JP2006132678A - Toroidal variable transmission and step-less transmission unit - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To secure the power transmission efficiency and the durability by preventing the excessive increase of slide at the traction part (rolling contact part). <P>SOLUTION: The oil pressure lead to an oil pressure room 45 of a pressing equipment 5 is regulated by a pressure regulating valve 41. This pressure regulating valve 41 is switched according to the operation condition of the speed change ratio of a toroidal variable transmission, the lubricant temperature in this toroidal variable transmission and the revolution speed etc. in addition to the magnitude of torque to pass the toroidal variable transmission. The above speed change ratio in these respective operating condition is detected based on the step count of a stepping motor 29 to switch the control valve 21 that feeds the pressure oil into an oil-pressure room 26a, 26b of an actuator 19. Even in the case that the slide occurs in a traction part as a result of this, the above pressure regulating valve 41 can be prevented from being switched in the direction where the pressure of the above pressing equipment 5 is lack, which can solve the above subject. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a toroidal-type continuously variable transmission used as an automatic transmission for a vehicle (automobile) and a continuously variable transmission incorporating this toroidal-type continuously variable transmission, and relates to a traction section (rolling) that transmits power. This prevents the slippage at the contact portion) from becoming excessive and realizes a structure that can ensure transmission efficiency and durability.

  Toroidal type continuously variable transmissions used as automatic transmissions for automobiles are described in many publications such as Patent Document 1, Non-Patent Documents 1 and 2, and are partly implemented and well known. Such a toroidal-type continuously variable transmission includes a plurality of input-side disks (for example, a first disk) and output-side disks (for example, a second disk) having a toroidal curved surface in the axial direction facing each other. The power roller is sandwiched between. During operation, the rotation of the input side disk is transmitted to the output side disk via these power rollers. Each of these power rollers is rotatably supported by a support member such as a trunnion, and each of these support members is subject to swinging displacement about a pivot that is in a twisted position with respect to the central axes of the two disks. It is supported freely. When changing the gear ratio between the two disks, the support members are displaced in the axial direction of the pivot by a hydraulic actuator. Such supply and discharge of pressure oil to and from the actuator is controlled by a control valve, and the movement of the support member is fed back to the control valve.

  When each support member is displaced in the axial direction of the pivot based on supply / discharge of pressure oil to / from the actuator, a rolling contact portion between the peripheral surface of each power roller and the side surface of each disk on the input side and output side ( The direction of the tangential force acting on the traction section changes (side slip occurs in the rolling contact section). Then, with the change in the direction of the force, each support member swings (tilts) about the pivot, and the contact position between the peripheral surface of each power roller and the side surface of each disk on the input side and output side. Changes. If the circumferential surface of each of the power rollers is brought into rolling contact with the radially outward portion of the side surface of the input side disc and the radially inward portion of the side surface of the output side disc, The gear ratio is increased. In contrast, if the circumferential surface of each power roller is brought into rolling contact with the radially inward portion of the side surface of the input side disk and the radially outward portion of the side surface of the output side disc, The gear ratio between the disks is on the deceleration side.

  Further, when the above-described toroidal continuously variable transmission is incorporated into an actual automatic transmission for automobiles, as described in Patent Documents 2 to 7, etc., a gear-type differential unit such as a planetary gear mechanism and the like It has been conventionally proposed to configure a continuously variable transmission in combination. Of these, for example, Patent Documents 6 to 7 are called so-called geared neutrals, and the rotation state of the output shaft can be switched between forward rotation and reverse rotation with the input shaft rotated in one direction with the stop state interposed therebetween. A step transmission is described. In the case of such a continuously variable transmission, the torque (passing torque) that passes through the toroidal continuously variable transmission can be obtained while the output shaft is stopped or rotated at an extremely low speed while the input shaft is rotated. It is necessary to regulate appropriately. In view of such circumstances, Patent Document 8 discloses that the rotational speed of the engine that drives the input shaft is roughly controlled, and the speed ratio of the toroidal continuously variable transmission is adjusted according to this rotational speed. A control method is described in which the torque passing through the toroidal continuously variable transmission is regulated to a target value.

  Patent Document 9 discloses an invention that prevents a pressing force generated by a hydraulic pressing device from temporarily decreasing when a torque (passing torque) passing through a toroidal-type continuously variable transmission fluctuates suddenly. Is described. That is, in the case of the structure described in Patent Document 9, when the passing torque increases rapidly, a signal for increasing the hydraulic pressure introduced into the hydraulic chamber of the pressing device is controlled by the pressure oil introduced into the hydraulic chamber. To the control unit for For this reason, even when the torque changes suddenly, the pressing force generated by the pressing device can be maintained at an appropriate value, and transmission efficiency and durability can be ensured.

  Further, Patent Document 10 describes an invention in which the hydraulic pressure introduced into the hydraulic pressing device is appropriately controlled according to the operation state in order to make the surface pressure of the traction portion (rolling contact portion) appropriate. That is, in the case of the structure described in Patent Document 10, the pressing force generated by the pressing device is used as the force (passing torque) passing through the toroidal continuously variable transmission, that is, between the input side and output side disks. In addition to the magnitude of the force transmitted between them (transmission torque), it depends on the gear ratio between the input and output disks, the temperature of the lubricating oil present inside, and the rotational speed of the engine that is the drive source It can be adjusted to the optimum value. More specifically, the hydraulic pressure introduced into the hydraulic chamber of the pressing device can be adjusted to a target value (a larger value as the passing torque increases) set according to the magnitude of the passing torque (transmission torque). At the same time, the hydraulic pressure adjusted to this target value is changed to correspond to the necessary value required for the pressing device to generate the optimal pressing force, which changes according to the gear ratio, temperature, and rotational speed (decompression). It is free.

  For this reason, in the case of the structure described in Patent Document 10, the pressure adjusting valve for adjusting the hydraulic pressure introduced into the hydraulic chamber of the pressing device changes in proportion to the magnitude of the passing torque. The switch can be switched based on the hydraulic pressure difference between the hydraulic chambers of the hydraulic actuator for displacing the support member (trunnion) that supports the power roller. At the same time, the controller for controlling the solenoid valve for switching the switching state of the pressing force adjusting valve calculates the necessary value based on the detected passing torque, speed ratio, temperature, and rotational speed ( And a function (control function) for controlling the open / close state of the solenoid valve so that the hydraulic pressure adjusted to the target value becomes the calculated required value.

  In the case of such a structure described in Patent Document 10, during operation, the pressing force adjustment valve is based on the hydraulic pressure difference between the hydraulic chambers of the actuator and the opening and closing of the electromagnetic valve controlled by the controller. The switching state can be switched. Based on such switching, the hydraulic pressure introduced into the hydraulic chamber of the pressing device is set to a necessary value necessary to generate an appropriate pressing force corresponding to the passing torque, speed ratio, temperature, and rotational speed. Adjusted. For this reason, it is possible to ensure the transmission efficiency and durability of the toroidal continuously variable transmission by optimizing the pressing force generated by the pressing device, and hence the surface pressure applied to the traction surface based on the pressing force. .

By the way, in the case of such a conventional structure described in Patent Document 10, in order to obtain the speed ratio (N _ID / N _OD ) of the toroidal continuously variable transmission, the rotational speed (N _ID ) of the input side disk The rotation speed (N _OD ) of the output disk is detected by a rotation sensor. The gear ratio is calculated based on the detected rotational speeds of both the input and output disks. However, when the gear ratio is calculated from the rotational speed in this way, for example, when a slip occurs in the traction part for some reason, such as a temporary insufficient pressing force, the above pressing force is calculated based on the calculated gear ratio value. This control may increase this slip. Hereinafter, this point will be described.

  That is, when slipping occurs in the traction unit, the slipping in the traction unit is a gear ratio that corresponds to the gear ratio calculated from each rotational speed and the actual power roller inclination (tilt amount, swing amount). There is a possibility that a shift occurs in the gear ratio in the case where there is no occurrence. If the gear ratio shifts in this way, the hydraulic pressure introduced into the pressing device may be adjusted to a value corresponding to a gear ratio different from the gear ratio corresponding to the actual inclination of the power roller. is there. In such a case, depending on the direction of deviation of the speed ratio calculated from each rotational speed with respect to the speed ratio corresponding to the inclination of the power roller, the hydraulic pressure introduced into the pressing device may be It becomes lower than the oil pressure corresponding to the inclination. Then, there is a possibility that the pressing force generated by the pressing device is lower than the pressing force required at the gear ratio corresponding to the inclination (the pressing force is insufficient). In this way, when the pressing force generated by the pressing device is insufficient, there is a possibility that the slip is excessive in the traction portion. When the slip becomes excessive in this way, the difference between the transmission ratio calculated based on the rotational speeds of the two disks and the transmission ratio corresponding to the inclination of the power roller becomes larger, and the pressing force becomes the inclination. A vicious circle occurs that is even lower than the appropriate value. As a result, the transmission efficiency of the toroidal-type continuously variable transmission is reduced, and in the extreme case, excessive wear and temperature increase may occur in the traction portion, and durability may be reduced.

JP 2001-317601 A JP-A-1-169169 Japanese Patent Laid-Open No. 1-312266 Japanese Patent Laid-Open No. 10-196759 JP 11-63146 A JP 2003-307266 A JP 2000-220719 A JP 2004-225888 A JP 2004-169719 A JP 2004-76940 A Motoo Aoyama, "Bessed Best Car Red Badge Series 245 / A book that understands the latest mechanics of cars", Sanyusha Co., Ltd./Kodansha Co., Ltd., December 20, 2001, p. 92-93 Hirohisa Tanaka, “Toroidal CVT”, Corona Inc., July 13, 2000

  The toroidal-type continuously variable transmission and continuously variable transmission of the present invention, in view of the circumstances as described above, are slipped by a traction part (rolling contact part) that transmits power temporarily due to a temporary shortage of pressure for some reason. The present invention has been invented to realize a structure that can secure the required pressing force at that time, prevent the slip from increasing further, and obtain excellent transmission efficiency and durability.

Among the toroidal-type continuously variable transmission and continuously variable transmission of the present invention, the toroidal-type continuously variable transmission according to claim 1 includes a first disk, a second disk, a plurality of power rollers, and a plurality of supports. A member, an actuator, a transmission ratio control unit, and a pressing device are provided.
Of these, the first and second disks are arranged concentrically and rotatably relative to each other.
Each of the power rollers is sandwiched between the inner surfaces of the first and second disks facing each other, and transmits power between the first and second disks.
The support members support the power rollers rotatably.
Further, the actuator is a hydraulic type, and each of the support members is displaced in the axial direction of the pivots provided at both ends thereof, so that a shift between the first disk and the second disk is achieved. Change the ratio.
The gear ratio control unit controls the displacement direction and the displacement amount of the actuator in order to set the gear ratio to a desired value.
The pressing device presses the first disk and the second disk in a direction approaching each other.
The pressing device is of a hydraulic type that generates a pressing force proportional to the hydraulic pressure as the hydraulic pressure is introduced.
And the hydraulic pressure adjusting means for adjusting the hydraulic pressure introduced into the pressing device is a force (transmission torque, transmission force) that transmits the hydraulic pressure introduced into the pressing device between the first disk and the second disk. The pressing device, which changes in accordance with the magnitude of the passing torque) and the value of the gear ratio between the first disk and the second disk, is required for the appropriate pressing force to be generated. It is introduced into the pressing device in a state adjusted to the required value of the hydraulic pressure.
In particular, in the toroidal type continuously variable transmission according to the present invention, the transmission ratio required for adjusting the hydraulic pressure to the required value is displaced by the drive member constituting the transmission ratio control unit or the drive member. Obtained based on the amount of displacement of the member to be obtained.

According to a fourth aspect of the present invention, a continuously variable transmission includes a toroidal continuously variable transmission and a gear-type differential unit formed by combining a plurality of gears.
The differential unit includes a first input unit that is rotationally driven by an input shaft together with a first disk that constitutes a toroidal-type continuously variable transmission, and a second input unit that is also connected to the second disk. The rotation corresponding to the speed difference between the first and second input parts is taken out and transmitted to the output shaft.
In particular, in the continuously variable transmission of the present invention, the toroidal continuously variable transmission is a toroidal continuously variable transmission as described above.

  According to the toroidal type continuously variable transmission and the continuously variable transmission of the present invention configured as described above, the transmission ratio control unit is configured to determine the transmission ratio required for adjusting the hydraulic pressure introduced into the pressing device to the required value. Since the required value is calculated based on the amount of displacement of the drive member or the like (hereinafter referred to as the drive member or a member displaced by the drive member unless otherwise specified), the necessary value can be accurately calculated. That is, the amount of displacement of the drive member constituting the speed ratio control unit correlates with the inclination (tilt amount, swing amount) of the power roller that swings based on the movement of the actuator controlled by the speed ratio control unit. Have a relationship. For this reason, based on the amount of displacement of the drive member or the like, the inclination of the power roller, and hence the gear ratio corresponding to the inclination of the power roller can be obtained. Then, if the hydraulic pressure introduced into the pressing device is controlled to a required value based on the transmission ratio corresponding to the inclination of the power roller thus obtained, even if slippage occurs in the traction portion, the pressing device is generated. The pressing force can be regulated to an optimum value according to the transmission gear ratio corresponding to the inclination of the power roller. For this reason, even when slip occurs in the traction portion based on a temporary decrease in the pressing force as described above, the pressing force generated by the pressing device is reduced and the slip is not further increased. , Ensuring transmission efficiency and durability.

Preferably, when carrying out the present invention, as described in claim 2, the drive member constituting the gear ratio control unit is a stepping motor for switching a control valve for supplying pressure oil into the hydraulic chamber of the actuator. . Then, based on the drive amount (number of steps) of this stepping motor, the gear ratio between the first disk and the second disk is obtained.
If comprised in this way, the displacement amount of the said drive member or the member displaced by this drive member can be detected, without providing a rotation sensor, a displacement sensor, etc. For this reason, the structure for calculating | requiring the said gear ratio can be comprised simply, and size reduction and weight reduction of an apparatus can be achieved.
It should be noted that control for optimizing the pressing force of the pressing device (control using the hydraulic pressure introduced into the pressing device as a required value) is performed by directly detecting the inclination (tilting amount, swinging amount) of the power roller. It is also conceivable to carry out based on the gear ratio corresponding to this inclination. However, in such a case, it is necessary to provide a rotation sensor on a support member or the like that supports the power roller, and the structure for detecting the tilt may be complicated. On the other hand, when detecting the number of steps, which is the driving amount of the stepping motor, as described above, the speed change corresponding to the number of steps from this number of steps without providing a sensor such as a rotation sensor or a displacement sensor. Ratio or the slope of the power roller. Therefore, the advantage of being able to omit sensors such as the displacement sensor and the rotation sensor can be obtained more remarkably.

When the present invention is implemented, preferably, as described in claim 3, the force (transmission torque) transmitted between the first disk and the second disk and the first disk and the second disk are transmitted. This is a state quantity other than the above-mentioned force and gear ratio that affects the appropriate pressing force to be generated by the pressing device in addition to the gear ratio with the other disc, for example, the temperature of the lubricating oil existing inside and the driving source. The required value of hydraulic pressure is obtained according to the engine speed and the like.
According to this configuration, the pressing force generated by the pressing device is an optimum value not only according to the transmission torque and the transmission ratio but also according to state quantities (temperature and rotational speed) other than the transmission torque and the transmission ratio. Can be finely adjusted. For this reason, it is possible to further ensure the transmission efficiency and durability by making the pressing force, and hence the surface pressure of the traction portion more appropriate.

  1 to 3 show an embodiment of the present invention. First, the continuously variable transmission of this embodiment will be described with reference to the block diagram of FIG. In FIG. 1, a thick arrow indicates a power transmission path, a solid line indicates a hydraulic circuit, and a broken line indicates an electric circuit. The output of the engine 1 is input to the input shaft 3 via the damper 2. The power transmitted to the input shaft 3 is transmitted from the pressing device 5 constituting the toroidal type continuously variable transmission 4 to the input side disk 6 and further to the output side disk 8 via the power roller 7. Of these two discs 6, 8, the rotational speed of the input side disc 6 is measured by the input side rotational sensor 9, and the rotational speed of the output side disc 8 is measured by the output side rotational sensor 10, and is input to the controller 11. The gear ratio (speed ratio) between the disks 6 and 8 (of the toroidal type continuously variable transmission 4) is calculated. In this embodiment, as will be described later, the speed ratio calculated in this way is not used as it is for the control for adjusting the pressing force of the pressing device 5 to an optimum value. Further, as shown in FIG. 2 to be described later, the pressing device 5 is of a hydraulic type that generates a pressing force proportional to the hydraulic pressure when the hydraulic pressure is fed.

  The power transmitted to the input shaft 3 is transmitted directly or via the toroidal continuously variable transmission 4 to the planetary gear type transmission 12 which is a differential unit. Then, the differential component of the constituent members of the planetary gear type transmission 12 is extracted to the output shaft 14 via the clutch device 13. The clutch device 13 represents a low speed clutch 15 and a high speed clutch 16 shown in FIG. In the case of this embodiment, the output shaft rotation sensor 17 can detect the rotation speed of the output shaft 14 so as to determine whether or not the input side rotation sensor 9 and the output side rotation sensor 10 have a failure. Safe is possible.

  On the other hand, the oil pump 18 (18a, 18b in FIG. 2) is driven by the power extracted from the damper 2 portion, and the pressure oil discharged from the oil pump 18 supports the pressing device 5 and the power roller 7. The trunnion, which is a support member, can be fed into a control valve device 20 for controlling the amount of displacement of an actuator 19 (see FIG. 2) that displaces the trunnion in the axial direction of a pivot (not shown). The control valve device 20 includes a control valve 21, a differential pressure cylinder 22, correction control valves 23a and 23b, a high-speed switching valve 24, and a low-speed switching valve 25 shown in FIG. It is a thing. Of these, the control valve 21 controls the supply and discharge of hydraulic pressure to the actuator 19. The hydraulic pressure in a pair of hydraulic chambers 26a and 26b (see FIG. 2) provided in the actuator 19 is detected by a hydraulic sensor 27 (actually, a pair of hydraulic sensors 27a and 27b as shown in FIG. 2). The detection signal is input to the controller 11.

  The controller 11 calculates a torque (passing torque) that passes through the toroidal continuously variable transmission 4 based on a signal from the hydraulic sensor 27. Then, in order to correct the gear ratio of the toroidal type continuously variable transmission 4 according to the passing torque calculated in this way, a sleeve 28 (see FIG. 2) which is a component of the control valve 21 is connected to the differential pressure cylinder 22. Displace by. The supply / discharge of the pressure oil to / from the differential pressure cylinder 22 is controlled by the correction control valves 23a and 23b. Further, the control valve device 20 switches the stepping motor 29 as a driving member, the line pressure control electromagnetic on-off valve 30 for switching a pressing force adjusting valve 41 described later, and the correction control valves 23a and 23b. The operation state can be switched by the electromagnetic valve 31 and the shift electromagnetic valve 32 for switching the high-speed switching valve 24 and the low-speed switching valve 25. The stepping motor 29, the line pressure control electromagnetic on-off valve 30, the electromagnetic valve 31, and the shift electromagnetic valve 32 are all switched based on the control signal from the controller 11. In the case of the present embodiment, the control members 20, 30, 31, 32 that are switched based on the control signal from the controller 11, the control valve device 20 including the control valve 21, The controller 11 constitutes the transmission ratio control unit described in the claims.

  In addition to the signals from the rotation sensors 9, 10, 17 and the hydraulic sensor 27, the controller 11 includes a detection signal from the oil temperature sensor 33, a position signal from the position switch 34, and an accelerator sensor 35. The detection signal and the signal of the brake switch 36 are input. Of these, the oil temperature sensor 33 detects the temperature of the lubricating oil (traction oil) in the casing that houses the continuously variable transmission. The position switch 34 emits a signal indicating an operation position (selection position) of a shift lever (operation lever) provided in a driver's seat for switching a manual hydraulic pressure switching valve 37 described later in FIG. It is. The accelerator sensor 35 is for detecting the opening of the accelerator pedal. Further, the brake switch 36 detects that the brake pedal has been depressed or the parking brake has been operated, and issues a signal indicating that fact.

  Further, the controller 11 is configured to detect the stepping motor 29 and the line pressure control electromagnetic on-off valve 30 based on signals from the switches 34 and 36 and the sensors 9, 10, 17, 27, 33 and 35. In addition to sending the control signal to the solenoid valve 31 and the shift solenoid valve 32, the control signal is sent to the engine controller 38 for controlling the engine 1. And as described in the above-mentioned Patent Document 8, the toroidal continuously variable transmission changes the speed ratio between the input shaft 1 and the output shaft 14, or stops or runs at a very low speed. 4 to control the torque applied to the output shaft 14 (passing torque).

  FIG. 2 shows a hydraulic circuit for controlling the continuously variable transmission as described above. In this hydraulic circuit, the pressure oil sucked from the oil reservoir 39 and discharged by the oil pumps 18 a and 18 b can be adjusted to a predetermined pressure by the low pressure side adjustment valve 40 and the pressing force adjustment valve 41. Among these, the said pressing force adjustment valve 41 which adjusts the hydraulic pressure sent to the press apparatus 5 side is provided with the function as a relief valve, and is provided with the 1st-3rd pilot parts 42-44. Among these, the first and second pilot portions 42 and 43 are torques (passing torques) passing through the toroidal type continuously variable transmission 4, that is, between the input side disk 6 and the output side disk 8. This is for adjusting the valve opening pressure of the pressing force adjusting valve 41 according to the magnitude of the transmitted force (transmission torque). On the other hand, the third pilot section 44 is a transmission ratio of the toroidal-type continuously variable transmission 4, the temperature of the lubricating oil (traction oil) existing in the toroidal-type continuously variable transmission 4, and a drive source. This is for adjusting the valve opening pressure of the pressing force adjusting valve 41 in accordance with operating conditions other than the transmitted force such as the rotational speed of an engine 1. In the case of the present embodiment, by appropriately adjusting the hydraulic pressure introduced into the first to third pilot portions 42 to 44, the pressing force generated by the pressing device 5 is changed to that of the toroidal continuously variable transmission 4. It is configured to properly regulate according to the driving situation.

  For this reason, in the case of the present embodiment, as the hydraulic pressure to be introduced into any one of the first and second pilot portions 42 and 43 increases, the valve opening pressure of the pressing force adjusting valve 41 increases. And the hydraulic pressure introduced into the hydraulic chamber 45 constituting the pressing device 5 is increased. At the same time, a differential pressure between a pair of hydraulic chambers 26a and 26b provided with a piston 46 sandwiched between an actuator 19 for displacing a support member (trunnion) supporting the power roller 7 in the axial direction of the pivot. Is introduced into one of the pilot portions 42 and 43 via the differential pressure take-out valve 47. The differential pressure take-off valve 47 is one of the pressure adjusting valves 41 as the difference between the hydraulic pressures in the hydraulic chambers 26a and 26b of the actuator 19, that is, the force passing through the toroidal continuously variable transmission 4 increases. These are switched so that the hydraulic pressure introduced into the pilot portions 42 and 43 increases. Accordingly, the hydraulic pressure introduced into the hydraulic chamber 45 of the pressing device 5 and thus the pressing force generated by the pressing device 5 increase as the force passing through the toroidal type continuously variable transmission 4 increases. The pressing force generated in the pressing device 5 in this manner is required when the gear ratio of the toroidal type continuously variable transmission 4 is a value that requires the greatest pressing force (for example, 1.32). The oil pressure required for this is set as the target value. Such a target value is set to a value larger than a necessary value described later.

  In this embodiment, pressure oil can be introduced into the third pilot section 44 based on switching of the line pressure control electromagnetic on-off valve 30 controlled by a command from the controller 11. That is, the controller 11 is generated in the pressing device 5 in consideration of the gear ratio of the toroidal-type continuously variable transmission 4, the temperature of the lubricating oil present therein, the rotational speed of the engine 1 as a drive source, and the like. Calculate the required value of hydraulic pressure according to the optimum value of the pressing force to be applied. Then, a hydraulic pressure corresponding to a correction value that is a difference between the necessary value and the target value is introduced into the third pilot section 44 based on the switching of the line pressure control electromagnetic on-off valve 30. The hydraulic pressure introduced into the third pilot portion 44 in this way pushes the spool 48 of the pressing force adjusting valve 41 to the left in FIG. 2, and reduces the hydraulic pressure introduced into the pressing device 5 ( Depressurize). As a result, the hydraulic pressure introduced into the pressing device 5 is proportional to a value obtained by subtracting a correction value based on the hydraulic pressure introduced into the third pilot section 44 from the target value set by the differential pressure take-out valve 47. It is corrected (reduced pressure) to the required value. The oil pressure introduced into the third pilot section 44 is such that the oil temperature decreases as the shift ratio increases from a predetermined value (a value that requires the largest oil pressure, for example, 1.32). Make it higher. In this embodiment, the pressure adjusting valve 41, the differential pressure take-off valve 47, the controller 11, and the line pressure control electromagnetic switching valve 30 are used to adjust the hydraulic pressure as described in the claims. Is configured.

  Further, in the case of the present embodiment, the gear ratio obtained for adjusting the hydraulic pressure to the required value as described above is used as the drive amount of the stepping motor 29 for switching the control valve 21 constituting the gear ratio control unit. Based on the request. For this reason, in the case of the present embodiment, the speed ratio of the toroidal type continuously variable transmission 4 (in a state where no slip occurs in the traction portion) and the number of steps which is the driving amount of the stepping motor 29 The correlation is obtained in advance and stored in the memory of the controller 11. Then, the transmission ratio corresponding to the current number of steps of the stepping motor 29 is obtained from the stored correlation, and the hydraulic pressure is adjusted to the required value as described above based on the command signal of the controller 11. . For example, let us consider a case where the transmission ratio of the toroidal-type continuously variable transmission 4 and the number of steps of the stepping motor 29 have a relationship as shown in FIG. That is, the maximum reduction ratio (Low_max) of the toroidal-type continuously variable transmission 4 is 0.5 and the maximum speed increase ratio (High_max) is 2.2. The speed ratio is from the maximum speed reduction ratio to the maximum speed increase ratio. Consider the case where the number of steps of the stepping motor 29 required to change the value is 390 steps.

Such a correlation is obtained by calculation in advance or by actually operating the toroidal continuously variable transmission 4. That is, while operating the toroidal continuously variable transmission 4 from the minimum deceleration state to the maximum acceleration state (with no slippage in the traction section), the number of steps of the stepping motor 29, the input side, the output The speed ratio N _OD / N of the toroidal continuously variable transmission 4 calculated based on the rotational speeds N _ID and N _OD of the input and output disks 6 and 8 obtained by the side rotation sensors 9 and 10. _{The ID} is stored in the memory of the controller 11 in a state corresponding to each other, for example, a mathematical formula or a map. The relationship between the number of steps obtained in this way and the gear ratio N _OD / N _ID is stored in advance in the controller 11 as an initial setting at the time of factory shipment, and each time the ignition switch is turned on, The toroidal type continuously variable transmission 4 may be reset by operating from the minimum deceleration state to the maximum acceleration state.

  In any case, when there is a correlation as shown in FIG. 3, the amount of change in the gear ratio of the toroidal continuously variable transmission 4 per step of the stepping motor is (2.2- 0.5) /390=0.00436. Therefore, the gear ratio of the toroidal-type continuously variable transmission 4 is the maximum deceleration state {the state of the maximum reduction ratio (0.5)}, or the maximum acceleration state {the state of the maximum acceleration ratio (2.2)}, The state where the output shaft 14 is stopped while the input shaft 3 is rotated {the state where the gear ratio is infinite = GN position (1.7)} is used as a reference, and from this state to the current state If the required number of steps of the stepping motor 29 is known, the transmission ratio of the toroidal type continuously variable transmission 4 can be obtained. Then, a necessary value of the hydraulic pressure corresponding to the optimum value of the pressing force to be generated in the pressing device 5 is calculated from the speed ratio thus determined, and the hydraulic pressure introduced into the pressing device 5 is adjusted as described above. .

  According to this embodiment, the hydraulic pressure introduced into the pressing device 5 is changed to the operating state (passing torque, gear ratio, lubricating oil temperature, engine speed, etc.) of the toroidal continuously variable transmission 4. It can be finely adjusted according to your needs. Therefore, it is possible to ensure the transmission efficiency and durability of the toroidal-type continuously variable transmission 4 by making the surface pressure of the traction portion appropriate. In addition, in the case of the present embodiment, as described above, the transmission ratio of the toroidal-type continuously variable transmission ratio 4 that is obtained in order to adjust the hydraulic pressure introduced into the pressing device 5 according to the operating state is set to the stepping. Obtained based on the number of steps of the motor 29. For this reason, the required value of the hydraulic pressure required for the pressing device 5 to generate an optimal pressing force can be accurately calculated.

  That is, the number of steps of the stepping motor 29 is determined by the inclination of the power roller 7 (inclination amount, swing amount), and the gear ratio corresponding to the inclination of the power roller 7 (inclination amount, swing amount). Correlation. For this reason, based on the number of steps of the stepping motor 29, the inclination of the power roller 7, and hence the gear ratio corresponding to the inclination of the power roller 7, can be obtained. If the hydraulic pressure fed to the pressing device 5 is controlled to a necessary value based on the inclination of the power roller 7 thus obtained or the gear ratio corresponding to this inclination, even if slip occurs in the traction portion, The pressing force generated by the device 5 can be optimized. For this reason, as described above, the pressing force generated by the pressing device due to the slip of the traction portion decreases, and this slip does not increase further, and transmission efficiency and durability can be ensured.

  In the case of the present embodiment, the case where the control for setting the hydraulic pressure introduced into the pressing device 5 to the required value is performed based on the number of steps of the stepping motor 29 as described above. However, the present invention is not limited to such an embodiment. For example, the hydraulic pressure is set to a required value based on the displacement amount of the sleeve 28 of the control valve 21 that is displaced by the stepping motor 29 and the differential pressure cylinder 22. It can also be controlled. However, in this case, the displacement amount of the sleeve 28 or a member displaced together with the sleeve 28 needs to be detected by a displacement sensor or the like, and a rotation sensor or the like is provided to directly detect the inclination of the power roller 7. As with, the structure can be complex. Further, the differential pressure cylinder 22 stops the output shaft 14 while rotating the input shaft 3 or rotates the torque (passing through the toroidal continuously variable transmission 4 while rotating at an extremely low speed). In order to properly regulate the torque, the sleeve 28 is displaced to adjust the gear ratio of the toroidal continuously variable transmission 4. Moreover, the speed ratio width (adjustment width) of the speed ratio adjusted by the differential pressure cylinder 22 is small. For this reason, even if the hydraulic pressure introduced into the pressing device 5 is adjusted based on the gear ratio corresponding to the driving amount (number of steps) of the stepping motor 29 as in the present embodiment, the hydraulic pressure can be sufficiently adjusted to the required value. In addition, in this case, the advantage of not requiring the sensor as described above can be remarkably obtained.

  If the speed ratio is obtained from the detection signals of the input side and output side rotation sensors 9, 10, the speed ratio including the correction by the differential pressure cylinder 22 can be obtained. As described above, the traction section If excessive slip occurs, the required gear ratio becomes inaccurate, and as described above, there is a possibility that the pressing force is insufficient. Taking these points into consideration, the hydraulic pressure is normally regulated based on the transmission ratio obtained from the detection signals of the rotation sensors 9 and 10, and the obtained transmission ratio corresponds to the number of steps. Therefore, the hydraulic pressure can be regulated based on the gear ratio corresponding to the number of steps.

  In addition, the present embodiment is a geared neutral type continuously variable transmission that can switch the rotation state of the output shaft 14 between forward rotation and reverse rotation with the input shaft 3 rotated in one direction with the stop state interposed therebetween. The case where the present invention is applied is shown. However, it is not limited to such a structure. In the low-speed mode, power is transmitted only by the toroidal continuously variable transmission, and in the high-speed mode, the main power is transmitted by a planetary gear type transmission that is a differential unit. The present invention can also be applied to a power split type continuously variable transmission that adjusts the transmission ratio with the toroidal type continuously variable transmission. In addition, the present invention is applied not only to a continuously variable transmission comprising a toroidal type continuously variable transmission and a planetary gear type transmission as an operation unit combined via a clutch device, but also to a toroidal type continuously variable transmission alone. You can also.

The block diagram of the continuously variable transmission which shows the Example of this invention. The hydraulic circuit diagram which shows the mechanism for adjusting the gear ratio of the toroidal type continuously variable transmission built in this continuously variable transmission, and the pressing force which a pressing device generate | occur | produces. The diagram which shows one example of the relationship between the gear ratio of a toroidal type continuously variable transmission, and the number of steps of a stepping motor.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Engine 2 Damper 3 Input shaft 4 Toroidal type continuously variable transmission 5 Pressing device 6 Input side disk 7 Power roller 8 Output side disk 9 Input side rotation sensor 10 Output side rotation sensor 11 Controller 12 Planetary gear type transmission 13 Clutch device DESCRIPTION OF SYMBOLS 14 Output shaft 15 Low speed clutch 16 High speed clutch 17 Output shaft rotation sensor 18, 18a, 18b Oil pump 19 Actuator 20 Control valve device 21 Control valve 22 Differential pressure cylinder 23a, 23b Correction control valve 24 High speed switching valve 25 Low speed Switching valve 26a, 26b Hydraulic chamber 27, 27a, 27b Hydraulic sensor 28 Sleeve 29 Stepping motor 30 Line pressure control electromagnetic switching valve 31 Solenoid valve 32 Shifting solenoid valve 33 Oil temperature sensor 34 Position switch 35 Acceleration sensor 36 Brake switch 7 Manual Hydraulic Switching Valve 38 Engine Controller 39 Oil Reservoir 40 Low Pressure Side Adjusting Valve 41 Pressing Pressure Adjusting Valve 42 First Pilot Part 43 Second Pilot Part 44 Third Pilot Part 45 Hydraulic Chamber 46 Piston 47 Differential Pressure Extraction Valve 48 spool

Claims (4)

  The first and second discs are sandwiched between the inner and outer surfaces of the first and second discs that are concentrically arranged and relatively rotatable, and the first and second discs facing each other. A plurality of power rollers that transmit power between each other, a plurality of support members that rotatably support the power rollers, and the support members that are displaced in the axial direction of the pivots provided at both ends. A hydraulic actuator for changing the speed ratio between the first disk and the second disk, and for controlling the displacement direction and the amount of displacement of the actuator in order to set the speed ratio to a desired value. A gear ratio control unit, and a pressing device that presses the first disk and the second disk in a direction approaching each other, the pressing device being a pressing force proportional to the hydraulic pressure as the hydraulic pressure is introduced The hydraulic pressure adjusting means for adjusting the hydraulic pressure to be introduced into the pressing device generates the hydraulic pressure to be introduced into the pressing device between the first disk and the second disk. The pressing device, which changes according to the magnitude of the force to be transmitted and the speed ratio between the first and second discs, is required for the appropriate pressing force to be generated. In a toroidal type continuously variable transmission that is introduced into the pressing device in a state adjusted to the required value of the hydraulic pressure, the transmission ratio calculated to adjust the hydraulic pressure to the required value is set to the transmission ratio control. A toroidal continuously variable transmission characterized in that it is obtained based on a displacement amount of a drive member constituting the unit or a member displaced by the drive member.   The drive member constituting the transmission ratio control unit is a stepping motor for switching a control valve that supplies pressure oil into the hydraulic chamber of the actuator. Based on the drive amount of the stepping motor, the first disk and the second disk The toroidal-type continuously variable transmission according to claim 1, wherein a transmission gear ratio between and is determined.   In addition to the force transmitted between the first disk and the second disk and the gear ratio between the first disk and the second disk, it affects the appropriate pressing force that the pressing device should generate. The toroidal continuously variable transmission according to any one of claims 1 to 2, wherein a required value of the hydraulic pressure is obtained according to a state quantity other than the force and the gear ratio.   A toroidal-type continuously variable transmission and a gear-type differential unit formed by combining a plurality of gears. Among these, the differential unit is connected to the first disk constituting the toroidal-type continuously variable transmission by an input shaft. It has a first input unit that is rotationally driven and a second input unit that is also connected to the second disk, and rotates according to the speed difference between the first and second input units. In the continuously variable transmission which is taken out and transmitted to the output shaft, the toroidal continuously variable transmission is the toroidal continuously variable transmission according to any one of claims 1 to 3. A continuously variable transmission device.

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