may be created based on the results of obtaining the correspondence between the respective creep amounts and the tilt angle φ by experiments and simulations. In this case, the respective creep amounts are estimated, and the adjustment result (target tilt angle) of the tilt angle φ is obtained by comparing the estimation result with the map.

  In this way, the map may be obtained by variously changing the conditions of the respective creep amounts and the tilt angle φ of the planetary ball 12, but information for estimating the creep amount (hereinafter referred to as “creep amount estimation information”). May be used as a parameter. Each creep amount changes according to the oil temperature, the required driving force, the vehicle speed, etc. of the hydraulic oil, that is, the gear ratio control information. For this reason, gear ratio control information may be used as the creep amount estimation information. When only a part of the gear ratio control information corresponds to the creep amount estimation information, the part of the information is used as the creep amount estimation information. This map is created on the assumption that the gear ratio control information and the condition of the tilt angle φ are variously changed. In this case, the necessary adjustment amount (target tilt angle) of the tilt angle φ can be obtained directly from the gear ratio control information. Further, the map may be created by changing the speed ratio control information and the condition of the above difference ΔN in various ways. In this case, since the current difference ΔN is known from the gear ratio control information, a necessary adjustment amount (target inclination angle) of the tilt angle φ corresponding to the difference ΔN is obtained. In addition, the map may be created by changing various conditions of the transmission ratio control information and the differential state of the differential mechanism 30 (rotational difference between the ring gear 31 and the sun gear 32). In this case, since the current differential state (rotational difference) is known from the gear ratio control information, the necessary adjustment amount (target tilt angle) of the tilt angle φ corresponding to the differential state is obtained.

  In the case of the continuously variable transmission 100 of FIG. 1, the drive control device 1 acquires the gear ratio control information (step ST11) and fixes the gear ratio at the current gear ratio, as shown in the flowchart of FIG. It is determined whether or not it is performed (step ST12). When it is determined that the gear ratio is changed, this control operation is terminated.

  On the other hand, when it is determined in step ST12 that the gear ratio is fixed, the drive control device 1 adjusts the tilt angle φ (target tilt angle) based on the gear ratio control information and any one of the above maps. Is acquired (step ST13). Then, the drive control device 1 controls the tilt angle φ of each planetary ball 12 based on the adjustment amount (target tilt angle) of the tilt angle φ (step ST14).

  Here, since the rotation information detection unit (the first rotation information detection unit 41 and the second rotation information detection unit 42) can be eliminated by adopting such a configuration, the drive control device 1 further reduces the cost. Thus, the effects described above can be obtained. A configuration similar to this may be employed in the continuously variable transmission 110 of FIG. 3 or the continuously variable transmission 120 of FIG. 5, and the same effect can be obtained.

  As described above, the drive control device according to the present invention is useful as a technique for suppressing an increase in drive loss.

DESCRIPTION OF SYMBOLS 1 Drive control apparatus 10 Continuously variable transmission mechanism 11 Sun roller 12 Planetary ball 13 1st output disk 14 2nd output disk 30 Differential mechanism 31 Ring gear 32 Sun gear 33 Planetary gear 34 Planetary gear carrier 41 1st rotation information detection part 42 1st 2-rotation information detection unit 100, 110, 120, 130, 140 continuously variable transmission 102 output shaft 103 rotation information detection unit

Claims (7)

In a continuously variable transmission drive control device in which a continuously variable transmission mechanism for continuously changing a transmission gear ratio and a differential mechanism having a plurality of rotating elements are disposed between an input unit and an output unit.
The continuously variable transmission mechanism continuously changes the ratio of the rotational speeds between the plurality of output members, and the differential mechanism moves the rotating element with respect to the output member for each output member. Are engaged in a one-to-one relationship,
A drive control device characterized in that each output member can be controlled to the same rotational speed.   2. The drive control device according to claim 1, wherein a ratio of the number of rotations between the output members is controlled so that a rotation difference between the rotation elements in the differential mechanism falls within a predetermined range.   3. The drive control apparatus according to claim 2, wherein the ratio of the rotational speed between the output members is controlled so that the rotational difference of the differential mechanism is within a predetermined range including zero.   The continuously variable transmission mechanism includes an input member connected to the input unit, a rolling member that rolls as the input member rotates, and the two output members that sandwich the rolling member, The torque of the input member is transmitted to the output members by the frictional force generated between the input member, the rolling member, and the output members, and the rotation speed between the output members is The drive control device according to claim 1, wherein the ratio is continuously changed in accordance with a tilt angle of the rolling member.   The rotation ratio between the output members is controlled by the creep angle of each output member and the tilt angle of the rolling member which is arranged between the output members and changes the rotation ratio between them in a stepless manner. The drive control apparatus according to claim 4, wherein the drive control apparatus is performed using a map that describes the relationship between   6. The drive control device according to claim 2, wherein the rotation speed ratio between the output members is controlled by detecting the rotation speed of each output member. .   When the continuously variable transmission mechanism includes the two output members, the ratio of the rotation speed between the output members is controlled by any one of the output members and the engagement of the output members. 6. The drive control device according to claim 2, wherein the drive control device performs detection by detecting the number of rotations of a rotating element in the differential mechanism that is not related. 6.

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